EP0400507A2 - Ensemble à haute pression - Google Patents

Ensemble à haute pression Download PDF

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Publication number
EP0400507A2
EP0400507A2 EP90110004A EP90110004A EP0400507A2 EP 0400507 A2 EP0400507 A2 EP 0400507A2 EP 90110004 A EP90110004 A EP 90110004A EP 90110004 A EP90110004 A EP 90110004A EP 0400507 A2 EP0400507 A2 EP 0400507A2
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EP
European Patent Office
Prior art keywords
pressure
piston
fluid
pistons
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP90110004A
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German (de)
English (en)
Inventor
Karl Eickmann
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Individual
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Individual
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Publication date
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Publication of EP0400507A2 publication Critical patent/EP0400507A2/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members

Definitions

  • the invention relates to a high-pressure unit. It can be a high pressure pump or a control unit, or both combined into a single unit.
  • High pressure pumps are known for example from DE-OS - 3 711 633. Controls for several pump pistons can be found, for example, in British Patent 1,599,524.
  • the pistons are driven by eccentric discs or by swash plates. Despite the use of 5 or seven pistons, these units have the delivery irregularities known from the hydraulic pumps, e.g. B. by three percent for seven pistons.
  • the control of the named British patent can, as the present invention recognizes, only be used for limited pressures because it has not recognized the influence of the compression of the liquids at high pressures and cannot control them.
  • the non-uniformity of the multi-coal piston pumps according to the German published specification is indeed portable for hydraulic pumps up to 500 bar, but no longer for precision drives with high pressures of over a thousand bar.
  • the present invention is therefore based on the object of creating a control or a high-pressure unit for very high pressures, which enables a uniform flow even at high pressures and is also simple to manufacture and particularly reliable in operation.
  • a high-pressure unit that can be a pump or a control arrangement is described above.
  • the harmful influence of the compression of the liquids at high pressures of more than 1000 bar has been investigated and measures have been proposed which reduce or overcome these harmful influences.
  • the influence of the relaxation of the compressed liquids is not or not sufficiently mentioned.
  • the object of the invention according to the current patent application is therefore to limit or overcome the harmful effects of the expansion of the compressed liquids or fluids, or to arrange means which restrict or prevent the harmful effects of the expansion and compression of the fluids at high pressures.
  • High-pressure units are known in the art, which can also be used as water pumps for several thousand bars, for example the "axial boosters" or pressure boosters.
  • the European patent applications 0 102 441 and 0 285 685 also show high-pressure units.
  • modern high-pressure units are described in (not yet published) patent applications by the inventor.
  • the invention is therefore based on the object to limit the shortcomings of the known technology and to create an effective high-pressure unit which works largely without dead spaces and without long periods of pressure drop or reduction in conveyance.
  • Figure 10 shows the longitudinal section through an axial booster of the known technology.
  • medium pressure is alternately directed into the chambers "A” and “B”, whereby the piston “K” with a diameter "D” in the unit is moved periodically from left to right and from right to left.
  • the reversal of the fluid coming from a pump is carried out in a conventional manner, for example by means of magnet-operated reversing slides.
  • the piston "K” is provided with piston rods of smaller diameter "d” which extend to the left and right, so that these piston rods dip into the cylinders "D” and “E” and are moved back and forth in them.
  • At the left and right end of the cylinder there are covers which serve the inlet and outlet valves (not shown in the figure) for the introduction and discharge of the high pressure fluid to and from the cylinders "D” and "E".
  • the volume of the cylinder D is now (d2) pi / 4) times the stroke "S" (stroke in English).
  • the dead space volume “G” is a geometric size that results from the construction and it can be used in "Vg".
  • Vctt [(V D + V G ) Fcw Ph / V D ] + V N Fco Pm / V D (6)
  • Vq (D2 - d2) (pi / 4)
  • the known technology has partly managed to put pressure accumulators, that is accumulators, between the medium pressure pump and the inlets V and W of the chambers A and B. However, these then only had the same pressure that the medium-pressure pump delivered, ie only the pressure P m . If these accumulators had a volume that corresponded to the compression volume Vc, then their pressure dropped to half when the pressure accumulator emptied into chamber A or B. So only half a success was achieved.
  • the volume of the pressure accumulators is made much larger than the compression volume Vc, then they work better, but then they become very large, heavy and large line cross sections are then required for sudden emptying, which in turn create dead space M and N, or increase these dead spaces, which in turn leads to greater production time losses.
  • FIG. 11 shows another example of a technique that has not yet been published.
  • Two medium-pressure pistons K are arranged here, which alternately drive the high-pressure pistons "P". These convey into the outer chambers "OC", which are separated from the inner chambers "IC" by membranes. This separation is done so that a lubricating fluid, such as oil, can be used in the outer chambers, while those with inlet and outlet valves (in the The valves are not shown in the figure).
  • Inner chambers can be used to convey non-lubricating fluid, for example water).
  • the cylinders can again have dead spaces, which are again designated with H, G, M and M.
  • strokes with incomplete strokes can occur again.
  • the fluid in the inner chambers has to be compressed before delivery from the unit can begin.
  • the volume of the outer chambers and inner chambers, if leakage losses remain unconsidered or do not occur and closing time losses of the valves remain unconsidered or do not occur, are equal to the volume of the high pressure chambers D or E.
  • Vcm [V oc ⁇ F cw ⁇ P h + (V D + V N ) F co Ph + D2 ⁇ 4th 4F co P m ] / V D (10)
  • FIG. 1 shows a longitudinal section through a high-pressure unit of the invention. It has in the main housing 464 the medium-pressure cylinders 45, 15 with the medium-pressure pistons 8 and 9 that can be reciprocated therein, and the high-pressure cylinders 11, 12 with the high-pressure pistons 5 and 6 that are reciprocating therein.
  • the middle chamber is formed between parts of the main housing and the pistons mentioned 44, 45, 46, 44 forming the connecting channel between the cylindrical chamber parts 45 and 46 of the central chamber common to all four pistons.
  • the control housing 18, which also closes the medium-pressure cylinders 14, 15, is arranged under the main housing 464. In FIG.
  • valve head or cover 489 is arranged above the main housing 464, to which the high-pressure cylinders 11, 12 open and which the inlet and outlet valves (not shown) for the high-pressure cylinders 11, 12, as well as the inlets and outlets 64.65 to the valves mentioned.
  • 64 shows the inlets and outlets to the cylinder set 11 and 65 the inlets and outlets to the cylinder set 12.
  • the seats 490 are designed for the screws for fastening and detaching the cover from the main housing.
  • an extra medium pressure pump 19 driven by the electric motor 401 by means of a line or flange 486, is usually connected to the supply connection 488 of the medium pressure fluid pump to the connection 487 of the high pressure unit 464.
  • a particular advantage of the high pressure unit 464 is that it can be used anywhere where medium pressure fluid delivery pumps are already available. This is the case, for example, in excavators, bulldozers, tractors, many trucks, etc.
  • medium-pressure fluid which may be between 100 and 800 bar, is fed into the inlet port 487 and flows through the channel (channels) 91 of the control valve 17 via a medium-pressure port 93 and via channel 471 or 473 into one of the medium-pressure cylinders 14 or 15 depending on the position of the control body 17. It is now assumed that the medium pressure fluid is directed to the cylinder 14. Then the medium-pressure piston 8 is pressed upwards and since the medium-pressure piston 8 is connected to the high-pressure piston 5 of the smaller diameter 5 to the piston 8, the high-pressure piston 5 is also pushed upwards, that is to say deep into the cylinder 11, with it being high-pressure fluid from the outlet 64 of the cylinder 11.
  • the middle chamber 44-46 is filled with fluid, for example by means of the pump 484 via line 485 and kept at a constant middle chamber pressure by a pressure valve on line 413.
  • the pressure valve can be commercially available and is therefore not shown in the figure.
  • the fluid in the middle chamber mentioned is a liquid, for example oil, and the middle chamber pressure is relatively low, this fluid in the middle chamber compresses little and presses the piston 9 down when the piston 8 runs up. Analogously, piston 8 runs downwards when piston 9 is pressed upwards.
  • the fluid is pressed out of the cylinder 14 or 15 under the relevant piston 8 or 9 and flows over the mouth in question and line 94 of control valve 17 into line 301, 302 and from there through inlet 313 into the control body drive motor 97 in order to drive it for rotation or for axial stroke.
  • the motor 97 drives the control body 17, for example via the transmission 467, 466, in terms of speed parallel to the amount of medium-pressure fluid which is introduced into the unit 464 of FIG. 1 through the connection 487.
  • control body 17 is kept in continuous motion, for example in rotation, and the pistons 5-8 and 6-9 alternately run up and down, high-pressure fluid being delivered from the high-pressure cylinders 11 and 12 via the outlets 64 and 65.
  • the present invention recognizes. that the aggregates of the British and US patents mentioned can at most be effective as low or medium pressure aggregates. For the very reason that they do not take into account the compression time losses that are recorded and described under "Technical principles" in this document. At high pressures, according to the technical principles of the invention described at the outset, high delivery time losses have to occur during the reversal of the stroke of the pistons, during which the unit cannot deliver a high pressure fluid flow.
  • the current invention recognizes that there is no advantage in using at least three differential pistons in the unit, as required by the British patent.
  • Two differential pistons according to FIG. 1 are not only completely sufficient, but they offer the safest implementation and mastery of continuous funding equality if one follows the basic rules and claims of the current patent application. Controlling the stroke movements of three differential pistons would not increase the conveyance uniformity but would cause additional losses, costs and control problems.
  • the present invention recognizes that the US system prevents its use as a high-pressure unit. Because gear motors are due to their leakage losses or their high friction only for low pressures and the medium pressure of the fluid flow to the medium pressure cylinders 14, 15 should apply up to pressures of 800 bar.
  • the rotating control body 17 of FIG. 1 and its additional figures 2 to 9 is driven not by an upstream gear motor but by a downstream hydraulic motor for rotation and is kept in rotation.
  • the motive fluid flow i.e. the medium pressure fluid flow
  • the medium pressure fluid is taken directly from the pressurized fluid line in the vehicle or from the line 488 of the pump 19 of FIG. 1 and is immediately passed directly into the inlet 487 of the control housing 465 of FIG. 1 without flowing through a motor .
