US3641878A - Compressed liquid engine or pump - Google Patents

Compressed liquid engine or pump Download PDF

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Publication number
US3641878A
US3641878A US832513*A US3641878DA US3641878A US 3641878 A US3641878 A US 3641878A US 3641878D A US3641878D A US 3641878DA US 3641878 A US3641878 A US 3641878A
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United States
Prior art keywords
mandrel
timing sleeve
piston
sleeve
timing
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Expired - Lifetime
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US832513*A
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English (en)
Inventor
Witold Rozwadowski
Aleksander Szymanski
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Individual
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Individual
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Priority claimed from PL125133A external-priority patent/PL63282B1/pl
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L23/00—Valves controlled by impact by piston, e.g. in free-piston machines
    • 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
    • F01B11/00—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston 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
    • F01B7/00—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F01B7/18—Machines or engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with differential 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
    • F04B5/00—Machines or pumps with differential-surface pistons
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/123—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber
    • F04B9/127—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting elastic-fluid motor, e.g. actuated in the other direction by gravity or a spring

Definitions

  • ABSTRACT In a fluid operated device, a novel timing system which is formed by a fixed hollow mandrel mounted in a working cylinder with a timing sleeve and a piston mounted on the mandrel and within the cylinder. Compressed fluid is fed axially through the mandrel and through radial ports therein, which ports are selectively opened and closed by the timing sleeve sliding on the mandrel.
  • the timing sleeve is provided with catches acting on corresponding catches on the piston to move the timing sleeve in response to piston movement.
  • the object of the invention is to provide an engine with a reciprocating motion piston which is driven by means of liquid or gas, and most advantageously by compressed air, or pump of similar construction destined for compressing liquids.
  • This type of timing is generally directly controlled by the piston or the element connected with it, for instance a piston rod as described in British Pat. No. 635,629.
  • the slide valve may be controlled by a pneumatic or hydraulic system, as described in German Democratic Republic Pat. No. 40,325.
  • timing sleeve and piston valve sleeve are equivalents and the first one has been used in the present specification. In this manner the most compact construction of timing gear is obtained.
  • this engine a three-stage telescopic piston is used which automatically displaces the timing gear in the position corresponding with the backward motion of the piston.
  • this backward motion may happen only after a decrease of the working medium pressure under the action of the external force.
  • this engine may be considered as an engine with a separated timing gear which is different in comparison with the scope of application of the invention in question. It should be added that the described engine, because of the telescopic construction of the piston, causes unequal forces on the piston rod as a function of piston travel.
  • the faults of the known solutions listed above have been eliminated in the construction of the engine which is the object of the present invention.
  • the solution according to the present invention may be applied in the engines with reciprocating single-acting as well as double-acting pistons which are driven by means of liquid or compressed gas, and most advantageously by compressed air.
  • the solution according to the present invention may be especially useful as the engine for driving hydraulic pumps, in this case it is most advantageous to use the construction in which the engine piston constitutes the pump piston.
  • the solution according to the present invention may be used with a good result as the pump for liquids and especially for gases.
  • the engine consists of a cylinder with a stationary mandrel mounted inside.
  • the mandrel has a central bore by which the working medium, most advantageously air, is fed.
  • the slidable timing sleeve is mounted on the mandrel. This sleeve may be partly inside the hollow cylinder body and in such case the outside surface of the sleeve collaborates with the cylinder.
  • the timing sleeve has holes and ducts which, in the dead center position of the sleeve, connects the corresponding sides of the cylinder, divided by the piston, with the bore in the mandrel by which the working medium is fed.
  • the timing sleeve On the external surface of the timing sleeve there is a piston connected with a piston rod which passes through the end of the cylinder opposite to the end in which the mandrel for feeding the working medium is mounted.
  • the piston rod may be shaped as the plunger of the hydraulic pump combined with the engine.
