US2964234A - Constant clearance volume compressor - Google Patents

Constant clearance volume compressor Download PDF

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Publication number
US2964234A
US2964234A US429660A US42966054A US2964234A US 2964234 A US2964234 A US 2964234A US 429660 A US429660 A US 429660A US 42966054 A US42966054 A US 42966054A US 2964234 A US2964234 A US 2964234A
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swash plate
shaft
stroke
piston
pump
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US429660A
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Iii Peter B Loomis
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Houdaille Industries Inc
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Houdaille Industries Inc
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036Component parts, details, e.g. sealings, lubrication
    • F04B27/1054Actuating elements
    • F04B27/1072Pivot mechanisms
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14Control
    • F04B27/16Control of pumps with stationary cylinders
    • F04B27/18Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00Machine element or mechanism
    • Y10T74/16Alternating-motion driven device with means during operation to adjust stroke
    • Y10T74/1625Stroke adjustable to zero and/or reversible in phasing
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00Machine element or mechanism
    • Y10T74/18Mechanical movements
    • Y10T74/18056Rotary to or from reciprocating or oscillating
    • Y10T74/18208Crank, pitman, and slide
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00Machine element or mechanism
    • Y10T74/18Mechanical movements
    • Y10T74/18056Rotary to or from reciprocating or oscillating
    • Y10T74/18296Cam and slide
    • Y10T74/18336Wabbler type

Description

Dec. 13, 1960 P. B. LOOMIS m 2,964,234

CONSTANT CLEARANCE VOLUME COMPRESSOR Filed May 13, 1954 2 Sheets-Sheet l Dec. 13, 1960 P. B. LOOMIS Ill 2,964,234

CONSTANT CLEARANCE VOLUME COMPRESSOR Filed May 13, 1954 2 Sheets-Sheet 2 lllllllll P; fer 5. L 00 715,122

2,964,234 CONSTANT CLEARANCE VOLUME COMPRESSOR Peter B. Loomis III, Birmingham, Mich., assignor to Houdaille Industries, Inc., a corporation of Michigan Filed May 13, 1954, Ser. No. 429,660

1 Claim. (Cl. 230-20) The present invention relates to variable displacement compressors, and more particularly, to a novel means for balancing, and for adjusting capacity, and to' a novel result of sustained high volumetric elficiency with minimal stroke and wear.

Swash plate pumps have, of course, been used for manyyears. Pumps of this type vary in structure over a wide range, but are all similar in that they operate reciprocating pistons from a rotary power input shaft by means of a swash plate or ring driven by a tilted crank associated with the power input shaft.

Although the use of such a swash plate, as above described, has been commonly used in the prior art,

to my knowledge none of the prior art pumps utilizing this method of pump piston reciprocation have provided 'a constant minimum piston clearance. In the prior art structures with which I am familiar, the pump stroke, or

the distance which the pump pistons travel, is varied by tilting the power shaft and its swash plate with respect to the rotating block of cylinders, or if a stationary cylinder block is used, by tilting the swash plate on trunnions fixed to the power shaft. Either ofthese dictates, a pump operation in which the pistonsapproach their respective piston heads at the ends of the piston stroke, to a varying degree depending upon the angle of swash plate adjustment. In such an arrangement, the

piston clearance, or distance between the piston and the end of the cylinder when the piston is at'the end of its valve until approximately 70% of the stroke is completed. The output capacity at 70% of full stroke may under such circumstances therefore be zero. In automotive air conditioning, particularly, it is often desirable to operate the compressor at very high speed but to maintain a capacity equal to that of full displacement. at idling. If. this requires 73% of full stroke, the inertia forces and Wear are high.

In the present compressor, a small fraction of full- .stroke can deliver the rated capacity at top speed, with -low forces and Wear, and automatic control is greatly simplified. The need for by-pass valve, variableratio drive, and disconnect clutch is also. eliminated. By thus providing for a constant, small, clearance volume, ah-igh volumetric efficiency is retained.

Another serious drawback to the swash plate pump structures of the prior art is the presence of relatively large. unbalanced forces found therein. While, a tilting .swash plate is, of course, statically balanced, it will become dynamically unbalanced as soon asit is, tilted *relative to the input'shaft.

of the swash plate type.