  • the medium pressure fluid reaches the inner channel 91 of the control body, see the sectional figures 2 and 3, after which the medium pressure fluid within the inner medium pressure channel of the control body 17 to the right or left (in FIG. 1) to the right or left medium pressure control ports 93 below the lines 472 or 473 flows to the medium pressure cylinders 14 or 15, depending on which of the control ports 93 is connecting to the line 472 or to the line 473.
  • the medium-pressure fluid presses up the relevant piston 8 or 9 (in FIG. 1), as a result of which the liquid in the middle chamber 44-46, according to the law of the communicating tubes, pushes the other of the pistons 8 or 9 downward press starts.
  • the control body 17 is provided with the drain control pockets 94 which are located radially opposite the medium pressure control pockets 93. See the control ports 93 and 94 in different rotational positions in the sectional figures 4 to 9, in which the fluid flow directions are also shown by arrows.
  • the backflow flows along the control body 17 through corresponding recesses in the control body 17 to the channels 302 and through them into the channel 301, from which it enters the fluid motor 97 through the inlet 313, it and flows through its swallowing fluid chambers and rotates the rotor with the shaft of the motor 97.
  • the engine 97 can now be a low pressure motor, since the medium pressure fluid flow has used most of its pressure to drive the piston 8 or the piston 9.
  • the fluid motor 97 connected in this way also does not require a high pressure, since it is only intended to deliver the low torque which is required to overcome the friction during the rotation of the control body 17 in order to set and keep the control body 17 in rotation.
  • the hydraulic motor 98 also drives the middle chambers of the fluid delivery pump 486 directly or indirectly via the control body 17 and, if appropriate, an additional gear transmission. This feeds through outlet 485 and through line 485 into the middle chamber 44-46.
  • a pressure limiting valve, overflow valve can be connected to the middle chamber outlet 413 in order to maintain a certain desired maximum pressure in the middle chamber.
  • Such a pressure relief valve available on the market is installed in almost all cases (in FIG. 1) but is not shown in FIG. 1 because such valves are known in the art.
  • the medium pressure limiting or overflow valve 409 (with spring loading or other pressure control 410) was connected (or installed) to the inlet line 408 or to the pump 19 or the line between the two, and the overflowing fluid through the line 412 into the line 301 or into the inlet 313 of the hydraulic motor (control body driving motor) 97.
  • Parts 489, 471 connect the drive shaft 489 to the control body 17 in a rotationally fixed manner, and the parts 469, 470 seal the control body 17 in the control housing 18 axially to the outside, so that no fluid escapes into the open.
  • the control body 17 which is driven by the motor directly or via toothed wheels, also rotates somewhat faster. than was planned.
  • This somewhat faster rotation of the control body 17 then has the consequence that the control orifice 93 closes the channel 472 somewhat too early, namely at a point in time at which the upward-driven piston has not yet completed the full upward stroke.
  • the invention recognizes that the previously unknown conditions shortened the stroke of the pistons and, due to the premature closing of the control ports of the control body 17, the fluid flow supplied to the unit was temporarily forced through the pressure valve 409 (or that of the delivery pump 19) escaping high pressure rise. This gave rise to the previously unrecognized problems and the operational inability of the control arrangement, which the present invention now has to overcome by means of a usable solution.
  • the invention recognizes other causes which have not been recognized to date and which have contributed to the previous inadmissibility. Such are the leakage that flows between the diameter of the piston and the inside diameter of the cylinder wall from the cylinder 14 or 15 into the middle chamber 44-46 during the medium pressure stroke of the piston 8 or 9 going up. Because this increases the volume of the middle chamber even further and thereby drives the piston 8 or 9 running downward even faster, so that the fluid motor 97 rotates even faster, that is to say all the more, too quickly. Another such cause is that radially pressure-balanced control bodies are not stable but rather unstable.
  • control body 17 of FIG. 1 has perfect radial pressure compensation and can therefore also float in the fluid in the housing 18 without friction.
  • the present invention recognizes that they can be perfect, they can even be one hundred percent perfect, but they don't have to be perfect.
  • the invention recognizes that the perfect radial pressure balancing is not stable but rather unstable. Small external influences can shift the control body 17 from the central position into an eccentric position relative to the axis of the bore in which it is fitted.
  • the larger swallowing volume is in the volume size the sum of those volumes which were fed to the engine during half a revolution of the control body 17 beyond the volume of the upward stroke of the piston 8,9 concerned.
  • Qfm The volume supplied to the motor 97 during half a revolution of the control body 17
  • Qdm the volume by which the motor must be built larger per half revolution of the control body 17
  • a second delivery pump is used according to the invention, which is intended to deliver a conveying time loss overcoming fluid flow.
  • This pump can also be driven by the fluid motor 97, for example, if it is not powered by a separate drive. It is advantageous for the universal and simple usability of the high-pressure unit of the invention to drive this second-flow pump (to have a short word for the pump which is to overcome the delivery time losses) directly or indirectly by means of the fluid motor 97.
  • this second-flow pump is 476 and it is indirectly driven by the fluid motor 97 via the control shaft 17 and the gear (toothed wheels) 482, 480, whereby this drives the control body 17 in the manner described via 467-466.
  • the delivery volume of this second delivery pump should be a certain percentage, depending on the construction of the unit, the stroke loss in question "Sc", "Sct”, “Sctt”, “Scttt”, or “Scm”. It is preferred that this percentage e.g. 200 percent is and the delivery pressure of this second delivery pump should be as high as possible twice as the medium pressure of the first, the main delivery pump.
  • "Sct" is Vct x S
  • Sctt is Vctt times S.
  • Sctt times S and Scm is Vcm times S.
  • the second delivery pump delivers its delivery volume in the pressure accumulator 478.
  • a compromise is sometimes made with the costs and the percentages and pressures given above for the second conveyor pump. Then the system works accordingly with lower efficiency or less perfection. But in technology, a compromise between price and perfection often has to be made if the units are to be sold.
  • a second control body namely the auxiliary control body 517 shown in the sectional figures 2 to 9, is arranged.
  • the output 479 of the pressure accumulator, accumulator 478 or 477 of the second delivery pump 477 is connected to the inlet 489 to the auxiliary control body 517.
  • the auxiliary Control body 517 is again directly or indirectly set in rotation by fluid motor 97 and kept in rotation. However, this drive can also be replaced by another drive.
  • the auxiliary control body 517 should take place at the same speed as the control body 17 or at a smaller or larger multiple of this speed.
  • the auxiliary control body again has control ports, namely 491, which are temporarily connected to channels 474 or 475. See FIGS. 1 to 9 for this purpose.
  • the pressure accumulator 478 thus uses the fluid volume obtained from the second delivery pump in order to fill up the stroke loss immediately with the aid of the auxiliary control body 517, that is to say the pistons 8 or 9 upwards to the stroke stroke loss "Sct", the stroke stroke loss "Sct” etc., which was calculated at the beginning to move.
  • the relevant control opening 93 of the control body 17 then opens to the relevant channel 4572 or 473 and begins to drive the relevant piston 8 or 9 to its actual stroke.
  • the cylinders 11, 12 receive their high pressure "Ph" immediately and without any significant loss of time, so that the pistons 11 and 12 alternately bring a constant, uniform delivery as an evenly continuous high-pressure delivery stream in a constant, uniform, constant manner over time, without any intermediate time losses.
  • FIGS. 2 to 9 are self-explanatory, without having to be described, since one immediately sees that the control bodies in the figures have rotated clockwise from top to bottom by 90 degrees. It is also understood from the figures that e.g. 468 and 481 are protective hoods so that the gearboxes are not exposed.
  • the bushings 459,460 have the same axes as the bores in which the pistons 5,6 run in the housing 464.
  • the seals 453, 454 are held in seats formed by different diameters in the housing and in the bushings.
  • the sockets themselves are provided with upper flanges in the upper seats in the housing 464 and in them they form, with the upper end of the housing 463, the flat end surface 463 onto which the valve head 489 is screwed, as a result of which the valve head moves the sleeves 459, 460 upwards in the axial direction held in housing 464.
  • the housing 464 can be made of rusting material, such as cast iron or steel
  • the bushings 459,460 are made of rustproof material if, for example, water is to be pumped in the cylinders 11, 12.
  • the pistons 5, 6 are then also non-rusting material.
  • the pistons 5, 6 can then be VEW stainless steel, Japanese SUS 630 steel or STAVAX or other suitable material, such as occasionally ceramic or sapphier.
  • the bushings are then, for example, bronze, other ceramics or the like.
  • the pistons 5, 6 and the cylinder parts in which they run can have the same diameter with appropriate fits, so that the bushings 459 and 460 can be drilled, honed and lapped simultaneously with the housing 464 in order to achieve high axial alignment.
  • the pistons 5, 6 are then running in an oil film at the bottom but in water between the outside diameters of the pistons and the inside diameters of the cylinder walls. Seals 453 and 454 separate the water from the oil and the oil from the water.
  • the broken lines 492 and 493 are intended to indicate that the seals 453 and 454 can also be made so long that they become longer than the piston strokes, so that a surface part of the pistons 5,6 can never enter water and oil.
  • the collecting chambers 451, 455, 452 and 456 are of great importance because the collecting chambers 451, 452 collect the oil leakage and are provided with the drain line 457, through which the leakage oil is led out of the housing 464, while the collecting chambers 455 and 456 collect the water leakage and pass it through remove the water leakage drain pipe 458 spatially separated from the oil drain pipe 457 out of the housing 464. This ensures that lubricating (oil) and non-lubricating (water) fluids can never be mixed together.
  • this embodiment according to the invention is based on the following consideration:
  • the conventional boosters in Figure 10 use very expensive pistons made of expensive material, such as hard ceramic, Sapphier or the like, or they are sealed by Nerima or other soft, rustproof, lead-like metals in fabric bushings. With the latter method, the seal is also perfect if the fabric bushings are tightened from time to time and refilled with sealing metal. However, such a seal causes high friction.
  • the sealing in FIG. 1 for the pistons 5, 6 in the bushes 459,460 is preferably carried out by simple, tight fitting. In the described embodiment according to FIG.
