US3824045A - Variable-capacity sliding-vane pump - Google Patents

Variable-capacity sliding-vane pump Download PDF

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Publication number
US3824045A
US3824045A US00226681A US22668172A US3824045A US 3824045 A US3824045 A US 3824045A US 00226681 A US00226681 A US 00226681A US 22668172 A US22668172 A US 22668172A US 3824045 A US3824045 A US 3824045A
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US
United States
Prior art keywords
rotor
pump
vane
cylinder
vanes
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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.)
Expired - Lifetime
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US00226681A
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English (en)
Inventor
W Wisniewski
J Piotrowski
Z Szeler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
CENTRUM TECHNIKI OKRETOWEJ PRZEDSIEBIORSTWO PANSTWOWE WYODREBNIONE P
CT TECHNIKI OKRETOWEJ PRZED PA
Original Assignee
CT TECHNIKI OKRETOWEJ PRZED PA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from PL146413A external-priority patent/PL67784B1/pl
Priority claimed from PL15166871A external-priority patent/PL74307B2/pl
Application filed by CT TECHNIKI OKRETOWEJ PRZED PA filed Critical CT TECHNIKI OKRETOWEJ PRZED PA
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Publication of US3824045A publication Critical patent/US3824045A/en
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Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/20—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the form of the inner or outer contour of the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/44—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C2/08 or F04C2/22 and having a hinged member with vanes hinged to the inner member