2,954,234 FatentedDec. 13 1960 'I 'hus, as the tilt occursza couple is setup, asa result of'centrifugal force, tending to cause the swash plate to assume its untilted or neutral position.- At the same time, the force couple set up tends to cause an unbalanced load. on the bearings of the drive shaft causing vibration and wear. The structure of the present invention therefore contemplates the provision of dynamic balancing apparatus linked to the swash plate for automatic controlled movement thereby to provide an oppositely acting-balancing couple on the rotating shaft, and the bearings thereof.

In overcoming the disadvantages found in theprior .art', and as discussed above, the present invention con.-

templates the provision of a swash plate supported on a rotating drive shaft by means. of trunnions mounted for reciprocation on the drive shaft axially thereof. Axial "movementof the trunnions of the swash plate causes tilting movement of the plate about a control point adjacent the periphery of the swash plate as well as a tilting about the trunnions themselves. This combined tilting action causes the end of'the piston stroke to'o'ccur atv substantially the. same. spot. irrespective of the angular adjustment of the swash plate.

Elimination. of the unbalance found in prior art structures. isaccomplished in the present invention through the pivotal mounting of counterweights on trunnions extendingparallel tothe support trunnions of the swash plate by a connecting linkage such that the adjustment of the swash plate to a particular angle relative to the rotating ,drive shaft will simultaneously cause an adjustment of the-angular position of the counterweights to providea substantially identical, counteracting, force couple. It is therefore: an object of the present invention to provide a novel constant clearance volume compressor A furtherobject-of the present invention is to provide a swash plate'type pump having a substantially constant .clearance volume-under all pump stroke adjustments.

Still a further object of the present invention is ,to pro- .vide animproved stroke-adjusting apparatus for swash plate pumps or compressors.

Yet another object of the present invention is-to provide .a novel piston stroke adjustment and. counter-balancing apparatus for swash plate-pumps .whereby dynamic unbalance. is eliminated at all adjusted conditions of the pump stroke.

A feature ofv the present invention is an adjusting actuator operable to vary theswash' plate angle of a'pump .by movement of the swash platetrunnions axially along. the longitudinal axis. of rotation;

Yet afurther feature. ofthe. invention is the incorporationin atsw-ash plate type pump of an adjustment. actuator mounted coaxially. with: the swash platedrive shaft for adjustingthe angle ofthe swash. plate. relative thereto.

Another feature-of the. invention resides inthe provision of ardynamic balancing apparatus connected. to'the swash plate, for simultaneous but opposite tiltingyaction relative thereto.

Still furtherobjects and features of the. present invention will at once become apparent. to those skilledin the artfrom a, consideration, of the. attached. drawings wherein:

, Figure 1. is a. side .elevational view intcrossasectionillustrating. the. pump in its maximum stroke conditiont Figure 2 is an elevational view of thepump of the present. invention; in cross-section andshowing the. ad-

justment of the parts-to their neutral condition;

Figure 3 is a cross-sectional viewtaken along; the

men-1 111 of., Fig ure 1,'..an d.

FigureA-is across-sectional view' of: the-swash. k n lonathe line IV:-IV.of Figure 1...

As shown on the drawings:

As illustrated in Figures 1 and 2, the pump of the present invention comprises a pump housing having a plurality of radially spaced, axially extending cylinders 11 integral with, or fixedly secured, to one end thereof. The drive shaft 12 is rotatably supported in bearings.13 in the housing end cap 11a. The opposite end of the shaft 12 is slidably splined to the sleeve 14 which is rotatably mounted within the bearing 15 thereby providing a bearing support for the left hand end of the shaft -12.

Pistons 16 are reciprocably mounted within the cylinders 11 and are reciprocated by means of connecting rods 18 universally secured to the pistons 16 at 19 and universally secured to a common drive ring 20 at 21. The ring 20 is prevented from rotation relative to the housing .lfl by means of a splined connection com-prising a generally arcuate spline 22 extending longitudinally of the housing, and a clevis 23 fixedly secured to the ring 20. It is to be understood, of course, that a plurality of splines may be utilized if so desired.

The ring 20 is caused to reciprocate the several connecting rods 18 with their associated pistons 16, by means of the swash plate 25 which is mounted therein for antifrictional rotation therewith through the balls 26. The swash plate 25 is caused to rotate with the sleeve 14 by means of the trunnions 27 which are secured to the sleeve and upon which the plate 25 is pivotally mounted.

It will be seen that rotation of the swash plate 25, when lying in a plane perpendicular to the axis of the shaft 12 as shown in Figure 2, will not cause any re- .ciprocation of the pistons 16. However, as the swash plate 25 assumes a gradually tilted condition, the extreme of which is shown in Figure I, rotation thereof will cause the ring 20 to nutate thereby successively re- 'ciprocating the pistons 16 into the furthest left hand position'as viewed in Figure 1.