  • the pistons 5, 6 can also be finely ground so that they can be fitted into the cylinders 11, 12 with a diameter clearance of about 0.010 mm or less. Your friction during the piston stroke is then negligibly small due to the accuracy of the machining. But the leakage in the diameter gap with a radial width of 0.005 mm is very high at the high pressure of thousand to 4000 bar, because the leakage grows parallel to the pressure and the third power of the radial fit gap, or the third power of the diameter difference of the pistons 5,6 and the cylinder 11, 12.
  • the water leakage which is about 40 times greater than that of oil leakage, can be reduced by using a longer sealing gap and the power loss due to leakage at high stroke frequencies and high piston speeds is less than the loss of power due to friction due to Glands seals. There is therefore a speed range in which the simple seal according to FIG. 1 is more efficient than that of some types of sealing of the known technology.
  • the leakage losses are often accepted, because the high-pressure unit of the invention Can be used outdoors, in excavators, vehicles, etc., where no electricity is available for the use of electric motors for the pump drive.
  • the pistons 5, 6 pump oil into the outer chambers 35 in cylinders 11, 12.
  • Each of the pistons 5, 6 serves two such outer chambers 35, one on the right and one on the left of the piston.
  • Water is introduced into the inner chambers 37 with a little pressure, so that it pushes the membranes 58 fully into the outer chambers 35 when the pistons 5, 6 have made their way fully down.
  • the volume of the outer chambers 35 is zero when the membranes are fully pushed in.
  • they must first compress the water in the inner chambers 37 to the left and right of the piston concerned to the “Ph” high pressure by displacing the membranes.
  • the unit can no longer deliver any fluid of 4000 bar if the diameter difference becomes 0.04 mm. It would be excellent with the diameter difference of o, oo5 mm. However, this is difficult and can only be achieved with expensive fine ceramics, sapphires, etc.
  • FIG. 13 A further improvement of the high pressure control according to the invention is illustrated in FIG. 13 and its sectional figures 14 to 17 in longitudinal and cross sections.
  • FIG. 13 shows again the cylinders 14 and 15 with the pistons 8 and 9 reciprocating in them, and the middle chamber 44-46.
  • these parts and also the new control arrangement according to the invention are accommodated in the housing 418 and the cylinders 14, 15 are closed by the bottom cover 512, 513. (The closure can also be done differently).
  • the most important figure is the figure 14 because it shows all control means in a single section, that along the arrowed line XIV-XIV of figure 13.
  • the cylinders 14 and 15 can be seen in cross section here, the high-pressure cylinders 11, 12 are shown in broken lines because they are not directly visible.
  • the housing 418 has the two cylindrical bores 510, 511, in which the control slides 417 and 617 fit tightly and are axially movable. The drive for the axial movement takes place via the already described motor 97 via parts 500 to 509.
  • the control slide 417 forms the main control, namely that for the medium pressure flow from line 408.
  • the slide 617 forms the second flow control, namely the control of the fluid flow the second delivery pump 484 (FIG. 1), which passes through line 489 to bore 511.
  • Control spool 417 has three fits, 497,498 and 499 with recesses for fluid flows in between.
  • Control spool 617 has only two fits 495 and 496 with only one recess for fluid flow therebetween.
  • the control spool 417 alternately connects the channel 408 with the channel 472 and the channel 473, so that the medium pressure of the driving fluid alternately into the cylinder 14, then into the cylinder 15 and then back into the cylinder 14 is directed.
  • the easily controllable backflow is not shown in the figure.
  • the reverse fluid streams from the cylinders 14 and 15 flow again through the lines (channels) 302, 301 and motor inlet 313 into the fluid motor 97 in order to set its shaft in rotation and to keep it in constant rotation.
  • the auxiliary control slide 617 which fulfills the purpose of the auxiliary control body 517 of FIGS. 2 to 9, is shown in its right position in FIG. 14. It connects the auxiliary fluid supply line 489 with the channel 475 to the cylinder 15. If the control slide 671 is moved to its left end position, it connects the supply line 489 with the channel 474 to the cylinder 14.
  • the fluid motor 97 drives the shaft 500 with its shaft, which is shown in FIG. 14 as being mounted in the housing 418.
  • the disc 501 which is connected to the shaft 500 in a rotationally fixed manner, can be seen at the bottom.
  • This tread is encompassed by the right eye 507 of the connecting rod 503, while the left eye 506 of the connecting rod 503 is connected by means of a pin 504 to the connection 505 of the main control spool 417.
  • the eccentric 501 thus moves the main slide 417 once to the left in the end position and once to the right in the end position.
  • this control slide is in the middle position because the eccentric (FIG. 17) is rotated ninety degrees to the axis of the control slide 417. (Caution, not exactly exactly 90 degrees, because at exactly 90 degrees the control slide is not exactly in the middle position. Where it is exactly at which angular position of the eccentric 503 can be found in DE OS 38 21 617 by the inventor.
  • FIGS. 16 and 17 are sections through FIG. 14 along the arrowed lines XVI-XVI and XVII-XVII.
  • cam 502 on the shaft 500 can see that these two parts revolve in a window 523.
  • the window forms the surfaces 524 and 525 on the connecting part 508, 509 of the auxiliary control slide 617. If the cam 502 hits the wall surface 525 of the part 509 while the shaft 500 rotates, then the slide 617 is moved to the right. If the cam 502 strikes the surface 524 while it is rotating, then the slide 617 is moved to the left. In FIG. 16, cam 502 points straight to the right, but in practice it is rotated a few degrees to achieve the correct opening times, or eccentric disk 501 is rotated somewhat back relative to cam 502.
  • the wall surfaces 524, 525 are not designed to be flat (as in FIG. 16) but rather double-bellied or curved, for example as indicated by the dashed line 526 in FIG. 16.
  • main control slide and the channels 473, 473 are also indicated in FIG. 13, at least in places, partly by cutting
  • This simple solution according to FIGS. 13 to 17 has a special purpose according to the invention.
  • it moves the main control spool very quickly when overflowing via the inlet channel 408, while the main control spool 417 remains in its end positions for a relatively long time and thus offers large flow cross sections for a long time.
  • FIG. 15 shows the cross section through FIG. 14 along the arrowed line XV-XV and only for the sake of completeness.
  • the period of the expansion process prevents the full filling of the cylinder 15 that is subsequently operating. Because the engine 97 is temporarily rotating too fast, the time of the inflow of the fluid to the cylinder subsequently operating is corresponding shortened. As a result of this shortening of the time of connection of the fluid supply to the corresponding cylinder, the amount of fluid supplied to the relevant cylinder is reduced because the supply time has been shortened.
  • the present invention therefore arranges a control valve 550 in a fluid line 558 from the first cylinder 14 to the second cylinder 15 in FIG.
  • This control valve 550 is opened at the time of completing the pumping of one of the piston sets.
  • the volume of expansion of one piston set flows into the cylinder of the other set, namely through line 558 and valve 550, until pressure equilibrium is established in both cylinders 14 and 15.
  • the valve 550 is closed immediately.
  • Figure 17 ' shows approximately the scale of the pressure over the circumferential angle "alpha" of the fluid motor 97, namely Figure 17' shows the pressure curve in the cylinders above the high pressure pistons 5 and 6 for different pressures.
  • This figure shows with the words: “expansion” the expansion process, with “compression” the compression process “and with” filling "the effect of the second measure of the invention, which will be described later in this application.
  • The” expansion “and” Compression “lines in FIG. 17 ′ are dashed lines because they show what the pressure curve is without the arrangements of the present invention.
  • FIG. 18-A shows the pressure curve in the cylinders 14 and 15, the pressure peaks 560 being the overflow through the pressure relief valve 409 of FIG. 1 of the main application.
  • FIG. 18-8 shows the pressure in the middle chamber 44-46 of the main application and of FIG. 15, the pressure peaks 661 showing the overflow through the pressure relief valve on line 413 of FIG. 1 of the main application.
  • Their unusual height comes from the excessive hardness of the pressure relief valve used.
  • Figure 18-C shows the pressure curve of the high-pressure delivery from the chambers above the pistons 5 and 6. These curves would therefore have to dashed lines, but then at the top fully drawn lines correspond to FIG. 17. It should be borne in mind that different scales are used for the ordinates of FIG. 18 in the automatic print recorder because the prints are too different to be written on the same scale.
  • the second and third measures of the invention therefore have the task of filling the loss areas of FIG. 17 labeled "filling" to full pressure or partially fulfilling this task.
  • an auxiliary pump 551 is arranged (FIG. 16), which supplies excess pressure or high pressure fluid to a pressure accumulator 552. (Fig.15).
  • This has lines 555 and 556 to the cylinders 14 and 15 and is also provided with a controller 553.
  • the auxiliary pump 551 supplies the pressure fluid into the inlet 554 of the pressure accumulator or the controller 552 or 553.
  • the control opens the pressure accumulator to the relevant cylinder 14 or 15 and closes it again at the circumferential angle at which the curve "M" in question reaches the high pressure line "D" (in FIG. 17).
  • the third measure of the invention is that a line 559 (FIG. 16) is set from the return fluid line 302, 301 to the input of the auxiliary pump 551. Because this means that the auxiliary pump 551 does not take its fluid delivery volume from a tank, as in previous patent applications by the inventor, but is forced to take it from the return fluid line 301, 302 to the fluid motor 97.
  • the fluid of the auxiliary pump is now removed from the fluid flow to the fluid motor 551.
  • This measure of the invention thus forces the fluid motor 97 to rotate more slowly precisely at the time which would be used for the rest of the compression process.
  • the "filling”, ie the supply of the fluid from the auxiliary pump 551 or from the pressure accumulator 552 into the relevant cylinder 14 or 15, can take place suddenly or quickly.
  • the invention achieves an almost uniform conveyance according to line "D" in FIG. 17 over the entire cycle from 0 to 360 degrees. More precisely, should be achieved approximately, because in technology you have losses in many places and the practice is never quite as perfect and fast as the theory.
  • FIG. 19 is a section through a three-piston high-pressure pump, as is widespread on the market. These pumps were offered with up to 700 bar a decade ago, but recently such pumps can also be found in the catalogs of specialist companies for up to 2,500 bar.