  • the timing sleeve has various bosses collaborating with the corresponding bosses on the piston, which causes displacing of the timing sleeve to dead center in which the cylinder is fed by working medium from one or the other side of the piston.
  • the timing sleeve has a special surface in a plane perpendicular to its oblong axle, which surface is under the pressure of working medium fed to the engine. After displacing of the timing sleeve in one dead center, independently to the following piston motion the sleeve is kept in its position by means of pressure of the working medium.
  • the engine may be built not only as the double-acting type, in which working medium presses alternately against one or the other side of the piston, but also as the single-acting type in which motion of the piston is forced by the working medium only in one direction and backward motion is effected by a spring element pressing the piston.
  • spring elements in the timing gear of the engine which is the object of the invention, but it is not indispensable in the basic embodiments of the invention.
  • Coil springs which are the most simple and reliable, are used.
  • the invention may be also used in the construction of pumps for liquids and specially for gases by using any engine for transferring the reciprocating motion to the piston rod of the engine made according to the invention.
  • the most advisable use of the invention is for the construction of piston engines.
  • H6. 2 is a partial vertical sectional view of a single-acting engine connected to a hydraulic pump;
  • FIG. 3 is a view like FIG. 2 of a modification of the engine shown in FIG. 2;
  • FIG. 4 is a partial vertical sectional view of a further modification of a single-acting engine connected to a hydraulic pump and having a special valve for feeding compressed air over the liquid level in the feeding tank ofthe pump;
  • FIG. 5 is a horizontal section on line 5-5 of FIG. 4.
  • the piston 32 In the cylinder 31, there is a piston 32 having a piston rod 33, the piston rod being connected with any equipment to be driven.
  • the mandrel 34 In the bottom end of the cylinder 31 is an opening 1 in which the mandrel 34 is mounted.
  • the mandrel has an axial bore 25 which is closed on one end.
  • On the mandrel 34 a slideble timing sleeve 35 is mounted. The bottom part of the timing sleeve 35 collaborates in a slidable manner with the opening I located in the bottom end of cylinder 31.
  • the timing sleeve has an annular groove 2 with upper edge 3 and bottom edge 4 which enclose duct 5 connected by the aperture 6 with the outlet to atmosphere 7 and duct 8 of the air conduit 9 which is connected with the chamber 10 above the piston 32.
  • the timing sleeve 35 has radial holes 11.
  • the distance between upper edge of each of the holes 11 and bottom edge of duct 8 and duct 12 is greater than the distance between upper face 13 of the timing sleeve 35 and the upper edge of the inlet duct 14, the last distance being less than or equal to the distance between bottom edge 4 of the annular groove 2 in the timing sleeve 35 and the upper edge of duct 8.
  • the duct 12 is located on the surface of the mandrel 34 and is connected with its axial bore 25.
  • the mandrel 34 has a ring-shaped duct 15 connected with the axial bore 25 by means of the holes bored above bottom face 16 of the timing sleeve 35 at a distance greater than the distance between bottom edge 4 of the annular groove 2 of the timing sleeve 35 and upper edge of the duct 8, but less than the distance between upper edge 3 of the annular groove 2 of the timing sleeve 35 and upper edge 17 of the opening 1 bored in the bottom of the cylinder 31.
  • the upper part of the timing sleeve 35 has a collar 36 which constitutes a catch cooperating with a catch in the form of an annular recess 18 in a bore which is formed in the piston rod 33 and which encloses the mandrel 34 and the timing sleeve 35.
  • an elastic ring 19 is placed on the collar 36 of the timing sleeve 35.
  • the inside diameter 20 of the bore in the upper part of the sleeve 35 and the equal outside diameter of the upper part of mandrel 34 are greater than the inside diameter 21 of the bottom part of the bore in the timing sleeve 35 and equal to outside diameter of bottom part of mandrel 34. In this way a free closed space formed between step 22 of the mandrel 34 and step 23 of the timing sleeve 35 is connected by means of holes 24 in the timing sleeve 35 with the annular groove 2 in timing sleeve 35.
  • a chamber 27 under the piston 32 is connected, by means of a bore provided in piston rod 33, to the chamber 38 formed between the piston rod 33 and the timing sleeve 35.
  • the bottom edge of the bore in the piston rod 33 is equipped with a catch in form of a boss 28 cooperable with the mentioned catch in the form of a collar 36 formed on the timing sleeve 35.
  • boss 28 and collar 36 are used for controlling motion of the timing sleeve 35 directly by the piston 32.
  • the bottom surface of the collar 36 of timing sleeve 35 is equipped with a ring 29 made of elastic material similar to the ring 19.
  • the ring 30 made of elastic material is located on the bottom of the opening 1 bored in the cylinder 31.
  • the mandrel 34 has a duct 26 located between the ducts 12 and 14 which is connected with the axial bore 25 and when the timing sleeve 35 is in the bottom dead center position the port 37 bored in the timing sleeve 35 connect the duct 26 with the chamber 27 under the piston 32.