Reciprocation of the pistons 16 will cause a pumping action, carried out in a conventional manner not illustr'ated. It is to be understood, however, that each of the cylinders 11 may be connected to a common source by means of a check valve, and to a common outlet by means of an oppositely acting check valve so as to provrde a conventional force pumping action. It is to be understood that various valve arrangements may be .utilized with the present invention without departing from the novel concepts thereof.

- Adjustment of the angularity of the swash plate 25,

which will vary the stroke of the pistons 16, is accomplished in a novel manner. As shown in Figures 1, 2, and 4, the sleeve 14 is slidably mounted on the shaft 12 thereby-permitting axial movement of the trunnions 27. The swash plate 25 is provided with a radially extending control arm 28 having an arcuate slot 29 adjacent the outer end thereof and in cooperation with a pin 30 carried by the clevis 31; The clevis 31 is integral with, or affixed to'the shaft 12 for rotation therewith, and the center of the arc of the slot 29 is coincident with the center of the ball connection 21 shown adjacent the pin 30 in Figure 1. It will be understood that the centers of the plurality of balls 21 which connect the rods 18 to the annular ring 20 lie on a circle and that the center point of the arc of radius of the slot 29 lies on that circle.

In view of the relationship set out above between the sleeve 14 and the shaft 12, it will be observed that reciprocation of the sleeve 14 from an extreme left hand posltion, shown in Figure 2, to an extreme right hand position shown in Figure 1, will cause the swash plate 25 to pivot about its trunnions 27 and also to pivot and slide relative to the pin 30 passing through the control arm28. By placing the pin 30 substantially at the same "aeeaaat.

distance from the center of rotation of the shaft 12 as the endi2lof theconnecting rods 18, it will be found that 4 taneously adjacent the control arm 28 will maintain a substantially constant axial position. This is achieved through the provision of the arcuate slot in the arm 28 and may be controlled in a rather precise manner through control of the shape of the slot 29.

In effect, the linkage shown causes the plane of the swash plate 20 to tilt about a point on the circular line upon which the centers of the ends 21 of the connecting rods 18 lie when in their respective furthermost left-hand position.

As a result of this action, the clearance volume be tween the left-hand end of the pistons 16 and the lefthand end of the cylinders 11, when the pistons 16 are in their furthermost left-hand, or compression stroke, position remains substantially constant irrespective of the length of the piston stroke. Thus, it is possible to provide a very small volume clearance and cause substantially all of the fluid entering the respective cylinders on the suction stroke to be exhausted on the compression stroke, thereby permitting short stroke, high speed operation with high volumetric efficiency. Such operation, as explained above, minimizes wear and possible piston seizure by reducing piston speeds and reducing operating friction losses and at the same time provides satisfactory out put volume at high speeds.

Axial adjustment of the sleeve 14 may be accomplished in various manners, one of which is shown in the figures. As may be seen from Figures 1 and 2, a hydraulically operated piston 33 is connected to a reciprocal piston rod 34 carrying thrust bearings 35, 36 which cooperate with the left-hand end of the sleeve 14. By pumping an incompressible fluid into the chamber 37, or, alternatively, chamber 38, the axial position of the piston 33 may be accurately controlled. With the piston 33 in a fixed, adjusted position, the sleeve 14 will be maintained securely in an axial adjusted position relative to the shaft 12 by the thrust bearings 35 and 36. In such adjusted position, the sleeve 14 will absorb a portion of the axial load imposed upon the system by the reciprocating pistons 16 and the remainder of the load will be absorbed through the clevis 31 and bearing 13 which is provided with a thrust surface 13a.

The entire rotating system of the pump described above is both statically and dynamically balanced by means of a novel balancing linkage automatically adjustable with adjustment of the swash plate. As may be seen in Figures 1 and 2, weight 40 is pivotally mounted as at 41 to the shaft 12 to rotate with the swash plate 25. A connecting link 42 secures the ring 40 to the control arm 28 by means of the clevis pins 43 and 44, respectively, such that movement of the sleeve 14, and hence movement of the pin 44 will cause tilting of the annular ring 40 in a direction opposite to the tilt of theswash plate 25. Thus, the force couples associated with the swash plate 25 and weight 40, respectively, will balance each other out relative to the respective support bearings 14 and 13, thereby minimizing the tendency of the shaft 12 to vibrate within those bearings.