  • the crankshaft with its three eccentric bearings 571 to 573 is supported all round.
  • the driving piston 576 is moved back and forth in the cylinder 575 via the connecting rod 584 in question, that is to say reciprocally.
  • This piston is connected by means of the connection 577 to the high-pressure piston 578, which is sealed in the high-pressure cylinder 580 by means of a material sleeve filling 579. Due to its reciprocal movement, fluid, in particular water, is admitted into the high-pressure chamber via the inlet valve 582 and is conveyed out of the pump via the outlet valve 583 during the pressure stroke.
  • FIG. 20 therefore shows Eickmann's calculation formulas for the strokes and the speeds of such pumps driven by crankshafts.
  • the corresponding calculation forms from Rotary Engine Kenkyusho can be found below the sketch and formulas.
  • the first realization of the present invention is therefore that these three-plunger pumps cannot deliver an even water jet, but the amount that flows through the water nozzle fluctuates by over 20 percent. When water jet cutting, these pumps can therefore not deliver a uniform cut.
  • a pipe 585 from the pump 570 to the nozzle 586 is therefore shown in FIG.
  • the behavior of this pipe is then calculated in the calculation form below.
  • the calculation brings the internal stresses in the pipe and the radial expansion of the pipe under the high internal pressure.
  • the penultimate column on the right shows the cubic centimeters that a tube of this type can hold by one meter in length due to expansion under internal pressure. From this one finds that a very long pipeline acts like an accumulator, i.e. like a pressure accumulator.
  • FIG. 23 shows that thin-walled tubes cannot be used for high pressures. In the case of the thick-walled tubes, however, the accumulator effect is only about 0.1 cubic centimeters with one meter of tube length. There are limits to the use of the tubes as accumulators.
  • FIG. 25 therefore shows the pressure booster or the high-pressure pump of the known technology.
  • the parts described with reference to FIG. 25 can also be found in the following figures, but the reference numbers are not shown in the subsequent figures because they are known from FIG. 25.
  • pressure oil is passed through the pump 612, which is driven by the electric motor 611, for example, to a reversing slide 614, which is usually automatically operated by magnets, that is to say the fluid flow direction is passed alternately via the lines 615, 616 to the units 601 and 602.
  • These units have medium pressure cylinders 603, 604, which are filled with the pressure oil and in which the pressure oil drives the medium pressure pistons 605 and 606.
  • the piston in question must first cover the described 12 to 18 (or more) percent of its way until the fluid in the high-pressure cylinder has reached the delivery pressure.
  • the pressure in the high pressure cylinder rises approximately evenly over the path, as shown in the time (t) - pressure (p) diagram on the right side of the figure.
  • This compression of the fluid is a loss, the size of which is shown in the squares under the time-pressure curve.
  • the aggregate still has medium pressure in the medium pressure cylinder and at least high pressure in the dead space. Therefore, these pressures relax through the reversing slide "S" back into the tank. This relaxation of the medium pressure and high pressure fluids is in turn a loss. It is shown in its size under the loss of compression by the vertical rectangles in Figure 25.
  • FIG. 26 therefore shows how the high-pressure pump of the known technology according to FIG. 25 improves and completes the present invention can be come.
  • the return lines 617 and 618 are therefore connected backwards from one another to a line 619 according to FIG. This leads to the tank, but a one-way check valve 620 is switched on in line 619.
  • the fluid expanding from one of the units during the reversal cannot therefore flow back into the tank because the one-way valve 620 blocks the way to the tank.
  • Line 619 can be filled through valve 620, but no fluid leaves lines 617, 618 in the tank.
  • the (expanding) fluid that relaxes from the one unit (601 or 602) is forced to flow into the medium-pressure cylinder of the other of the units, which at this point in time has the pressure "zero". 26
  • the expansion fluid becomes the pre-compression fluid for the cylinder of the other one of the units that is working afterwards.
  • the other of the aggregates is thus immediately brought from zero pressure to an average pressure of slightly below half the high delivery pressure. (Losses in lines and in the reversing valve are not taken into account when considering this principle.)
  • Figure 27 therefore shows how one can completely overcome the conveyor unevenness. The applicant is currently not aware of whether such means, as described in FIG. 27, have already been used in technology or whether they are a new invention.
  • the complete uniformity of the delivery is achieved by using two pumps and two control slides.
  • Each of the units 601 and 602 receives its own pump (here with its own electric motor drive) and its own reversing slide. This makes it possible to initiate the changeover before the conveyance of the previously working unit (601 or 602) has been completed. More precisely, the changeover is initiated so early for the aggregate working afterwards (601 or 602) that the compression of the fluids in the aggregate working afterwards has ended at exactly the point in time when the aggregate (601 or 602) previously working has completed the delivery due to the end of the piston stroke). So you get a completely constant, uniform conveyor curve in the time-pressure diagram in the right half of Figure 27. On the other hand, the compression and the expansion losses of Figure 25 are fully available.
  • FIG. 27 Another new additional loss is represented by thin long rectangles, namely the electrical drive power for the second electric motor plus the losses due to unpressurized (low-pressure) flow of the amount of oil fluid pumped by the non-pressing pump.
  • the figure shows rectangles lying one above the other, which is to say that both the additional electromotive drive power, that is to say the losses due to friction, deflections of the fluid and friction in the pump, occur as losses.
  • FIG. 28 two controllable pumps, designated “PV”, are therefore used in accordance with the invention.
  • PV controllable pumps
  • the losses in the reversing slide are overcome first because the reversing slide continues.
  • friction losses due to fluid flow in lines are overcome because the lines can be shorter.
  • the compression losses remain and the drive power of the two electric motors remains. You can see this under the time-pressure diagram on the right side of Figure 28.
  • FIG. 29 of the invention two controllable and reversible pumps 642 and 643 are driven by the electric motors 632 and 633 and one of the pumps is used to operate the unit 601, the other to operate the unit 602. Since the pumps are reversible, the pumps act as motors as long as the expansion fluid flows into them. The expansion fluid is therefore not lost, at least not entirely. The compression losses and the drive losses of the pumps and electric motors which temporarily do not supply pressure remain as losses. These losses are shown in the right side of the figure again under the time-pressure diagram.
  • FIG. 30 An IDEPU pump, for example according to the inventor's US Patent 3,805,675, is used here.
  • the second electric motor of FIG. 29 with its losses is thereby saved.
  • the rotor of the pump has two piston groups in the common rotor, each of the piston groups having a piston stroke control that is independent of the other and reversible.
  • the lines 647, 648 from the IDEPU pump 644 to the units 601 and 602 can be short and the flow heating is not disturbed by deflections in the control slide.
  • the IDEPU pump has a one-way valve 619 in its suction line 646 for both chamber groups, which prevents fluid from flowing back into the tank. Since the circuit is then a closed one, the cooler 621 according to FIG. 26 is expediently used.
  • the piston groups When one of the piston groups is on conveyors, the other can be on inlet so that the expansion fluid from one aggregate in the same rotor can act as a motor for the partial compression of the other of the aggregates 601, 602. By moving the compression forward, the conveying curve can again achieve complete uniformity, as in FIGS. 27 to 29. Since the second electric motor is saved, this embodiment according to the invention works more efficiently than that with two electric motors, but without any additional disadvantages.
  • FIG. 31 shows the double-acting axial booster of the known technology.
  • the high-pressure pistons and cylinders 607 to 610 are designed as in FIG. 25 and so are the inlet and outlet valves.
  • the pump 612 and the control slide 614 are, as shown in FIG. 25.
  • the medium-pressure piston is a single piston 650, which reciprocates in the cylinder with the cylinder subchambers 651 and 652, specifically under the medium pressure obtained from the pump via the control slide.
  • FIG. 32 shows an embodiment according to the invention for the operation of double-piston axial boosters.
  • the drive unit 611 drives a controllable and reversible pump 653 and also a small high-pressure pump 658 with a small delivery quantity.
  • the controllable pump has an inlet and an outlet line 654.655. Since the pump is reversible, the fluid flow direction can be reversed so that the inlet pipe becomes the outlet pipe and vice versa.
  • Each of the lines 654 and 655 therefore also has, according to the invention, a one-way valve 6.56 or 657 for preventing fluid flow back to the tank. Because of the now closed circuit (because of the now closed circuits), oil coolers 621 are expediently assigned to the lines.
  • each of the lines 654 and 655 is connected to an individual pressure accumulator 659 and 660, respectively.
  • These accumulators are either filled through lines 654 or 655 or else through the small high-pressure pump 658 with its small delivery quantity. This small delivery quantity and the content of the tensioned pressure accumulator are sufficient to fill the delivery conveyor at the time of the changeover (reversing the delivery direction of the pump).
  • FIG. 33 shows that the cylinder sets of FIGS. 25 to 30 can also be arranged rotated by 180 degrees. However, it is important that the valve sets 582, 583 remain spatially separated from one another and that a partition 670 is arranged between the high-pressure cylinders 609 and 610. However, a common inlet line 671 can then be arranged upstream of the inlet valves 582 and a common drain line 672 can then be arranged behind the outlet valves in a simple and flow-efficient manner.
  • FIG. 34 shows that the cylinder sets can also be arranged side by side in parallel. Then there is the structural advantage that the middle chambers between the piston and cylinder parts can easily be connected by a line 673. This construction principle is also used in the EREW pumps of the invention.
  • the middle chambers form a common middle chamber with the inlet 674 for the introduction of the low-pressure fluid for the automatic return of the pistons after the end of the pressure stroke.
  • an object of the invention is also to create a dead space-free aggregate.
  • the high-pressure piston or generally the piston 606 reciprocates again in the cylinder block 601. It can also be a low-pressure piston, because the principle of the invention in FIG. 35 can generally be used.
  • the invention consists in that the valves form a common surface, in this case a flat surface, 683 for the cylinder, which is created by the end faces of the valves.
  • the valves have, for example, conical seats, the inlet valve being seated in the outlet valve according to the invention.
  • the exhaust valve has an inclined valve seat 686 in the cylinder head.
  • the inlet duct 689 is formed, which is provided with the inlet connection 690.
  • the outlet valve 682 can also be guided in the guide 687 of the housing and it is conveniently pressed with a spring 689 'against the valve seat 686.