  • the working medium preferably compressed air
  • FlG. 1 presents the position of the movable parts of the engine according to the invention at the moment when working medium flows from the axial bore 25 in the mandrel 34 through ducts 14 and 26 to the chamber 27 under the piston 32 driving the piston 32 upward.
  • FIG. 2 A different example of using the invention is the singleacting engine illustrated in FIG. 2.
  • the piston 41 of this engine constitutes also a plunger of a hydraulic pump coupled with the engine.
  • the piston 41 biased by a spring 67, is located inside a cylinder 68 which is integral with the cylinder 69 of the hydraulic pump and its plunger, which is formed by the upper part ofa piston 41.
  • the piston 41 has an axial bore 42 with a ringlike lip 43 protruding inwards from the lower open end and a step 44 formed near the upper closed end.
  • the lip 43 and step 44 serve to control the motion of the timing sleeve 54
  • the timing sleeve 54 is mounted in a sliding manner on the mandrel 45 which has inside an axial bore 46.
  • the mandrel 45, with the timing sleeve 54 mounted thereon, is located inside the axial bore 42 of a piston 41.
  • a duct 50 opening to atmosphere and in the lateral surface of the mandrel 45 are bored holes 51 and 52 connected with this duct 50.
  • a retainer ring 53 is mounted on the upper part of the mandrel.
  • the bottom end of the timing sleeve 54 which is mounted on the mandrel 45, rests on the surface of flange 55 of the mandrel which closes the air cylinder 68.
  • the upper part of the timing sleeve 54 has a collar 56 which constitutes a catch collaborating with the step 44 and lip 43 which are on the piston 41.
  • the holes 51 have a diameter smaller than the holes 52 and the distance between the flat end surface 61 of axial bore 58 in the timing sleeve 54 and the bottom edge of the holes 52 is smaller than the distance between the upper surface of the collar 56 and the retainer ring 53.
  • a ring 63 Inside the flange 55, opposite to the bottom surface of the timing sleeve 54, there is mounted a ring 63.
  • the bottom of the flange 55 rests on step 62 formed in cylinder 68.
  • the upper part of the cylinder 68, above the piston 41, is directly connected with atmosphere through the port 66. Through this port the air which is above the piston 41 may escape outside cylinder 68 in the direction according the arrow D.
  • the hydraulic pump coupled with the engine is built of cylinder 69 which is connected with the engine cylinder 68, a plunger formed by the upper part of piston 41 and one way inlet valve 64 and one way exhaust valve 65.
  • Medium compressed by the hydraulic pump is supplied by a pipe in the direction according an arrow B and discharged by a pipe in the direction according an arrow C.
  • the working medium is fed through the axial bore 46 in the direction according arrow A and through the duct 48 and recess 47 into the space above the collar 56 of the timing sleeve 54, causing a downward displacement of the timing sleeve 54 to the position in which its bottom surface contacts the ring 63 on flange 55.
  • the axial bore 58 is connected through the holes 51 with the duct 50 and through this duct with atmosphere. Simultaneously the working medium flows through the duct 49 and the recess 47 to the space under the collar 56 of the timing sleeve 54 and then to the space under the piston 41 causing its upwards motion. While the piston 41 moves upwards, its control lip 43 hitches the controlling collar 56 of the timing sleeve 54. From this moment the movement of the piston 41 causes lifting of the timing sleeve 54 and consequently its bottom surface separates from the flange 55 and the working medium flows to the axial bore 58. It causes the compensation of the downward pressure induced by the working medium on the collar 56 of the timing sleeve 54 and upward pressure on the surface 61 of the timing sleeve 54.
  • the force of the spring 60 is large enough to press the timing sleeve 54 up into the contact with the retainer ring 53.
  • the holes 51 have diameters small enough to keep in the axial bore 58 a pressure of the working medium sufficient for compensation of the thrusts pressing against the timing sleeve 54.
  • the diameter of the holes 51 is big enough so that the working medium which could flow to the space of the axial bore 58, owing to leakage between the bottom surface of the timing sleeve 54 and the flange 55 which closes the air cylinder 68, may flow to the atmosphere making it impossible to increase the pressure in the axial bore 58.
  • the surface 61 of the bore 58 opens the holes 52, in this manner connecting the space under the piston 41 through the bore 58, holes 51, 52 and the duct 50 with the atmosphere.
  • the working medium flows over the collar 56 of the timing sleeve 54 inducing a pressure sufficient for pressing the spring 60 and displacing the timing sleeve 54 to its bottom position with its bottom surface contacting the flange 55.
  • the bottom edge of the hole 57 opens the duct 49 connected through the recess 47 with the axial bore 46 of the mandrel 45 with the effect that the working medium flows under the piston 41 causing the repetition of the described working cycle.
  • FIG. 3 shows an example using the invention, in which its fundamental features are kept, which concerns also a singleacting piston operating according to the invention and connected with a hydraulic pump.