Definitions

  • ABSTRACT The invention relates to a technical solution of a double-acting, thus relieved, sliding-vane pump, its capacity being adjustable in a continuous way during operation of the pump.
  • the adjustment of the capacity of said pump is performed at constant speed of the pump rotor, by means of turning a movable cylinder, movable inlet and outlet chambers, or by deformation of a flexible cylinder, relatively to the modification of the pump.
  • Said pumps can have pendulous vanes mounted non-centrically on shafts, or rotatively, or artitulatively mounted in channels of the rotor, or rotatively and centrically mounted on shafts.
  • the vanes mounted in all the modification of the pump are provided with seals at the contact areas with the cylinder, and in channels of the rotor.
  • the seal of the vane against the cylinder is realized by means of a plate pack, pushed out individually by an elastic and flexible material.
  • the sealing of the vane in the rotor is secured by means of a rubber bar or elastic thin-walled seal with spread arms.
  • VARIABLE-CAPACITY SLIDING-VANE PUMP The invention relates to a variable-capacity doubleacting sliding-vane pump which being driven by another pump becomes an engine of variable torque.
  • the invention relates to a pump having a cylinder provided with an oval hole and a cylindrical rotor in which pendulous vanes are mounted, sliding over the bearing surface in course of rotation of the rotor.
  • Said cylinder is arranged inside a housing and can be of rigid or flexible construction.
  • a flexible cylinder its hole forming the bearing surface for the vanes is during the operation of the pump purposely deformed into an oval shape in order to achieve the pump capacity as desired.
  • the invention relates also to the design of vanes being employed in the pump into consideration, and to sealing them against the rotor and the cylinder.
  • the arrangement according to the invention can operate as a pump or a compressor if driven by a motor or engine, and also as an engine having variable torque if driven with a liquid medium pumped by another pump.
  • Known sliding-vane pumps are single-acting or double-acting ones provided with rotors having plate vanes slidably pushed out, or vanes mounted rotationally on a shaft fitted in the rotor.
  • the rotor rotates in a cylinder forming simultaneaously the case, or ina cylinder constituting a separate part within the case.
  • the vanes mounted in it slide over the bearing surface of the cylinder, forcing the liquid from the suction to the delivery chamber.
  • adjusting of the capacity of the pump is usually performed by means of to vary the volumes of the suction and the delivery chambers, whereby the speed of the rotor is maintained at constant value.
  • the capacity is controlled by adjusting the eccentricity of the rotor against the cylinder.
  • the change of the eccentricity causes a change of volumes of the suction and delivery chambers.
  • Double-acting sliding-vane pumps have an oval cylinder of rigid construction, or flexible one admitting to shape it in an oval form.
  • Double-acting sliding-vane pumps with rigid cylinders enable to adjust the pump capacity by turning oval holes arranged on both sides of the cylinder axis, what causes the variation of the size of suction and of delivery chambers.
  • the adjusting of the pump capacity is performed by decreasing or increasing the ovality of the cylinder bearing surface.
  • vanes are known mounted rotationally on a shaft mounted on both sides in the rotor, or vanes mounted pendulously directly in channels made in the rotor. Said channels have their cross section shaped as a semi-circle or a polygone formed by several circular arcs.
  • the sealing of the vanes in the channels of the rotor is realized by strict fitting the bearing surface of the vane with that of the rotor.
  • Another method of sealing consists in providing the vane bearing surfaces with sealing straps being fixed durably.
  • Adjusting the capacity of a double-acting slidingvane pump by means of turning the oval holes arranged on both sides of the rotor demands a rather compli cated design of the side covers bearing said holes. Controlling of said covers is also rather inconvenient.
  • the structure of a sliding-vane pump with flexible cylinder is a complicated one, as it comprises numerous pistons and accompanying'control members, wnaufacturing of which and assembling are exceptionally difficult.
  • the plate vanes up to date most frequently employed in the practice, show an essential disadvantage consisting in high loadings on the edges of guide channels. Said disadvantage limits the range of working pressures.
  • Pendulous vanes mounted on comb hinges are suitable for to operate in pumps, they cannot be however employed in compressors owing to enormous volumetric losses caused by only partial draining off of the medium from chambers enclosed between the vanes.
  • the comb-type hinging of the vanes when applied in compressors renders it superfluously difficult to make hinges of complicated form.
  • the object of the invention is to eliminate the inconveniences and disadvantages of known sliding-vane pumps through reducing the complexity of the pump design, simplifying its servicing, and increasing the efficiency of the pump.
  • the invention consists in that in the known doubleacting sliding-vane pump provided with rotary cylinder having oval race way there are employed as a new element, self-aligning vanes mounted on comb hinges, such a design ensures better distribution of forces on the vanes hinges. During the pumps operation the vanes are pressed down to the race way by means of centrifugal force and spring or only by means of centrifugal force.
  • the sliding-vane pump according to a modification is provided with an immovable cylinder but arotary cross mounted on a control sleeve, turning of which causes a change of positioning of the suction and delivery chambers enclosed between the cylinder bearing surface and the recesses of the cross.
  • the change of positioningof the chambers in relation to the oval hole of the cylinder causes the change of the pump capacity, and at larger displacement the change of the flow direction of the medium.