  • the inlet valve 681 has an inclined inward direction from the end face, the seat in the outlet valve, the valve seat 685.
  • the valve stem 681 'extends and it can also be guided in the guide 691, the guide simultaneously being one of the bearings of the Suspension 692 can form, while the tension of the spring at the other end can be done by the bracket 693.
  • the inlet 694 or 695 to the inlet valve is also arranged in the valve housing. In the figure, the inlet valve opens by moving downwards, that is down out of the seat in the exhaust valve. The outlet valve opens upwards (in the figure) by lifting it up from the seat in the housing.
  • the intake valve opens by moving downward (against the weakly tensioned spring 692).
  • the spring 692 presses the intake valve upward into the seat in the exhaust valve and thus closes the inlet by closing the seat 685 by sealingly entering the seat.
  • the pressure stroke of piston 606 begins by moving upward and compressing the fluid in the cylinder.
  • the (slight) overpressure presses against the end face of the outlet valve 682 and lifts it upwards from the seat 686 by compressing the spring 689 '.
  • the outlet is now open by lifting the valve off the seat.
  • the inlet valve Since the inlet valve is located in the outlet valve, the inlet valve takes part in the movement of the outlet valve, but without opening the inlet, because the inlet valve remains firmly in the seat in the outlet valve during the outlet operation and keeps the inlet closed.
  • the guide 687 also serves to seal the low pressure inlet to the high pressure outlet.
  • the end faces of the valves 681, 682 form a common plane and because the head of the piston is flat, the end faces of the valves 681, 682 and the piston 606 are faces which are parallel to one another.
  • the piston can be brought so close to the valves that only the space 684 remains between the end face of the piston and the end faces of the valves.
  • the piston is stroked so close to the valves that the distance between the end faces of the valves and the end face of the piston is less than one millimeter, with precise high-pressure pumps of several thousand bar, only less than 0.1 mm. The dead space is then limited to the piston cross section times 0.1 mm.
  • FIGS. 36 to 39 illustrate how the difficulties of sealing the high-pressure water pistons of FIG. 19 can be overcome and their leakage can be completely eliminated by dismantling the water pistons of the known technology and using units of this invention or units of the other patent applications of the Inventor replaced.
  • FIG. 36 therefore shows the RATEW system assigned to piston 706 on the right in the figure.
  • the conical ring elements 707 to 709 are arranged between the head with the valves 702, 702 and the reciprocating piston 706 in such a way that they form between the water-containing inner chamber 701.
  • This system is called “RATEW” and is characterized in that the piston 706 relaxes the conical ring elements for water absorption and compresses the conical ring elements for water supply under pressure, thereby reducing the size of the inner chamber and thus pushing high pressure water out of the inner chamber 701 via the outlet valve.
  • the basics of this system can be found in RER reports and in the US patents that have been granted in the meantime, as well as in the German and European Patent Office publications.
  • the RATEW arrangement is accommodated in the housing 700 and the spring 704 and its holder 705, for example, are assigned to the outlet valve.
  • FIG. 37 shows the inventor's ETEW system in housing 712.
  • the piston 706 of smaller diameter pumps hydraulic fluid into a cylinder 710 of larger diameter and thus presses against piston 711 of larger diameter (reciprocable in cylinder 710), while piston 711 of the larger diameter Compression of the conical ring elements 708-709 and thus the inner chamber 701 already described in the figure 36 causes.
  • FIG. 38 shows in the housing 713 the EPEW system of the inventor, which is characterized in that the reciprocating piston 706 supplies hydraulic fluid into an outer chamber 714 formed in the housing 713, which is separated from the inner chamber 701 by axially deformable ring elements 716. Since the pressure in the outer chamber then corresponds to or slightly exceeds that of the inner chamber, the ring elements can be thin-walled with long strokes. In addition, the neighboring ring elements can mutually seal themselves according to the inventor's patent applications.
  • FIG. 39 illustrates the inventor's MEPEW system, which differs from the EPEW system of FIG. 38 in that it has two inner chambers 721 and 722, which are separated from the two outer chambers 719, 720 by membranes “M”, and which is also characterized thereby that a single piston 706 is used in the high-pressure cylinder 717 for the joint filling and emptying of the two outer chambers 719 and 720.
  • FIGS. 36 to 39 are indicated in the figures on the crank drive of the known three-piston pumps, and so they can be used.
  • Each of the RATEW, ETEW, EPEW and MEPEW systems has seals between surfaces that do not move relative to each other, so that the piston movement under water pressure is overcome by the known technology of axial boosters and three-piston pumps.
  • the invention systems are mounted on the crankshaft connecting rod drives of the three-piston pumps. You can do that, but mostly eccentric drives are used in the RATEW, ETEW, EPEW and MEPEW systems, because the crankshafts and connecting rods can often not deliver the high forces required to drive the piston for several thousand bars.
  • FIGS. 40 and 41 therefore show a new radial piston high-pressure pump according to the invention, FIG. 40 being the longitudinal section through the pump and FIG. 41 being a cross section through FIG. 40 along the arrowed line in FIG. 40.
  • the shaft 751 is rotatably supported in bearings 752 and provided with three eccentrics 753 to 755, which are angularly offset from each other by 120 degrees. Radially to the center of these eccentrics are three cylinders with pistons reciprocated therein, which are in turn offset by 120 degrees to each other. Swiveling piston shoes 756 for power transmission are arranged between the eccentric but cylindrical outer surfaces, the piston stroke guide surfaces of the eccentrics mentioned and the pistons in question. So you have three groups of cylinders, three axially Plates arranged one behind the other can be accommodated, each of the cylinder groups containing three cylinders with pistons reciprocated therein.
  • the pump according to these figures can also be used for the conventional piston system of the axial booster and the conventional three-piston pumps.
  • the described RATEW, ETEW and EPEW systems can also be used in these figures. Since the eccentrics are rotated by 120 degrees relative to one another, the pump operates with the same delivery rate as the nine-piston pumps, according to FIG. 24. In FIG.
  • figure 42 For the axial construction of high pressure pistons with several pistons in cylinders for several thousand bar water pressure, one finds the figure 42, which can be a five, seven, nine, eleven, or more piston pump.
  • the shaft 763 with its rotors 764 and 765 is rotatably supported in the housing 762, the bearings 771 also having to absorb high axial forces (in the case of small pumps around 30,000 kilograms).
  • the plurality of approximately axially directed cylinders 769 of larger diameter with the pistons 767 of larger diameter reciprocating therein are located in rotor 764.
  • the same number of cylinders 770 and pistons 768 of smaller diameter are located in the rotor 765.
  • the cylinders of smaller diameter also serve to convey non-lubricating fluid, such as water, while the piston of larger diameter is wetted by lubricating fluid (eg oil).
  • the pistons of larger diameter are offset radially further outwards, relative to the axes of the pistons of the smaller diameter, and the pistons of larger diameter are there to have space for pivoting pistons order shoes 789 for power transmission.
  • the lifting disc with the inclined piston stroke guide surface 790, on which the end faces of the piston shoes 798 run, is arranged in the housing. As a result, due to the inclined position of the piston stroke guide surface per revolution of the rotors, the pistons are moved in once and out once (to the right or to the left in the figure).
  • the system is provided with oil lines 777.778 and can be provided with pressure fluid pockets 781.781 'and 779 to form hydrostatic bearings.
  • the high-pressure pistons of the small diameter rest on the rear end faces of the pistons of the larger diameter.
  • the piston shoes grip around with their sleeves 789 in places the swivel-shaped heads 788 of the pistons of the larger diameter.
  • Retraction plate 780 pulls the larger diameter pistons out of their cylinders.
  • the smaller pistons are pressed against the end faces of the pistons of the larger diameter by pre-pressure. If you don't have a pre-pressure available, you can connect the small pistons radially to the large pistons.
  • the fluid leakage separating rotor 782 is advantageously arranged, through which the small or the large pistons can be sealed by seals 791, 792. In this way, the leaks are thrown outwards and the different fluids, such as the water and the oil, are collected in spatially separated chambers 783, 784 and discharged into the fluid containers.
  • the pistons of the larger diameter are exclusively driving pistons for the pistons of the smaller diameter in this figure, without the pistons of the larger diameter producing oil or other fluids.
  • the cylinders of the larger diameter are accordingly not cylinders closed at one end, but rather bores extending axially through the rotor.
  • the pressure chambers 774 are arranged in the rear cover or housing part; which can also be a single one. Pressure oil, which presses on the rear end of shaft 763, is advantageously passed into it.
  • the diameter of the rear end of the shaft together with the pressure in chamber 774 determine the force with which the shaft is pressed against front bearings 771 when chamber 74 is sealed by fitting the shaft end.
  • the fluid supply line 786 and the fluid discharge line 785 which can also be designed to act vice versa. They direct the water the pressing arrangements 773 of the control body. 772 or away from them.
  • the control body is provided with inlet and outlet channels and openings 792, 793 and its end face is pressed against the rear end face of the 785 rotor.
  • the control body can be one according to the FRG patents 2,300,639 or 2,324,563 or according to the FRG patent application P 38 38 284.9.
  • these control bodies have to be calculated and dimensioned differently than in the literature mentioned. Because the contact pressure of the control body must be absolutely limited to the pure sealing force, while all other forces, including those resulting from friction, have to be absorbed or handled by the pressure chamber 774 with seal 791. The correct dimensioning of the control part of the invention is therefore very important and it can be taken from the corresponding RER reports by organizations that acquire licenses.
  • Figure 42 accomplishes two important objects of the invention. At one point it can have nine pistons and thus achieve the conveyor uniformity of Figure 24. The conveying uniformity is extremely important for a precise water jet cutting technique.
  • this figure of the invention fulfills an even more important object of the invention, namely the dream so far of achieving long-term service life.
  • the service life of the high-pressure units was limited by the valves, which worked like Haemmer by lifting and putting them on their seats. Because the invention eliminates the valves according to FIG. 42, it also eliminates their limitation of the service life of the high-pressure units for water.
