Classifications

• • 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
  • F04B23/00—Pumping installations or systems
  • F04B23/04—Combinations of two or more pumps
  • F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
  • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
  • F03C1/00—Reciprocating-piston liquid engines
  • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
  • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
  • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
  • F03C1/0644—Component parts
  • F03C1/0652—Cylinders
• • 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
  • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
  • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
  • F04B1/2014—Details or component parts
• • 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
  • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
  • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
  • F04B1/2014—Details or component parts
  • F04B1/2035—Cylinder barrels
• • 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
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/14—Pistons, piston-rods or piston-rod connections
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
  • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
  • F01B3/0052—Cylinder barrel

Definitions

• the invention relates to a hydraulic transformer, which consists in principle of a hydraulic motor and a hydraulic pump, which are connected to each other via a drive shaft.
• a hydraulic transformer With a hydraulic transformer, a low inlet pressure can be converted into a high outlet pressure with a small volume flow and a high inlet pressure with a small volume flow into a low outlet pressure with a high flow rate.
• the roles of pump and motor can usually also be reversed to recover potential or kinetic energy.
• Fields of application of hydrotransformers are hydraulic networks designed as constant-pressure nets and low-loss operation of hydraulic cylinders on such nets. Hydraulic cylinders can then be operated and be supplied by the working as a pump part machine with pressure medium, even if the load pressure does not match the pressure in the pressure network. Conversely, when lowering a load carried by a hydraulic cylinder, energy can be recovered even if the load pressure does not match the pressure in the pressure network. Throttle controls or load-sensing controls can be replaced.
• hydrotransformers are state of the art. In general, hydrotransformers are built on the basis of swashplate engines, because this type inherently better adjusting dynamics of the adjustment has up than, for example, the bent-axis design. Hydrotransformers are known from a number of publications. Thus, DE 32 02 015 C2 shows a hydraulic transformer, which consists of two attached axial piston machines in swash plate design. From DE 196 54 567 A1 hydrostatic transformers in swash plate design are known in which the swash plate is common to both submachines. In a hydraulic transformer known from WO 2003/058035 A1, the control of the pressure medium flows via a control disk, which is adjustable relative to the swash plate of an axial piston machine.
• a hydrotransformer could also be designed using a hydrodynamic machine of the oblique-axis type, which in principle has a good start-up behavior.
• the oblique-axis design has the disadvantage that for the adjustment of the stroke inherently very large masses must be moved, namely the whole cylinder block. The suitability of this design as a secondary-controlled motor is therefore limited.
• the regulation of the transformer function takes place in contrast to the conventional hydrotransformer not by means of the classic stroke adjustment of the piston engine, but by rotatable control mirrors with three kidney connections. The mode of operation corresponds to a hydraulic phase control.
• a disadvantage is the high noise and pulsation development of this arrangement.
• the invention is based on the objective of the construction of a hydrotransform- gate with high efficiency, good start-up behavior and slow running good controllability in particular of the used mainly as an engine and secondary-controlled sub-machine of a hydrotransformer.
• the desired aim is with a hydraulic transformer with two hydrostatic submachines, wherein at least one sub-machine is a hydrostatic axial piston machine in swash plate construction with a drive shaft on which a flange is rotatably mounted, with a swash plate on which a driven over the drive shaft or Flaninace rotor disk is rotatably mounted, and with a plurality of distributed between the flange and the rotor disk and distributed about the axis of the drive shaft displacer units, each comprising a cylinder sleeve and a projecting into the cylinder sleeve piston with a ball head and a projecting into the cylinder sleeve spherical condyle.
• the rod ends are located on the flange disc and the pistons on the rotor disc.
• the pistons more or less dive into the cylinder sleeves, while the rod ends and the cylinder sleeves are pivoted relative to each other only against each other.
• the axis of a piston and the axis of the associated cylinder sleeve passing through the centers of the ball heads of the pistons and the rod ends intersect only at small angles, and therefore the pistons and cylinder sleeve are almost aligned with respect to their axes so that the pistons have a large diameter can be trained.