  • the cross is turned by means of a lever fastened to it.
  • the liquid inlet and outlet openings are made in the pump housing.
  • the pump capacity is adjusted also at constant rotor speed.
  • the maximum capacity of the pump can be obtained at positioning the arms of the cross at an angle of 45 to the axis of outlet and inlet openings. Whereas when the crosss arms coincide with the inlets and outlets then the capacity is equal to zero.
  • the bearing surface is formed by the inner surfaces of pistons which are connected between each other by flexible elements.
  • the elements constituting the continuity of the bearing surface admit the liquid to flow through openings being provided therein.
  • Deformation of the flexible elements is realized by the displacements of the pistons which being controlled in pairs narrow the bearing surface in one direction wherethrough it gets extended perpendicularly to the direction of contracting.
  • Controlling of the pistons may be performed continuously by hydraulic, pneumatic, or mechanical means, in course of rotations of the rotor.
  • the pump according to the present invention involves also new-type sealing of vanes both against the cylinder bearing surface and the rotor bearing surface.
  • each vane is provided with a pack of plates located loosely in a channel cut near to the edge of the vane. Said plates are forced out towards outside by an insert made of elastic material. Each plate of the pack is pushed out independently.
  • the midpoint of the thickness of the plate pack, adjoining the cylinder bearing surface covers with the point of intersection with the extended curvature line of the vane bearing surface.
  • the displacement of the plates towards outside is limited by the cylinder bearing surface.
  • Supporting of the plate pack on the elastic insert admits each plate to be pressed down to the bearing surface, independently on the angle measured along the generating line of the vane in relation to the cylinder bearing surface.
  • the plate pack contacting with the cylinder bearing surface forms a sort of labyrinth seal.
  • the vane with sealing plates arranged herein is pushed towards the cylinder bearing surface by centrifugal force or by spring.
  • the present invention involves also a modification of the rotor design according to which the rotor has on its periphery longitudinal channels having semi-circular cross section of a rim angle exceeding In the rotor bearing surface an at least one longitudinal groove is cut, in which a rod-shaped seal is placed.
  • the length of said seal equals approximately to the half of the vane length.
  • an identical or similar seal is to be placed on the opposite side of the channel.
  • the cross dimension of the seal is greater than the depth of the channel. Owing to elastic performance of the material, from which the sealis made, the-seal changes its cross dimension as the vane bearing surface is pushed towards or away from the rotor bearing surface. Thus its contact with surfaces to be sealed is always secured.
  • vanes To the shape of the channel the shape of vanes is matched, which in this case have a form of a cylinder planed on one side along the entire length.
  • the vanes are also provided with recesses for to arrange therein the springs pressing down the vane to the cylinder bearing surface and to generate the pressure difference beyond and under the vane, wherefore the rotor is provided with according holes.
  • the rotor according to the second modification differs from the former by a groove cut in the rotor surface.
  • a groove cut in the rotor surface.
  • a thinwalled seal with arms spread in an Y-shape.
  • the ends of the seal spread outwards are in contact with the vane bearing surface and seal it in both directions.
  • recesses are made in the rotor, into which come the spread ends of the seal at according thrust of the vane.
  • Said recesses secure the seal against squeezing in the clearance between the rotor and the vanes.
  • the vanes are in this design shaped as a cylinder planed on two sides of the entire length and are rotatively and concentrically born on the shaft.
  • the shaft is with its ends born in side rings. Said shaft carries only a part of the loading of the vane, since the fundamental loading, affected by the liquid pressure, is carried by the rotor bearing surface.
  • FIG. 1 shows in its left-hand half the sectional view A-A after FIG. 2, and the right-hand half is the sectional view B-B after FIG. 2,
  • FIG. 2 is the cross-sectional view according to the line CC in FIG. 1,
  • FIG. 3 shows in its left-hand half the sectional view E-E after FIG. 4, whereby the right hand half is the view of the pump
  • FIG. 4 is the cross-sectional view along the line D-D of FIG. 3,
  • FIG. 5 shows in its left-hand half the view of the pump, the right-hand half being the sectional view FF after FIG. 6,
  • FIG. 6 is the cross-sectional view of the pump along the line GG of FIG. 5,
  • FIG. 7 shows the detail of execution Q from FIG.
  • FIG. 8 is the half section of the rotor having vanes in form of a cylinder with planed sides
  • FIG. 9 is the top view of the vane
  • FIG. 10 is the sectional view of the vane along the line H-H after FIG. 9,
  • FIG. 11 shows the detail b of the rotor with vanes according to the FIG. 8,
  • FIG. 12 is the half section of the modification of rotor and vanes
  • FIG. 13 is the sectional view along the line JJ after FIG. 12,
  • FIG. 14 is the side view of the vane
  • FIG. 15 shows the constructionaldetail c of the rotor with vanes after FIG. 12.
  • the rotor 2 is arranged with vanes mounted on comb hinges and on axes 4, and the cylinder 5 with external toothing.
  • the cylinder 5 is on its periphery guided by four offsets 6 of the housing 1, and is on both sides closed by covers 7 screwed to the housing 1.
  • the space enclosed between the bearing surface 8 of the cylinder 5 and the rotor 2 and the covers 7 is in positions of four protrusions 9 sealed between adjacent vanes 3 with seal 10. Said spaced communicate beyond the protrusions 9 with eight chambers, four of which are the suctionchambers 11, and the remaining four are delivery chambers 12.