Static balancing of the system may be simply achieved through the addition of the weight 48 disposed at relative to the clevis 31. Additional weight to balance the link 42, both statically and dynamically, is provided at 49 on the annular ring 40. It will be seen that adjustably positioning the weights 40 and 49, in the manner above described, will substantially balance, both dynamically and statically, the rotating system of the present pump in all conditions of stroke adjustment. It will also be perceived that this system is unusually simple and that simplicity is achieved, in part, through the extremely simple, single, link 42 which acts to tilt the plate 25 and weight 40 in opposite directions. The single link may be used in the present invention since the swash plate 25 tends to pivot, on its adjustment,

central axis, while the weight 40 pivots about its central axis. In view of this arrangement, the positioning of the single link 42, as shown, provides a cross over efi'ect Without adding a bulky or complex balance weight control which crosses over the axis of the shaft 12.

It will be understood that other and further variations may be made in the structure described above without departing from the novel concepts of the present invention and it is therefore intended that the scope of the present invention be limited only by the scope of the appended claim.

I claim as my invention:

A constant clearance volume swash plate actuated pump comprising a rotating shaft, a swash plate, a sleeve mounted for rotation with said shaft in slidable relationship thereto and carrying radially extending trunnions pivotally supporting said swash plate, a plurality of axially disposed pistons circumferentially surrounding said shaft, a ring mounted on said swash plate with said swash plate being journalled therein, each of said pistons having a connecting rod having a pivotal connection therewith and with said ring, the connections with said ring being aligned in a circle, an arm member secured to said swash plate having a slot in the end thereof extending in generally radial alignment with said swash plate and formed in register with the pivotal connections of said connecting rods and said ring, a second arm member secured for rotation with said shaft in fixed axial relationship thereto, pin means secured to the end of said second arm member and positioned in said slot whereby relative axial movement of said sleeve and said trunnions relative to said shaft causes tilting of said swash plate about a point adjacent the periphery thereof, said point being defined by said pin and being in register with said circle to afford said constant clearance volume, and means for moving said sleeve and said trunnions relative to said second arm member.

References Cited in the file of this patent UNITED STATES PATENTS 803,149 Clark Oct. 31, 1905 1,825,691 Hall Oct. 6, 1931 1,869,189 Eggert July 26, 1932 2,031,346 Wahlmark Feb. 18, 1936 2,231,100 Wahlmark Feb. 11, 1941 2,337,511 Wahlmark Dec. 21, 1943 2,451,453 Tuxhorn Oct. 12, 1948 2,513,083 Eckert June 27, 1950 2,520,632 Greenhut Aug. 29, 1950 2,706,384 Schott Apr. 19, 1955 2,737,900 Smith Mar. 13, 1956 FOREIGN PATENTS 276,072 Great Britain Aug. 18, 1927 493,976 Italy May 12, 1954 605,215 France May 21, 1926

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Cited By (46)