• a preferred embodiment is that the drive shaft of the at least one sub-machine is mounted on both sides of the flange in pivot bearings and that the rotor disk between the flange and a Drehla- ger is arranged and has a central passage for the drive shaft.
• the rotor disk preferably has a flat sliding surface with respect to a sliding partner fixed in the direction of rotation of the drive shaft and is centered with respect to the sliding partner, this centering of the rotor disk and the sliding partner advantageously being effected by a centering collar on one part and a centering rotation on the other part.
• the inclination of the sliding partner relative to the axis of the drive shaft is variable, so that the stroke paths of the piston and thus the displacement volume of the axial piston machine is variable.
• the sliding partner in contrast, the rotor disk rotates a fixed in the direction of rotation of the drive shaft swash plate, which then like the rotor disk has a central passage for the drive shaft and whose inclination with respect to the axis of the drive shaft is changeable.
• a hydrotransformer according to the invention with the at least one axial piston machine with double-ball thruster, its displacement chambers are alternately fluidically connected to two working ports during operation via the flange disc and a distributor plate against which the flange disc rests. Accordingly, the commutation of the displacer spaces between high pressure and low pressure takes place via the rod ends, the flange disc and a distributor plate, which can also be a housing part.
• the rod ends therefore have a central bore for the commutation. This central bore may be larger in diameter than in the pistons, since the rod ends need not be as tightly constricted on their foot as the pistons.
• the inclination is from the rotor disk with respect to the axis of the drive shaft is changeable.
• the hydrostatic axial piston machine is thus preferably a machine which can be adjusted in its displacement volume (stroke volume or displacement per revolution).
• the inclination of the rotor disk is pivotable in opposite directions from a position in which the stroke of the pistons in the cylinder sleeves is zero. This is also referred to as a hydromachine which can be pivoted over zero or over a zero position.
• a hydrotransformer according to the invention has two sub-machines, both of which are designed as hydrostatic axial piston machines with a double-ball thruster.
• the start-up behavior of the hydrotransformer is very good due to the double-ball thruster used (no piston lateral forces, direct pressure torque conversion).
• the arrangement is very well suited for the sensitive start of a consumer. Due to the principle of the positive displacement principle, high efficiencies can be achieved over the entire operating range.
• the adjustment of the stroke volume of the secondary-controlled engine of the hydrotransformer takes place conventionally by means of a swivel cradle as in the swashplate design and thus ensures good controllability of the connected consumer.
• the noise and pulsation development lies in the area of classic piston engines, for example a swashplate engine.
• Figure 1 shows a longitudinal section through the axial piston machine
• FIG. 1 shows the circuit diagram with hydraulic transformer.
• the axial piston machine shown is constructed on the basis of an axial piston machine in swash plate design and intended for use as a hydraulic motor, but also as a hydraulic pump.
• the displacement chambers of the axial piston engine shown are each formed from a cylinder sleeve 31, a joint head 32 and a piston 33.
• the condyle and the piston are spherical in each case at the ends, which form the boundary of the displacer space.
• this arrangement has the advantage that the joint function is carried out both on the side of the joint head, as well as on the side of the piston in principle (ball in tube) with a hydrostatic discharge of 100 percent.
• the highly loaded joints of the hydraulic machine are designed due to the principle friction.
• this arrangement has the advantage that all elements are inherently positively connected to each other. As a result, it is entirely possible to dispense with a non-positive connection of the joint head with the cylinder sleeve, or the cylinder sleeve with the piston (for example by means of springs).
• the positive displacement principle is characterized by friction due to the principle. Due to the positive connection of the displacer is in principle the suitability for high speeds.
• the condyle and the piston have recesses which produce a gap compensation between the balls and the cylinder sleeve, which expands under pressure. possible.
• the recess is designed so that the remaining gap between the cylinder sleeve and condyle, or cylinder sleeve and piston under pressure targeted constant, or under pressure becomes smaller, or under pressure becomes larger under pressure by the ball expands depending on the pressure. This makes it possible to specifically influence the leakage through this column.
• the rod ends 32 are attached to the flange 34 and convert the hydraulic forces from the displacement in a torque on the drive shaft 35. With their axes, the rod ends parallel to the axis of the drive shaft. The centers of the ball heads of the rod ends 32 are thus all in the same plane perpendicular to the axis of the drive shaft.
• the pistons 33 are fastened to the rotor disk 36 and perform a lifting movement relative to the cylinder sleeves 31.
• the axes of the piston 33 extend in accordance with the variable inclination of the rotor disk obliquely to the axis of the drive shaft.