  • ceramic rotors 765 with ceramic pistons 769 and ceramic control bodies 772 can have an unlimited service life because they do not pound, but only slide if you have mastered the calculation and dimensioning of the control bodies 772, the pressure arrangement 773 and the pressure chamber with seal 774.791. But these things are not easy. With 9 pistons of 8 mm diameter on a pitch circle diameter of 40 mm, you are already dealing with forces of thirty thousand kilograms if the water level is to demand four thousand kg / cm2. In this respect, it is useful to use the experience of the inventor from forty years of activity in the field and one has to consider that such developments also cost and cost money.
  • Figure 43 is taken from it and shows the compressibility of water and oil.
  • the one for oil corresponds approximately to the information in the book by Chaimowitsch “Die Oelhydraulik” (VEB Verlagtechnik, Berlin, 1960) and the one for water is taken from the book “Huette, the engineers paperback”. Missing data are estimated.
  • the curves show the percentage compression of the oil (upper curve) (medium oil at 40 degrees Celsius) and the water (at 30 degrees Celsius) (lower curve).
  • the medium-pressure piston has a diameter of 80 mm, while the high-pressure piston has a diameter of 28 mm.
  • the piston stroke should be 42 mm (approximately).
  • valves of FIG. 19 are arranged in FIG. 25, resulting in a dead space of 18 mm in length and 29 mm in diameter (the space around the valves is connected to the high-pressure cylinder 609 or 610).
  • the medium pressure (oil) to be conducted into the cylinder 603 or 604 can be regulated from zero to 700 kg / cm2.
  • the factors used are the percentages of FIG. 43 divided by 100 in order to be able to calculate directly.
  • the high-pressure piston only makes a displacement of 6.16 CC per centimeter (namely the 616 mm3 according to the above calculation).
  • the axial booster of the known technology according to FIG. 25 therefore has a loss of 17.20 percent of the time of a piston stroke until it can reach the full delivery pressure of 4000 bar.
  • the well-known booster has no water supply. No water comes out of the pump. Such a high loss makes precise water jet cutting impossible.
  • the described losses due to compression and expansion are even higher in the EREW system of the invention than in the known technique described in FIG. 25, because oil is also compressed and expanded under high pressure. Nevertheless, the EREW systems of the invention are advantageous because they are structurally simple, do not require the sealing of pistons against water, and also because the EREW system of the invention uses means to largely shape the losses due to compression and expansion so that they do not, or little, negatively affect the uniformity of the promotion.
  • FIG. 44 shows the calculated time diagrams for the comparison of the above consideration of FIG. 25.
  • FIG. 46 shows the beginning of the compression stroke
  • FIG. 45 basically shows the beginning of the return stroke of the piston.
  • the control body connects the medium pressure line "HP" to the cylinder and directs the medium pressure fluid under the piston so that the piston can begin the pressure stroke but has not yet started it. Therefore, in Figure 46, the membrane "M” is still close to the lower stroke boundary wall. The entire displacement around the membrane is now still an inner chamber and filled with water. With the water at low pressure after the water inlet hub has been closed. The cylinder above the piston now forms the rest of the outer chamber.
  • the inlet valve is labeled "JV”
  • the outlet valve is labeled "OV”.
  • the motor drives the rotation of the Tax body.
  • the piston has ended the pressure stroke, so that the membrane "M” has been pressed fully up against the upper boundary wall.
  • the inner chamber became “zero” in volume because the water was fully pumped out of the inner chamber via the outlet valve.
  • the control body connects the cylinder space under the piston with the engine.
  • the water inlet pressure (or other means) then moves the piston downward so that the piston directs the low pressure fluid from the cylinder under the piston to the engine, causing the engine to rotate and thereby keeping the control body being driven in rotation.
  • the working space of the diaphragm "M” is now the space under the diaphragm and it is now the outer chamber, because it is still full of oil, which just gives you the freedom to relax through the channel in the control body and into the engine.
  • FIG. 45 also shows the dead spaces connected to the inner chamber and to the outer chamber.
  • the dead spaces connected to the inner chamber are those filled with water, formed around the valves and labeled "Dw”.
  • the dead spaces connected to the outer chamber are those filled with oil and labeled "Doil”.
  • Each high-pressure piston of this 1988 EREW version has a diameter of 28 mm and a stroke of 42 mm.
  • the dead spaces just mentioned are those of the two high-pressure piston arrangements of the EREW together.
  • Each individual high-pressure piston therefore includes half of the above dead space volume (1988 EREW version, as built and tested)
  • both high-pressure pistons with their surroundings and dead spaces are also considered below with regard to the EREW system according to the invention.
  • the same piston diameters and the same strokes are therefore used in order to be able to compare the known technology with the EREW system of the invention.
  • Figure 47 is a schematic representation of the EREW system in its simplest form, but with all organs used or required. Since all organs are shown in one plane of the sheet of the figure, the figure is not to scale, but illustrates the principle in such a way that later all details are referred to can be expected. However, only one of the two piston sets used in the current EREW is shown.
  • the separating membrane can be seen in its neutral central position, so that one can see the outer chamber "OC” to the right of the membrane “M” and the inner chamber “IC” to the left of it.
  • the inner chamber is connected to the inlet valve “IV” and to the outlet valve “OV”.
  • a backing pump “WpS” conveys water under low pressure of 5 to 20 bar to the inlet valve “IV” and over it into the inner chamber to push the diaphragm "M" to the right if this is possible. If you have high pressure in the water pipe connected to the EPEW, the backing pump "WpS" can be omitted if necessary.
  • the high-pressure piston "HPK” has the task of directing oil against the diaphragm “M” and thereby pushing the water out of the inner chamber with high pressure through the outlet valve. So that he can do this, the medium pressure piston “MPK” is assigned to him or forms a piston set with him. Because the EREW is only supplied with medium pressure oil. Once the inner chamber has filled up with water, the diaphragm “M” has been pushed all the way to the right up to the right stroke delimitation wall and the entire working area is then the inner chamber (left of the diaphragm).
  • the diaphragm "M” is pressed fully to the left up to the left boundary wall and all space is now on the right of the diaphragm and the outer chamber then filled with oil.
  • the stroke volume of the diaphragm during the stroke from right to left and from left to right corresponds to the stroke volume of the high pressure piston "HPK” (in principle, if corrections are not taken into account).
  • the EREW is usually connected to a medium pressure oil pump “MpS" available at the place of work. However, since FIG. 47 is intended to show everything, this medium-pressure pump “MpS” is shown in the EREW arrangement in FIG.
  • FIG. 47 shows the control body in the position in which the control pocket connects the medium pressure fluid supply to the cylinder “MPC”, in which the medium pressure piston “MPK” reciprocates.
  • the other control pocket of the control body “CV” connects the medium pressure cylinder “MPC” to the engine “D” and then directs the low pressure fluid when the piston "MPC” returns to the engine “D” to drive it.
  • the EREW has two sets of cylinders and sets of pistons, one of them is for each engine “D” "D” and the other connected to the medium pressure fluid supply “MpS” so that one of the piston sets makes the pressure stroke and the other of the piston sets makes the return stroke at the same time when the unit is properly built.
  • the figure also shows the low pressure pump “LpS” which is the filling pump for the middle chamber "MC”. Because if there is no fluid in the middle chamber above the piston "MPK", the piston set is not pulled back down. The middle chamber is connected by a line to the middle chamber of the other piston set. so that you have practically only one middle chamber in the EREW.
  • the filling pump "LpS” only requires very little oil and is actually only needed to start the EREW, because the leakage along the high pressure piston “HPK” will be greater than the leakage along the medium pressure piston “MPK”, so that the middle chamber fill itself with oil once the EREW has started.
  • the middle chamber “MC” must be provided with a pressure relief valve “R” so that the pressure in it never gets too high. It must always be lower than the water inlet pressure. From the middle chamber the line “L” goes to the inlet valve "B” above the high pressure cylinder "HPC". The valve “B” only opens if there is a lack of oil in the high pressure cylinder "HPC". Beware of clever engineers. Because the valves are all expandable and installable.
  • the workflow is as follows:
  • the inner chamber “IC” reaches its largest volume, which again corresponds to the delivery volume of the piston "HPK”.
  • the control body "CV” connects the medium pressure supply to the cylinder “MPC”.
  • the medium pressure fluid presses the piston set upwards with the constant speed of the medium pressure pump (or medium pressure supply) "MpS”.
  • the control body closes the connection of the medium pressure cylinder “MPC” to the medium pressure fluid supply "MpS” and connects the cylinder “MPC” to the line to the engine “D". Since the motor is resistant to the rotation, the pressure in the line to the motor “D” is lower than the pressure in the middle chamber "MC”. So the middle chamber, together with the water inlet pressure “WpS”, drives the piston set down and the fluid now flowing to the cylinder “MPC” to the engine “D” keeps the engine “D” and thus the control body "CV” driven by it in rotation. At this time, the second piston set of the EREW carries out the pressure stroke upwards, which was previously described for the piston set shown in the figure.
  • the two piston sets 1 and 2 are shown schematically in FIG. 48. Each piston set works in the DEPEW system against two "M” membranes.
  • the control body "CV” alternately operates both sets of cylinders one after the other. You can now first make the milk girl calculation that the piston sets 1 and 2 run at the same speeds, because the MPK pistons 1 and 2 both have 80 mm diameter in the calculation example and the HPK 1 and HPK 2 pistons have the 28 mm diameter of the calculation example.
  • the medium pressure line is conveyed by the MpS, for example 60 ltr / min, i.e. 1 liter per second, then the inflow of medium pressure oil is 1000 CC per second.
  • the working chamber in which the membrane "M" is arranged must therefore have a volume of 25.86 CC.
  • Both working chambers together must have a content of 51.76 Cc.
  • the relevant control orifice opens the medium-pressure inflow to the relevant cylinder (FIG. 46)
  • the corresponding piston set begins its upward pressure stroke.
  • the compression of the medium pressure fluid is not taken into account in this view in order to concentrate on the high pressure effects.
  • the piston set in question therefore moves upwards, but the unit cannot yet deliver high-pressure fluid (water) because the pressure remains outside the pump despite the upward pressure stroke of the piston set in question under the pressure of the pressure line. So long until the pressure in the inner chamber has become high enough to open the outlet valve "OV" against the pressure in the delivery line. So you have to compress the fluid in the high pressure cylinder with the outer chamber and that in the inner chamber to the high delivery pressure of at least a thousand bar before the system can begin to deliver high pressure water.