  • the hydraulic pump as in the previous example, is composed of the cylinder 69 which constitutes one unit with the engine cylinder 68.
  • the pumped medium is fed according to the direction of the arrow B and is discharged according to the direction of the arrow C through check valves, not shown in the drawing.
  • the piston 41 moves in the cylinder 68 and has a recess in which a mandrel 45 with an axial bore 46 and a slidable timing sleeve 54 mounted on the mandrel 45 are located.
  • a step 44 is formed in the recess of the piston 41.
  • the timing sleeve 54 has in its bottom part an axial bore 58 and the mandrel 45 has below the flat surface 61 of the axial bore 58 a step 73 of an accordingly enlarged diameter.
  • the flat surface 61 of bore 58 in the timing sleeve 54 in the bottommost position of the timing sleeve 54, covers the bottom edge of the hole 52 which is connected with the outlet duct 50 to the atmosphere according to the arrow E.
  • the collar 56 of the timing sleeve 54 rests on the spring 71, the other end of which rests on the ring-shaped lip 43 of the piston 41.
  • Two rings 70 and 72 are mounted on the mandrel 45.
  • the upper ring 70 adheres to the retaining ring 53 which limits the travel of the timing sleeve 54, and the bottom ring 72 adheres to the flange 55 which closes the air cylinder 68.
  • the end 74 of the timing sleeve 54 rests on the bottom ring 72.
  • the upper part of the cylinder 68 above the piston 41 is connected with atmosphere through the port 66 according to the arrow D.
  • the working medium is fed to the axial bore 46 of the mandrel 45 according to the arrow A.
  • the mandrel 45 has ducts 48 and 49 connected with the bore 46 and the timing sleeve 54 has the holes 57.
  • FIG. 3 the position is shown when the working medium flows from the bore 46 of the mandrel 45 through the duct 49 and hole 57 to the space under the piston 41 causing its up ward movement.
  • the piston by means of its ring-shaped lip 43 which serves as the controlling step, causes compressing of the spring 71 until the moment when the force of the spring 71 is large enough for lifting the timing sleeve 54.
  • the timing sleeve 54 covers the duct 49 through which the working medium flows to the space under the piston 41. After that, because of lifting up of the end 74 of the timing sleeve 54, over the edge of the step 73 in the mandrel 45, through the hole 52 and outlet duct 51, the space under the piston 41 is connected with atmosphere.
  • the collar 56 is used as the controlling step for the timing sleeve 54 and a step 44 with the lip 43 are used for controlling the piston 41.
  • the lip 43 collaborates with the collar 56 of the timing sleeve 54 through the intermediary of the spring 71; however, the fundamental above-described feature of the invention, which is controlling the motion of the timing sleeve by means of motion of the piston is still kept.
  • the working medium which also is used for driving the engine is utilized.
  • the construction and operation of the engine in this variation of invention are identical with the example shown in the FIG. 2 with the difference that the return downward motion of the piston 41 takes place only under the pressure of the pumped medium which presses the part of the piston 41 which constitutes the plunger of the hydraulic pump. Because of that, the spring 67 of FIG. 2 is not shown in FIG. 4.
  • the remaining parts of the engine which are similar to the example shown in the FIG.
  • the bottom part of the conduit 77 which is connected to the valve 76 does not touch the bottom of the cavity 79 in the pin 80 of the valve 76.
  • the conduit 77 has lateral scarfs 81 (FIG. 5) which contact the lateral walls of the cavity in the pin 80 of the valve 76.
  • In the lateral surface of the valve 76 there is an inlet 82 the axis of which is located at the same height as the axis of inlet 83 and outlet 84 in the bottom part of the body 75 of the valve 76.
  • Extension 85 of the mandrel 45 is connected to the valve 76 through a seal ring 86.
  • a hole 87 which connects the space above the valve 76 with atmosphere.
  • the outlet 50 of the mandrel 45 is connected to this space.
  • a rotating valve 88 which is connected with the conduit 77.
  • the valve 88 has, in its upper horizontal plane, holes 89 and in the lateral plane holes 90 which are located on the same level as the holes 91 in the upper part of the pump cylinder 69.
  • the hydraulic pump is equipped with a one-way inlet valve 64 and oneway outlet valve 65 which are of the plate valve type.
  • the chamber of the inlet valve 64 is connected with the interior of the cylinder 69 through the holes 92.
  • Rotation of the pin 80 of the valve 76 causes simultaneous rotation of the conduit 77 and the valve 88 which is connected with it, with the effect that the holes 90 of the valve 88 are moved away from alignment with holes 91 in the pump cylinder 69.
  • the working medium flows through the inlets 33 and 82 inside valve 76 then to the axial bore 46 in the mandrel 45 to the space over the bottom of the cavity 79 in the pin 80 of the valve 76 and to the conduit 77. From the conduit 77 the working medium flows inside the container 78 over the level of the pumped medium.
  • the working medium flows through the inlet valve 64 and holes 92 inside the cylinder of the pump 69 causing downward dislocation of the piston 41.