  • the medium being pumped is supplied to the four suction chambers 11 through four openings 13, and drained from delivery chambers 12 through four openings 14.
  • Rotation of the rotor 2 born in sleeves l5 and provided with the seal 16 provokes the suction and delivery of the medium respectively, through openings 13 and 14 in the direction marked by full arrows in FIG. 1.
  • the spring 20 causing the pressing down of the vane 3 to the bearing surface 8 is of particular significance when the unit according to the invention is employed as a hydraulic engine.
  • the rotor 2 with vanes 3 and shafts 4 are made identically as in preceding example, only the structure of the cylinder and the method of controlling the direction of flow and of adjusting the capacity differ.
  • the crosses 21, guided in the housing 22, are provided with splines 23 engaging with the splines of the control sleeve 24.
  • a sliding sleeve 25 is located in the sleeve 24 in the sleeve 24 .
  • the housing is on both sides closed with covers 26 fastened to the housing by means of threaded rings 27.
  • the scale 33 indicates the value of the pump capacity being set up, as well'as the direction of flow of the liquid through the pump.
  • the rotor 2 together with the vanes 3 and shafts 4 are made identically as in preceding examples, the design of the cylinder 34 and of the housing 41 is, however, different. Also the method of controlling the directions of flow and of adjusting the capacity are others.
  • the cylinder 34 according to this modification has thin flexible walls and is made as a single whole piece with four guiding pistons 35 and 36. Said pistons are situated oppositely to each other, along axes perpendicular to each other.
  • Such a cylinder, formed by flexible elements and pis- I tons, on its internal side has the bearing surface 37, over which the rotor vanes slide.
  • the form of the bearing surface changes from the circular one at zero position, that is according to the right-hand half of the FIG.
  • the change of the shape of the bearing surface corresponds with a change of the pump capacity, and of direction of flow of the liquid.
  • the rotor with vanes is on both sides closed with covers 42 fastened to the housing 41 with nuts 43, and rotates as in previous modifications.
  • FIG. 7 The exemplary sealing of the vane, according to the invention is shown in FIG. 7 showing the constructional detail Q after FIG. 1.
  • the pendulous vane 3 is mounted on the shaft 4,
  • the plates are made of steel but can also be made of other material.
  • a rubber insert 48 is arranged at the bottom of the channel.
  • the rubber or other material having similar elastic properties behaves like a fluid, transmitting almost equal thrusts on each plate of the inserted pack.
  • the thrust of the rubber insert and pressure of the spring or of the centrifugal force on the vane assures the requested pressing down of the plates to the bearing surface 8, 29, or 37 of the cylinder.
  • the rotor 50 is arranged in the cylinder of the variable-capacity double-acting pump.
  • Said rotor is provided with twelve channels 51 having a semi-circular cross section, being cut out on its periphery. In these channels vanes 52 are placed.
  • the vanes have a form of a cylinder planed on one side of the entire length.
  • the diameter of this cylinder is fitted with the diameter of the channel, what renders possible that the vane performs rotary motion in the channel in course of rotation of the cylindrical rotor within the oval cylinder.
  • the rim angle of the channel 51 exceeds 180.
  • the vane is provided with the recesses 53 in which four springs 54 are placed pressing down the vanes to the bearing surface. Besides the pressure of springs, the vane is pressed to the bearing surface by the pressure difference, generated by the supply and draining respectively the liquid from below the vane through the openings 55.
  • each channel of the rotor 50 On one wall of each channel of the rotor 50 a rectangular groove is cut out, reaching over the entire length of the rotor. In said groove a rubber round seal 56 is placed. The diameter of the seal is greater as the depth of the groove but smaller than its width. Owing to the difference the seal remain in permanent contact with the vane. The length of the sealequals to the length of the rotor and the vane.
  • the channels 62 of the rotor 63 has a groove having its length equal to the length of the rotor, being cut out in one of walls.
  • the seal 64 is placed, made of flexible sheet metal, being deflected on two sides, thus having a shape of the letter Y. Said seal is secured against falling out of the groove by means of the Wedge 65.-The seal abuts on the vane with both spread ends, thus a two-directional tightness is secured.
  • two suitable recesses 66 are provided in order to prevent the seal to be squeezed in the clearance between the vane and the rotor.
  • Variable-capacity double-acting sliding-vane pump which being driven by means of another pump becomes an engine of variable torque, consisting of a housing enclosing a cylinder arranged therein, and a rotor with vanes mounted therein, whichvanes slide over the bearing surfaces of the cylinder as the rotor rotates, said vanes being self-aligning and sealed by means of a plate pack placed loosely in a channel cut out in each vane and pushed outwards by an insert made of an elastic material, the channel for the plates being cut out near the edge of the vane, the center of the thickness of the plate pack, remaining in contact with the bearing surface, lying in the point of intersection of the extended line of the curvature of the vane bearing surface with the cylinder bearing surface.
  • the pump of claim 2 including movable crosses with arms mounted rotatively on a control sleeve, and connected with a lever for changing the-positions of suction chambers and delivery chambers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US00226681A 1971-02-22 1972-02-16 Variable-capacity sliding-vane pump Expired - Lifetime US3824045A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
PL146413A PL67784B1 (https=) 1971-02-22
PL14923071 1971-07-05
PL15166871A PL74307B2 (https=) 1971-11-20 1971-11-20