  • Figure 49 shows the pressure increase in the inner chambers over a working cycle of two pistons.
  • the work cycle is plotted as an abscissa over a 360 degree rotation of the control body.
  • the expansion volume of the outer chamber together with its dead space is equal to the compression volume of the outer chamber with its dead space, that is, as already calculated as the compression volume.
  • FIG. 50 is first drawn, in which the course of the funding is plotted over a full working cycle, if only the compression process is taken into account, but the expansion process is not included .
  • Figure 51 shows the expansion process. It is also taken into account that the expansion process has accordingly rotated the motor further, so that the compression process only begins when the expansion process has ended. The promotion (and the expansion process) thus obtained are again applied over a full working cycle of both pistons.
  • FIG. 52 shows the pressure curve over a work cycle or rotation angle for different pressures
  • FIG. 53 shows in principle the same as FIG. 52, but in FIG. 53 the pressure curves are shown individually for the pressures 1000, 2000, 3000 and 4000 bar.
  • the expansion is also shown in FIG. 53, but this is not noticeable in the high-pressure water production because it takes place within the EREW pump.
  • the pressures drop immediately to "zero" after the end of a piston stroke, and the far-reaching conveyor valves are created without the delivery of high-pressure water. This is unsustainable for water jet cutting and therefore the means of the current invention are to be used in the EREW system.
  • the expansion volume "Ve” or “Veb” should be fed as far as possible into the cylinder subsequently operating in order to support its compression work.
  • This should be achieved in an even simpler way.
  • the control slide described is provided with the reference symbol 801, while the changeover housing is designated 800.
  • the spool 801 has the control rims 803 and 804 at a distance of 806. This basically corresponds (apart from overlap) to the distance between the inner edges of the channels and the medium-pressure cylinders MPC-1 and MPC-2.
  • FIGS. 55 to 58 show the arrangement of a control slide 802 in the same control housing 800.
  • the distance between the control ribs 803 and 804 is greater than in FIG. 54 and provided with 805 as a reference number. Due to this further distance 805 between the control boards 802 and 803, which is now the distance of the If the inner edges of the channels to cylinders 1 and 2 are exceeded, the following object and solution are achieved:
  • the control body has the left end position.
  • the medium pressure fluid flows from “MpS” into the cylinder “MPC-1” while the backflow fluid flows from the cylinder “MPC-2” to the engine “D” and drives it.
  • the extremely opposite position is shown in FIG.
  • the control body is in its right end position.
  • the medium pressure fluid flows from “MpS” to the cylinder “MPC-2”, while the return fluid flows from the cylinder "MPC-1" to the engine “D” and drives it, which moves the control body.
  • the control body 802 has passed approximately half of its way to the right.
  • the larger distance 805 between the control shelves compared to the standard control body of the known technology in FIG. 54 therefore temporarily connects the cylinder “MPC-1” with the cylinder “MPC-2” in FIG.
  • This causes the expansion fluid to shoot out of working set 1 and into the "MPC-2" cylinder.
  • the distance 805 only needs to be a little longer at the very high pressures of 4000 bar, for example, than the distance 806 between the inner edges of the channels to the cylinders, because the high pressure in the cylinder previously operating forces a very high flow rate.
  • FIG. 57 shows the control piston 802 moved a little further to the right, shortly before the connection of the cylinder 1 to the cylinder 2 was terminated. During the later "left" movement of the control body 802 during the other half of the working cycle, the same connection takes place in “ vice versa "direction and sequence.
  • the medium pressure pump "MpS” continues to deliver. But this is relatively unimportant because the connection of the cylinder 1 to the cylinder 2 for the purpose of transferring the expansion fluid into the compression process of the following work set is only very short-term.
  • the control body 802 is driven according to patent application P 39 02 092.4 (FIGS. 14 and 17) by means of an eccentric by the motor "D", so that it has the highest speed in the middle position according to FIGS. 56-57.
  • the expansion fluid flows from one cylinder to the other in a fraction of a second.
  • FIGS. 59 to 62 show an exemplary schematic solution according to the present invention. From patent application P 39 02 092.4 it is already known that motor "D" can drive several units. After the embodiment according to the invention of FIGS. 59 to 62, he drives the control body 802 of FIGS. 55 to 58, as well as the pressure accumulator filling pump (here called accumulator filling pump), and additionally the second control body 810 of FIGS. 59 to 62. The latter additional, second, control body 810 is also arranged in housing 800 and axially reciprocated in it.
  • accumulator filling pump the pressure accumulator filling pump
  • a line 824 leads from the intermediate chamber to the inlet of the accumulator pump, a line 825 from the delivery port of the accumulator pump to the accumulator (pressure accumulator) 811 and a line 826 from the accumulator to the bed 823 of the control body 810.
  • the control body 810 has an add-on, which is provided with a rotary drive, so that the control body undergoes a back and forth movement (reciprocation) and a full rotation movement (rotation) per work cycle.
  • oblique grooves are arranged in the extension, into which a roller or a finger of a rotary device engages.
  • a roller 820 which is mounted in bearings 821, is favorable for engaging in the screw groove (s) 822.
  • the control body 810 also has, for example, the control channels 816 to 819.
  • the second control body 810 has its right end position. He is not turned. One can therefore see the mouths 823 and 824 of the channels 816 and 817. At the top right, the following movements, that is to say the movement to the left and the rotation upwards, are shown as arrows, the third arrow schematically indicating the resulting following direction of movement.
  • the control body 810 has been moved so far to the left (by a little more than half the stroke) that the orifices 823 and 824 of FIG. 59 have been moved in the direction of the arrow shown therein as a result of the left movement and the rotational movement.
  • the control body 410 has reached the connection of the mouth 823 to the channel 815 and the mouth 824 has reached the connection to the channel 826 just at the time when the control body 802 of FIGS. 55 to 58 has ended the expansion fluid overflow.
  • the backward mouths of the channels 816 and 817 reach the connection to the cylinders 1 and 2.
  • the intermediate chamber 813 is now without pressure or has only low pressure, because the accumulator pump during the previous movement of the control body 810 fluid from the intermediate chamber into the Accumulator pumped and this fluid to a higher pressure than the pressure of the medium pressure fluid has brought, for example to about twice the pressure relative to the delivery pressure of the medium pressure pump "MpS".
  • the connection according to FIG. 60 only exists in fractions of a second, specifically after the flow of the expansion fluid has ended in the subsequent cylinder in which the compression is to take place. At the time of the connections according to FIG.
  • the accumulator, the pressure accumulator 811 shoots its fluid obtained from the small high-pressure pump 812 through the line 826 to the control body 810 and through the channel 817 through it into the follower cylinder 2, that is to say into the cylinder " MPC-2 "and fills it up to the full delivery pressure of the EREW system. Because the high pressure of the accumulator shoots the small amount of remaining fill in a shot into the following cylinder. The follower cylinder therefore no longer needs to compress its fluid content because the accumulator completes the compression process in the follower cylinder 2 in a shot-like manner. The cylinder "MPC-2" can now immediately deliver with full delivery. The uniformity of the conveyor flow was interrupted only for a short time and never dropped to zero. Depending on the precision of the design, the non-uniformity of the flow of the cylinder set 2 can drop to insignificance.
  • control body 810 has reached its left end position. It has been rotated 180 degrees with respect to FIG. 59.
  • FIG. 60 connects the cylinder "Z1" to the intermediate chamber 813 via line 815 via channel 816, the remaining expansion fluid shoots out of the cylinder "Z1" into the intermediate chamber during the position according to FIG. 60 and thus helps the battery fill pump Filling the accumulator. Accordingly, in the position according to FIG. 62, the remaining expansion fluid shoots out of the cylinder "Z2" through the channel 819 of the control body 810 into the intermediate chamber 813.
  • the intermediate chamber works between the equilibrium pressure of expansion and compression on the one hand and the pressure close to zero on the other hand when the accumulator filling pump has pumped the intermediate chamber empty.
  • the intermediate chamber in the calculation example is a small chamber with only a few CC and the accumulator is also a small one with only a few CC. Somewhat larger, of course, at the very high pressures of 4000 bar.
  • the EREW unit with the aid of the arrangements according to the figures 55 to 62 according to the invention, almost completely overcomes the non-uniformities of the flow according to figures 49 to 53 and the flow of the EREW Pump becomes sufficiently uniform without the need for electrical spools or several medium pressure pumps have to be used.
  • Mounted on the shaft of the motor 97 is the gear 830, which meshes with the gears 831 and 832, the gear 831 being coupled to the shaft of the accumulator pump 812, while the gear 832 is the shaft 500 that supports the eccentrics 501 and 833 drives to circulation.
  • the eccentric 501 is encompassed by the eye 507, which forms a bearing for the connecting pin 504 in the part 505.
  • the connecting pin 504 engages in the holder 506 of the control body 802.
  • the eccentric 833 is surrounded by the eye 834, which forms a cage on its other part 839 for receiving the balls or bearings 836-837.
  • the end of the control body 810 forms a radial flange which engages between the balls 836 and 838.
  • the balls are held between the bodies 839 and 840, run between and hold the flange 837 of the control body 810 in the axial direction, move it in the axial direction when the eccentric 833 rotates with the shaft 500, while the balls or bearings 836 and 838 simultaneously allow the control body 810 to rotate.
  • the grooves 822 of FIG. 59 are drawn in as a development in a large magnification. You can see the roller 820 engage in different positions in the groove 822 and you can see the shape and the angle of the groove parts that cause the automatic rotation of the control body 810 during its axial movement.
  • a one-way clutch or ratchet can be arranged to prevent reverse rotation.
  • the groove parts of the groove 822 lie in such a way that when the axial direction of movement is reversed, the roller 822 always lies on one edge of the relevant groove part, the control body 810 is rotated uniformly and in the same direction of rotation in each of the two axial directions of movement.
  • FIG. 65 shows the core parts of a diaphragm pump in which the dead space-free valves of FIG. 35 of the invention are arranged.
  • This pump can also be an EREW unit.
  • One working chamber is formed between the left plate 847 and the middle plate, the other working chamber between the middle plate 848 and the right plate 849.