• the rotor disc is synchronously with the rotational speed of the flange 34 by a driving pin 37 which is inserted in a bore of the drive shaft and engages in slots on a collar of the rotor disc, taken during rotation, a pivoting movement between the drive shaft and the rotor disc takes place.
• the entrainment can be done for example via gimbal joint, a constant velocity joint, or the like.
• the rotor disk is rotatably mounted on the pivoting cradle (swash plate) 38, for example by means of a hydrostatic bearing or by means of a roller bearing. The centering of the rotor disc on the
• Swash plate is made via a centering collar 54 on the swash plate and a Zentrierewearhung 55 on the rotor disk.
• the drive shaft 35 is rotatably mounted on both sides of the flange disc 34 by means of tapered roller bearings 56 and 57 in the bottom 58 of a housing pot 59 and in a housing cover 51.
• the rotor disk 36 and the swash plate 38 are between the flange 34 and the tapered roller bearing 56, ie between the Flange plate 34 and the bottom 58 of the housing pot 59 are arranged and each have a central passage 48, 49 for the passage of the drive shaft 35.
• the drive shaft protrudes through the bottom 58 to the outside and has a stub shaft outside, so as to be coupled to a driving or driven machine part become.
• the stroke adjustment of the piston takes place, as in a conventional swashplate construction, by means of an adjustment system which is designed as a bush, first adjusting piston 40 with a large effective area, which is controlled by a valve not shown in detail, and an adjusting piston 41 smaller Working surface, which is constantly acted upon by the high pressure at a working port.
• the adjusting pistons are single-acting pistons and work, opposite to each other with respect to the pivot axis of the swash plate. With the adjusting piston 41 acts in the same direction, a return spring 42, through which a rest position of the swash plate is specified.
• the slant can be pivoted in opposite directions from a zero position in which it assumes a position in which the piston 33 perform no stroke.
• the hydrostatic machine is suitable for use as an open-loop Versteilmotor and suitable for secondary control, ie for controlling the speed or torque of the machine regardless of the upcoming high pressure, not only changed the direction of rotation, but also went from engine operation to pump operation can be.
• Secondary control is opposed to the primary control, in which the flow rate of the pump, so the primary unit is specified.
• the pump is usually pressure controlled, but the pressure setting may be variable.
• the commutation is carried out via a high-pressure channel and a low-pressure channel, which are not shown in detail on the housing cover 51 connection points lead to a distributor plate 52 which between the flange 34 and the housing cover 51 rotatably relative to the housing cover is arranged. Between the flange 34 and the distributor plate 52 is a sliding pair. In the distributor plate two arcuate recesses, not shown, are formed, each of which is open to one of the channels in the housing cover 51 and with which upon rotation of the flange 34 individual channels 53 in the flange, which through a condyle 32 through each to a Lead the displacement, get into overlap.
• the arrangement according to the embodiment allows a continuous drive shaft 35 and thus a drive through and the arrangement of several machines in a row. Such a drive-through is also possible if, in a variant of the axial piston machine shown, the flange disc 34 near the bottom and the rotor disc and the swash plate near the lid or when the stub shaft is on the cover side.
• the commutation of the displacer is carried out as in conventional hydrostatic axial piston machine in swash plate design by a distributor plate 52, and the flange 34. This adjustment is independent of the requirements of the commutation and the hydrostatic bearing of the flange disc possible. There are large swivel angle and a swing through feasible.
• hydrostatic axial piston machine in particular the hydrostatic axial piston machine described as an exemplary embodiment, are the following:
• Machine can swing (in addition to the above properties), thereby suitability as a hydraulic motor in the open circuit (secondary control);
• the machine can be driven through (multiple arrangement as with swashplate constructions possible).
• the hydraulic system according to FIG. 2 includes a double-acting hydraulic cylinder 60, in the present case a synchronous cylinder, with which a load m can be moved.
• the pressure medium paths between a hydraulic unit 61, a tank 62 and the two cylinder chambers 63 and 64 are controllable with a 4/3-way valve 65 having a pressure port, a tank port and two consumer ports.
• a 4/3-way valve 65 having a pressure port, a tank port and two consumer ports.
• the pressure connection is connected to the tank connection.
• the directional control valve can be brought into a working position by driving a Doppelhubelektromagneten in which a cylinder chamber is connected to the pressure port and the other cylinder chamber to the tank port.
• the hydraulic unit 61 is a unit with a constant displacement, which is operable in both directions of rotation both as a hydraulic pump and as a hydraulic motor. It has two working ports, one of which is connected to the pressure port of the directional control valve 65 and the other with a symbolized by a line 66 hydraulic network with impressed pressure (constant pressure network 66).