  • the upward stroke of the piston 41 causes the flow of the liquid through the valve 65 to the space of the container 78 under its partition 93.
  • the rotation of the pin 80 of the valve 76 causes rotation of the conduit 77 and with it the hydraulic valve 88 so that the holes 90 in the valve 88 are aligned with the holes 91 in the cylinder 69.
  • the result is the pumped medium, which is in the space under the partition 93 of the container 78, is pumped through the holes 90 and 91 under the pressure effected by the weight of the container 78. Then the medium is pressed into the space over the partition 93 which causes lowering of the container 78.
  • a fluid operated device comprising a cylinder having a chamber therein, a reciprocable piston mounted in said chamber and having a cavity therein and at least one catch thereon, a mandrel fixedly mounted in a bottom part of the cylinder extending into said chamber and said cavity, an axial bore formed in said mandrel, a plurality of radial ports in said mandrel leading to said bore, a timing sleeve slidably mounted on said mandrel and having radial ports therein, one end of said timing sleeve extending into said piston cavity, means to feed a working medium through the bore of said mandrel, said timing sleeve having at least one step which cooperates with said at least one catch on said piston, whereby said timing sleeve is displaced depending upon changes in the location of the piston in response to the pressure of the working medium to thereby control the flow of the working medium by selective opening and closing of said ports.
  • a fluid actuated device further comprising two spaced steps protruding inside the cavity in said piston and serving as the control catches, an annular duct in the bottom part of the mandrel coaxial with said axial bore and forming an outlet to atmosphere, at least two spaced radial holes in said mandrel leading into said annular duct, a retainer ring fixedly mounted adjacent the free end of the mandrel, a radial flange at the bottom end of the mandrel, the bottom end of said timing sleeve engaging with said flange a collar on the upper end of said timing sleeve forming said at least one step, at least one radial port of said timing sleeve being located at the same height as a port in the mandrel, an axial recess in the bottom end of said timing sleeve having a larger diameter than the diameter of the mandrel, a collarshaped step spaced from the bottom end of said timing sleeve, a
  • a fluid actuated device wherein said radial flange of the mandrel engages with the bottom of said cylinder.
  • a fluid actuated device further comprising a wear ring mounted in the radial flange of said mandrel and receiving the bottom end ofsaid timing sleeve.
  • a fluid actuated device according to claim 6, further comprising spring means mounted between an upper face of said piston and the top of said cylinder.
  • a fluid actuated device wherein the mandrel has at its bottom end a portion with a diameter equal to the inside diameter of an axial recess in the bottom end of said timing sleeve, the inner end of said axial recess being above the bottom edge ofa hole in said mandrel leading to the atmosphere.
  • a fluid actuated device further comprising a spring mounted between one of said at least one step on the timing sleeve and one of said at least one catch on the piston.
  • a fluid actuated device further comprising a container means containing a pumping medium and connected to one end of said device to be responsive to pumping action by said piston, an air valve means connected to the other end of said device, a conduit having a diameter smaller than the diameter of the axial bore in the mandrel and mounted to pass through said axial bore and the mandrel with its upper end projecting over the level of the pumped medium in said container and its bottom end connected to said air valve.
  • a fluid actuated device wherein said air valve comprises a valve housing having a chamber therein, a coaxially mounted valve body means extending into said valve chamber, inlet holes and outlet holes in said valve housing, and a hole in said valve body at the height of said inlet and outlet holes.
  • a fluid actuated device further comprising an extension of the mandrel extending into the chamber of the air valve, a hole in said housing connecting the portion of the air valve chamber between said valve body and the cylinder with the atmosphere.
  • a fluid actuated device further comprising a hollow pin in said valve coaxial with said valve body, a lateral scarf on the bottom end of said conduit contacting the lateral walls of the hollow pin, and a rotating valve means connected to an upper part of conduit in said container.
  • a fluid actuated device wherein the rotating valve has an upper horizontal plane with inlet holes therein and a lateral surface with holes therein located at the height of intake holes in the container.
  • a fluid actuated device further comprising a second container slidably mounted in the container and having a partition therein, the intake holes of said container being below said partition.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
US832513*A 1968-02-09 1969-02-05 Compressed liquid engine or pump Expired - Lifetime US3641878A (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
PL125133A PL63282B1 (cs) 1968-02-09
PL127742A PL64017B3 (cs) 1968-06-26
PL127741A PL63955B3 (cs) 1968-06-26
PL128283A PL59908B1 (cs) 1968-07-24
PL12947468 1968-10-11