  • the membrane clamping is limited by the limiting grooves 61,62, which are also leakage drainage grooves, but never get leakage with good EREW pumps, because the clamping of the membranes between the plates is completely tight when the work is done well.
  • the inlet valves 681 of FIG. 35 are arranged in the outlet valves 682 of FIG. 35 in such a way that the common end face 683 of the valves, which is known from FIG. 35 of the invention, faces the adjacent inner chamber and one Form part of the relevant stroke limiting wall 844.
  • the stroke delimitation walls on the other side are the walls 845 which delimit the outer chambers.
  • valves according to FIGS. 35 and 65 are therefore suitable according to the invention to replace the previous flow control bodies of the earlier patent applications of the inventor.
  • Each valve dead space is abolished according to the invention by FIG. 65 and the inner chambers can work with dead space equal to or almost "zero". This promotes the efficiency, the achievable pressure and the uniformity, i.e. uniformity of the flow of the unit or the pump.
  • FIG. 66 shows the conveyance of the unit according to FIGS. 54 to 64 over the work cycle, as the diagram still seems to be rationally achievable.
  • the invention thus improves the diagram of FIGS. 52-52 to that of FIG. 66. Further improvements are possible by increasing the pressure and the content of the accumulator, which forces a stronger accumulator fill pump. First of all, however, it is questionable whether so much effort is required for all applications.
  • FIG. 23 already shows the accumulator action of the pressure line to the cutting nozzle and, furthermore, the conveyance according to FIG. 66 is already much more uniform than that of the axial booster of FIG. 25 of the known technology, although this has to work with electromagnetic reversals that the EREW system saves the invention.
  • Diagram 66 is drawn below the diagram in FIG.
  • 603 and 604 are the first and second cylinders
  • 851 and 852 are the delivery lines from the first and second pumps to the first and second cylinders
  • 853 and 854 are the regulators of the two controllable and reversible pumps 642 and 643 which these pumps reverse from one direction of conveyance to the other so that the delivery lines mentioned then become inlet lines.
  • 751 ' shows the shaft and in Figure 42, position number 763' shows the rear end of the shaft 763.
  • the fluid separation means 782, 791, 792, etc. can advantageously also be arranged around the pistons 608 and / or 608 of FIGS. 25 to 32.
  • the arrangement of the means of FIGS. 55 to 64 in the unit of FIG. 48 in addition to the control body "CV" shown in FIG. 48 is particularly advantageous. Firstly, this prevents expansion fluid from flowing into the motor D, then rotating it too quickly and reducing the piston strokes and delivery quantities. and secondly, the expansion fluid is fully benefited from the compression process in the cylinder subsequently operating.
  • the losses due to expanding high pressure fluid do not seem to have been sufficiently recognized in the art.
  • the means of the invention therefore appear to bring substantial progress to high pressure pumps, including water pumps and medium or low pressure pumps.
  • FIGS. 67 and 68 show by way of example how the principles of FIGS. 26 to 32 can optionally replace the lower parts (the control parts) of FIGS. 1 and 12.
  • FIGS. 67 and 68 show that the medium pressure cylinders 14 and 15 can then be closed by a base plate 873.
  • the connections 870 and 871 are therefore either to the drive means of the figure 26, the figure 27, the figure 28, the figure 29, the figure 30, the figure 31 or the figure 32.
  • the medium-pressure pistons 8 and 9 with piston rods 860 and 861, which are sealed by the plate 873.
  • These can be provided with signal transmitters 862, 863, which can be moved manually on the relevant piston rod if required, or can be adjusted automatically by a corresponding arrangement depending on one of the pressures in the unit.
  • sensors (signal collectors) 864 and 865 can be arranged. These can also be slidably arranged on holders 866 or 876. The arrangement of the signal transmitters and the signal receivers is carried out according to the invention in such a way that the piston which is pressed later is switched on before the piston which is still working has fully completed its push stroke.
  • the next operating piston has to be switched on by the percentage of the stroke that is required according to the calculations in this document in order to have the full compression of the fluids in the cylinders of the subsequently pressing piston set in the assigned cylinders if the currently pressing piston set the printing stroke ended.
  • the signal pickups can be mechanical, hydraulic, pneumatic, electronic or electrical in nature. For example, light barriers with corresponding converters and amplifiers acting on solenoid-operated reversing valves or on the regulating elements of the regulating pumps. Also not shown are possible signal transmitters and signal receivers which utilize the end of the piston stroke in question. If such are not arranged, automatic time setting elements can be arranged which cause the fluid flow concerned to be reversed after a certain time.
  • FIG. 69 shows an alternative for the execution of a part of the main housing 464 of FIG. 1 with its alternative arrangements therein.
  • additional pistons 5555, 6666 are shown, the bottom surfaces of which are on pistons 5 and 6, respectively be stored or connected to these pistons, for example, can be flexibly connected, such as the pistons on the right-hand side of FIG.
  • the leakage collecting spaces 455, 456, 451, 452 with their drain lines 458, 457, as well as the sealing rings are shown again in the figure and correspond to those in FIG. 1.
  • the sealing rings in this figure have new reference numerals 1453, 454 and 2453, 2454 provided.
  • spaces 1455, 1456 are arranged surrounding the piston ends, which preferably have the length 872. If this length is at least equal to the length of the piston strokes, it is achieved that the surfaces of the pistons never touch different fluids.
  • a corresponding pressure compensation line 1457 may connect the spaces 1455, 1456 to the free or a low pressure space, so that no compressions of air or liquids occur in the chambers 1455, 1456.
  • the inlet and outlet valves 38, 39 are connected to the inner chamber 875, while the high-pressure cylinders 11, 12 are connected to the outer chambers 874.
  • Bellow-like separating means for separating the fluids of the inner and outer chambers from one another are arranged between the inner chambers and outer chambers.
  • These release agents consist of stainless steel sheets that are connected to one another, for example, by means of plasma welding. So you have the bottom plate 877, the upper clamping ring with the radial extension 880 for clamping between the valve cover 489 and the housing 464. Between the parts 877 and 889 mentioned there are a number of conical, thin rings, which alternately on the radially inner and outer Ends are welded or otherwise tightly connected.
  • Filling blocks extend from the cover 489 into the inner chambers, which can contain the inlet valves and which also form fluid lines to the inlet and outlet valves.
  • the left piston set 5-8 has the lower position at the end of the jerk stroke and before the start of the pressure stroke. Fluid separator 877-880 on the left side of the figure is now fully relaxed. In the right side of the figure, the piston set 6-9 has the upper position, i.e. after the end of the pressure stroke before the start of the return stroke. Fluid separator 876 is now fully compressed.
  • the base plate touches or is close to the end face of the filling part of the inner chamber.
  • the conical ring elements 878, 879 can have sufficiently large inner diameters to be able to produce the sealing connections of the radially inner ends well.
  • the elements 878,879 should spring less than four degrees in order to achieve a sufficiently long service life.
  • the special meaning of FIG. 70 is that with only two bellows-like separating means made of stainless steel or noble metal, a high conveying uniformity can be achieved without fluctuations with the help of the control elements according to this invention.
  • two housings 464, 464 ′ containing the cylinders and piston sets are aligned with one another and with their high-pressure cylinders facing one another, that is to say in opposite directions, to a center plate 881 arranged between them.
  • the membranes 58 and 58 ' are tightly clamped by means of a screw connection (not shown).
  • the cylinder 11 is connected to the outer chamber 884, the piston 12 to the outer chamber 885.
  • the inner chambers 886 and 887 are located between the middle plate and the membranes.
  • the bores 882 and 883 are arranged spatially separated from one another and with individual inlet and outlet valves 38.38 'and 39.39' provided.
  • valve housings 892 or 893 can connect in valve housings 892 or 893 and the housings can form a common supply line 894 or discharge line 895.
  • Bores 888 and 889 lead from the cylinders 11, 12 to the relevant outer chamber. These holes can be 2 or more mm in diameter.
  • a plurality of bores 890 of small diameter lead to the line 882.
  • a plurality of bores 891 of small diameter lead to the line 883.
  • the bores of small diameter should not exceed the diameter of 0.8 mm in units for 4000 bar when the membranes are 0.3 mm thick.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP90110004A 1989-05-31 1990-05-26 Ensemble à haute pression Withdrawn EP0400507A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3917598 1989-05-31
DE3917598 1989-05-31

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EP0400507A2 true EP0400507A2 (fr) 1990-12-05

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EP (1) EP0400507A2 (fr)
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130026818A1 (en) * 2010-01-28 2013-01-31 Continental Teves Ag & Co. Oag Electronic Control Device for a Braking System, Suitable for a Distance Control System
WO2015090288A3 (fr) * 2013-12-21 2015-09-03 Gerhard Stock Dispositif de refoulement pour un fluide
CN116292164A (zh) * 2023-04-28 2023-06-23 南通君集液压机械有限公司 可换流量集成式高压泵

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4029295A1 (de) * 1990-09-16 1992-03-19 Karl Eickmann Dichtung fuer hohe drucke
DE4041807A1 (de) * 1990-12-27 1992-07-02 Karl Eickmann Hoechst-druck aggregat
DE4222918A1 (de) * 1992-07-11 1994-01-13 Karl Eickmann Hochdruck Anordnung(en)
JP7007919B2 (ja) * 2018-01-10 2022-01-25 日立Astemo株式会社 ポンプ装置及びブレーキ制御装置

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4001815A1 (de) * 1989-01-25 1990-09-13 Karl Eickmann Hochdruck aggregat

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130026818A1 (en) * 2010-01-28 2013-01-31 Continental Teves Ag & Co. Oag Electronic Control Device for a Braking System, Suitable for a Distance Control System
US9205819B2 (en) * 2010-01-28 2015-12-08 Continental Teves Ag & Co. Ohg Electronic control device for a braking system, suitable for a distance control system
WO2015090288A3 (fr) * 2013-12-21 2015-09-03 Gerhard Stock Dispositif de refoulement pour un fluide
CN116292164A (zh) * 2023-04-28 2023-06-23 南通君集液压机械有限公司 可换流量集成式高压泵

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DE4017068A1 (de) 1990-12-06

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