• the hydraulic unit 61 forms, with a second hydraulic unit 70, a hydrotransformer which allows the hydraulic cylinder 60 to be operated on the constant pressure network without throttling losses and also to feed energy back into the pressure network.
• the hydraulic unit 70 is adjustable in its stroke volume above zero and connected to a first working port with the tank 62 and the second working port with the line 66, so the constant pressure network.
• the hydro unit can operated both as a hydraulic pump and as a hydraulic motor, although, unlike the hydraulic unit 61 is always present at the same working port relative to the other working port of the higher pressure.
• Constant pressure network does not mean that the pressure in the line 66 is kept at a very specific pressure. The pressure can change quite a bit.
• a pressure is present in the line 66 and the hydrotransformer is controlled so that the desired movement is obtained at the hydraulic cylinder 60.
• a hydraulic accumulator is usually connected to the constant pressure network.
• the two hydraulic units 61 and 70 can be separated from the constant pressure network.
• the engines of the two hydraulic units 61 and 70 are mechanically connected to each other via a shaft 71, so both have always the same speed.
• This speed is detected by a speed sensor 73 and given to a control device 74 which contains both hydraulic and electrical components and by which the hydraulic unit 70 is adjusted so that a desired speed is present.
• the hydraulic unit 71 has a constant stroke volume, a measure of the over the hydraulic unit 61 the hydraulic cylinder 60 flowing or over the hydraulic unit 61 away from the hydraulic cylinder 60 pressure medium quantity and thus a measure of the traversing speed of the Hydrozy- Linders.
• the load pressure may be higher than the pressure in the line 66.
• the hydraulic unit 61 is driven as a pump at a speed corresponding to the desired speed by the hydraulic unit 70 operating as a hydraulic motor. If the speed drops a bit, it will detected by the tachometer 73 and the hydraulic unit 70 is slightly further swung. If the speed is too high, the hydraulic unit 70 is slightly swung back. By the hydraulic unit 61, the pressure is increased from the pressure prevailing in the constant pressure network level to the load pressure.
• the hydraulic unit 61 operates as a hydraulic motor and drives the hydraulic unit 70. This is compared to the first case pivoted above zero and promotes the operation as a pump pressure fluid from the tank into the pressure network, the conveyed pressure medium quantity is smaller than the amount of pressure fluid swallowed by the hydraulic unit 61.
• the hydraulic unit 61 drives the hydraulic unit 70 at a torque given by the difference between the network pressure and the load pressure and the constant displacement.
• the stroke volume of the hydraulic unit 70 must be set to be smaller than the constant stroke volume of the hydraulic unit 61.
• the hydraulic unit 61 also works as a hydraulic motor and drives the hydraulic unit 70. The direction of rotation of the hydraulic unit 61 and thus of the shaft 71 is opposite to the direction of rotation in the first and in the second case.
• the hydraulic unit 70 is pivoted in the same direction as in the first case and promotes in operation as a pump pressure fluid from the tank into the pressure network. Energy is being recovered.
• a fourth case let the hydraulic cylinder be retracted at a certain speed under negative load, with the load pressure being lower than the pressure in line 66.
• the hydro unit 61 operates as a hydraulic pump and is driven by the engine operated hydraulic unit 70.
• the direction of rotation of the hydraulic unit 61 and thus the shaft 71 is opposite to the direction of rotation in the first and in the second case.
• the hydraulic unit 70 is pivoted relative to the first case from the zero position in the opposite direction. Energy is recovered again because more hydraulic fluid flows into the conduit 66 from the hydraulic cylinder than it is removed by the hydraulic unit 70.
• the two hydraulic units 61 and 70 from FIG. 2 are designed as axial piston machines with double-ball thrusters according to FIG.
• the outstanding from the housing of the machine according to Figure 1 stub shaft of the drive shaft 35 serves to couple the two units 61 and 70 together.
• it is preferably corrugated and not provided with the apparent from Figure 1 key.
• the stub shaft shown in FIG. 1 would be missing.
• the housing cover 51 has a central opening into which the drive shaft of the second unit projects with a corrugation.
• the two drive shafts can then be rotatably connected to one another with an attached coupling bushing.
• the two hydraulic units 61 and 70 may also be integrated with each other, wherein, for example, in a so-called back-to-back arrangement, a common housing consists of two housing pots and a common central part.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Reciprocating Pumps (AREA)

Applications Claiming Priority (2)

Publications (1)

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ID=47997434

Family Applications (1)

Country Status (2)

Cited By (1)

Families Citing this family (3)

Citations (6)

• 2012
  • 2012-03-29 DE DE102012006290A patent/DE102012006290A1/de not_active Withdrawn
• 2013
  • 2013-03-21 WO PCT/EP2013/055869 patent/WO2013143953A1/fr not_active Ceased

Patent Citations (6)

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