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US3641878A true US3641878A (en) 1972-02-15

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Application Number Title Priority Date Filing Date
US832513*A Expired - Lifetime US3641878A (en) 1968-02-09 1969-02-05 Compressed liquid engine or pump

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US (1) US3641878A (cs)
AT (1) AT294498B (cs)
CS (1) CS183608B2 (cs)
DE (1) DE1906549C3 (cs)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4611973A (en) * 1981-10-08 1986-09-16 P & B Industries Pumping system and method of operating the same

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1001821A (en) * 1911-06-12 1911-08-29 Coffield Motor Washer Company Water-motor.
US1032689A (en) * 1911-09-15 1912-07-16 Carl Martens Reciprocating engine.
US1458383A (en) * 1921-06-08 1923-06-12 American Liquid Meter Company Fluid meter
US2039570A (en) * 1935-05-16 1936-05-05 Elliot I Thornton Pump
US2361757A (en) * 1943-05-17 1944-10-31 Charles A Fink Fluid pressure operated device
FR76804E (fr) * 1959-07-11 1961-12-08 Injecteur de liquide à haute pression
US3014464A (en) * 1960-03-28 1961-12-26 Dehavilland Aircraft Canada Fluid converters
FR1312051A (fr) * 1961-11-04 1962-12-14 Groupe moto-pompe pour fluides divers
US3086470A (en) * 1960-03-28 1963-04-23 Skipor System for increasing fluid pressure
US3174409A (en) * 1962-11-29 1965-03-23 David C Hill Pumps and regulating means therefor

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1001821A (en) * 1911-06-12 1911-08-29 Coffield Motor Washer Company Water-motor.
US1032689A (en) * 1911-09-15 1912-07-16 Carl Martens Reciprocating engine.
US1458383A (en) * 1921-06-08 1923-06-12 American Liquid Meter Company Fluid meter
US2039570A (en) * 1935-05-16 1936-05-05 Elliot I Thornton Pump
US2361757A (en) * 1943-05-17 1944-10-31 Charles A Fink Fluid pressure operated device
FR76804E (fr) * 1959-07-11 1961-12-08 Injecteur de liquide à haute pression
US3014464A (en) * 1960-03-28 1961-12-26 Dehavilland Aircraft Canada Fluid converters
US3086470A (en) * 1960-03-28 1963-04-23 Skipor System for increasing fluid pressure
FR1312051A (fr) * 1961-11-04 1962-12-14 Groupe moto-pompe pour fluides divers
US3174409A (en) * 1962-11-29 1965-03-23 David C Hill Pumps and regulating means therefor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4611973A (en) * 1981-10-08 1986-09-16 P & B Industries Pumping system and method of operating the same

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Publication number Publication date
AT294498B (de) 1971-11-25
DE1906549C3 (de) 1974-04-11
DE1906549A1 (de) 1969-08-28
CS183608B2 (en) 1978-07-31
DE1906549B2 (de) 1973-09-13

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