Publications (1)

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US3824045A true US3824045A (en) 1974-07-16

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Family Applications (1)

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US00226681A Expired - Lifetime US3824045A (en) 1971-02-22 1972-02-16 Variable-capacity sliding-vane pump

Country Status (6)

Country Link
US (1) US3824045A (https=)
CH (1) CH550942A (https=)
DE (1) DE2208277A1 (https=)
FR (1) FR2127691A5 (https=)
GB (1) GB1383812A (https=)
IT (1) IT949156B (https=)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4851723A (en) * 1988-08-01 1989-07-25 Westinghouse Electric Corp. Coolant pump system for variable speed generators
US5235821A (en) * 1992-12-31 1993-08-17 Micropump Corporation Method and apparatus for refrigerant recovery
US5359971A (en) * 1993-05-07 1994-11-01 Espie Haven Rotary steam/internal combustion engine and rotary hydraulic motor
KR20160027938A (ko) 2014-09-02 2016-03-10 이동원 유압식 자동변속 자전거

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2292186A (en) * 1994-07-29 1996-02-14 John Richard Neville Roe Hinged vane motor
AUPQ479199A0 (en) 1999-12-21 2000-02-03 Merlin Corporation Pty Ltd A rotary apparatus

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1389466A (en) * 1920-06-30 1921-08-30 Glenn P White Engine
US1776452A (en) * 1928-09-19 1930-09-23 Max G Rosenthal Rotary pump and the like
US2052492A (en) * 1930-08-16 1936-08-25 Voith Gmbh J M Rotary engine
US2135760A (en) * 1934-09-15 1938-11-08 Moore Raymond John Francis Rotary engine and pump
US2387761A (en) * 1942-04-17 1945-10-30 Manly Corp Fluid pressure device
US2463118A (en) * 1946-05-14 1949-03-01 Moore Raymond John Francis Movable vane rotary pump or fluid motor
US2612110A (en) * 1947-01-11 1952-09-30 Carl J Delegard Pump and motor
US2612115A (en) * 1948-04-06 1952-09-30 Thompson Grinder Co Vane pump and vane therefor
US2804016A (en) * 1952-08-25 1957-08-27 Moore Raymond John Francis Hydraulic power transmission systems
US2842064A (en) * 1954-05-24 1958-07-08 Gunnar A Wahlmark Hydraulic pressure unit
US3234816A (en) * 1961-11-25 1966-02-15 Zahnradfabrik Friedrichshafen Adjustment mechanism
US3263912A (en) * 1963-07-23 1966-08-02 Goetzewerke Radial seal
US3334546A (en) * 1965-11-09 1967-08-08 Vuolle-Apiala Antti Ku Aukusti Fluid drive power transmission
US3452725A (en) * 1967-08-23 1969-07-01 Donald A Kelly High compression rotary i.c. engine

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1389466A (en) * 1920-06-30 1921-08-30 Glenn P White Engine
US1776452A (en) * 1928-09-19 1930-09-23 Max G Rosenthal Rotary pump and the like
US2052492A (en) * 1930-08-16 1936-08-25 Voith Gmbh J M Rotary engine
US2135760A (en) * 1934-09-15 1938-11-08 Moore Raymond John Francis Rotary engine and pump
US2387761A (en) * 1942-04-17 1945-10-30 Manly Corp Fluid pressure device
US2463118A (en) * 1946-05-14 1949-03-01 Moore Raymond John Francis Movable vane rotary pump or fluid motor
US2612110A (en) * 1947-01-11 1952-09-30 Carl J Delegard Pump and motor
US2612115A (en) * 1948-04-06 1952-09-30 Thompson Grinder Co Vane pump and vane therefor
US2804016A (en) * 1952-08-25 1957-08-27 Moore Raymond John Francis Hydraulic power transmission systems
US2842064A (en) * 1954-05-24 1958-07-08 Gunnar A Wahlmark Hydraulic pressure unit
US3234816A (en) * 1961-11-25 1966-02-15 Zahnradfabrik Friedrichshafen Adjustment mechanism
US3263912A (en) * 1963-07-23 1966-08-02 Goetzewerke Radial seal
US3334546A (en) * 1965-11-09 1967-08-08 Vuolle-Apiala Antti Ku Aukusti Fluid drive power transmission
US3452725A (en) * 1967-08-23 1969-07-01 Donald A Kelly High compression rotary i.c. engine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4851723A (en) * 1988-08-01 1989-07-25 Westinghouse Electric Corp. Coolant pump system for variable speed generators
US5235821A (en) * 1992-12-31 1993-08-17 Micropump Corporation Method and apparatus for refrigerant recovery
US5303559A (en) * 1992-12-31 1994-04-19 Micropump Corporation Method and apparatus for refrigerant recovery
US5359971A (en) * 1993-05-07 1994-11-01 Espie Haven Rotary steam/internal combustion engine and rotary hydraulic motor
KR20160027938A (ko) 2014-09-02 2016-03-10 이동원 유압식 자동변속 자전거

Also Published As

Publication number Publication date
IT949156B (it) 1973-06-11
GB1383812A (en) 1974-02-12
CH550942A (de) 1974-06-28
FR2127691A5 (https=) 1972-10-13
DE2208277A1 (de) 1972-09-14

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