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US3133447A (en) * 1957-02-16 1964-05-19 Mercier Pierre Reciprocating engine or pump
US3151528A (en) * 1960-12-02 1964-10-06 Clevite Corp Swashplate engine
US3663226A (en) * 1969-04-22 1972-05-16 Arnold E Biermann Variable piston-stroke mechanisms
US3861829A (en) * 1973-04-04 1975-01-21 Borg Warner Variable capacity wobble plate compressor
DE2534251A1 (en) * 1974-07-31 1976-02-12 Sankyo Electric Co COOLANT COMPRESSOR
US3959983A (en) * 1973-04-04 1976-06-01 Borg-Warner Corporation Variable capacity wobble plate compressor
US4061443A (en) * 1976-12-02 1977-12-06 General Motors Corporation Variable stroke compressor
US4073603A (en) * 1976-02-06 1978-02-14 Borg-Warner Corporation Variable displacement compressor
US4077269A (en) * 1976-02-26 1978-03-07 Lang Research Corporation Variable displacement and/or variable compression ratio piston engine
DE2751846A1 (en) * 1976-12-06 1978-06-08 Hans Bieri PROCEDURE FOR BALANCING MASS FORCES IN A PISTON MACHINE AND A PISTON MACHINE WITH A SWASHPLATE OR SWASHPLATE TO PERFORM THE PROCEDURE
DE2854049A1 (en) * 1977-12-16 1979-06-28 Borg Warner SWASHPLATE COMPRESSORS
EP0040161A1 (en) * 1980-05-14 1981-11-18 François Couillard Wobble plate of an axial-type piston pump
FR2484555A1 (en) * 1980-05-14 1981-12-18 Couillard Francois High accuracy dispensing pump for chromatography - has plungers held in contact with swashplate with curved track to reduce inaccuracy
EP0102691A1 (en) * 1982-08-02 1984-03-14 Diesel Kiki Co., Ltd. Variable displacement compressor
US4575317A (en) * 1985-06-26 1986-03-11 M&T Chemicals Inc. Constant clearance positive displacement piston pump
DE3545200A1 (en) * 1984-12-22 1986-07-03 Toyoda Automatic Loom Works SWASH DISC COMPRESSOR WITH VARIABLE LIFT
US4632640A (en) * 1984-02-21 1986-12-30 Sanden Corporation Wobble plate type compressor with a capacity adjusting mechanism
EP0207613A1 (en) * 1985-05-20 1987-01-07 Sanden Corporation Variable capacity wobble-plate type compressor
EP0216612A2 (en) * 1985-09-20 1987-04-01 Sanden Corporation Wobble plate type compressor
US4729718A (en) * 1985-10-02 1988-03-08 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Wobble plate type compressor
EP0259760A2 (en) * 1986-09-02 1988-03-16 Nippondenso Co., Ltd. Variable displacement swash-plate type compressor
EP0280479A2 (en) * 1987-02-19 1988-08-31 Sanden Corporation Wobble plate compressor
EP0282190A1 (en) * 1987-02-19 1988-09-14 Sanden Corporation Wobble plate compressor
EP0281819A1 (en) * 1987-02-19 1988-09-14 Sanden Corporation Wobble plate type compressor with variable displacement mechanism
US4778348A (en) * 1986-07-23 1988-10-18 Sanden Corporation Slant plate type compressor with variable displacement mechanism
US4780059A (en) * 1986-07-21 1988-10-25 Sanden Corporation Slant plate type compressor with variable capacity mechanism with improved cooling characteristics
US4782712A (en) * 1986-09-03 1988-11-08 Hitachi, Ltd. Variable displacement compressor
US4801248A (en) * 1986-09-05 1989-01-31 Hitachi, Ltd. Variable capacity swash plate compressor
US4815358A (en) * 1988-01-27 1989-03-28 General Motors Corporation Balanced variable stroke axial piston machine
US4836090A (en) * 1988-01-27 1989-06-06 General Motors Corporation Balanced variable stroke axial piston machine
US4850810A (en) * 1986-09-16 1989-07-25 Sanden Corporation Slant plate type compressor with variable displacement mechanism
US4886423A (en) * 1986-09-02 1989-12-12 Nippon Soken, Inc. Variable displacement swash-plate type compressor
US5063829A (en) * 1989-08-09 1991-11-12 Hitachi, Ltd. Variable displacement swash plate type compressor
US5079996A (en) * 1991-01-08 1992-01-14 General Motors Corporation Positive displacement control for a variable displacement compressor
US5127314A (en) * 1990-11-30 1992-07-07 General Motors Corporation Compensating cam socket plate torque restraint assembly for a variable displacement compressor
DE4405034A1 (en) * 1994-02-17 1995-08-24 Audi Ag Axial piston swash plate compressor
US5617759A (en) * 1994-06-14 1997-04-08 Nakanishi Dental Mfg. Co., Ltd. Mechanism for machining and grinding tool for converting rotational movement into reciprocating movement
WO2000014409A1 (en) * 1998-09-02 2000-03-16 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Axial piston motor
EP0911522A3 (en) * 1997-10-21 2001-06-06 Calsonic Kansei Corporation Swash plate type compressor
DE10152205B4 (en) * 2000-10-24 2004-09-30 Kabushiki Kaisha Toyota Jidoshokki, Kariya Displacement control device for a variable displacement compressor
US20040216603A1 (en) * 2003-04-04 2004-11-04 Otfried Schwarzkopf Reciprocating compressor, in particular CO2 compressor for vehicle air-conditioning units
US6957604B1 (en) * 1999-08-18 2005-10-25 Zexel Gmbh Axial-piston drive system with a continuously adjustable piston stroke
US20090078113A1 (en) * 2004-10-01 2009-03-26 Zexel Valeo Compressor Europe Gmbh Reciprocating Piston Machine, in Particular a Compressor for a Vehicle Air-Conditioning Unit
US20090196768A1 (en) * 2008-02-01 2009-08-06 Caterpillar Inc. Floating cup pump assembly
US20100074765A1 (en) * 2003-04-04 2010-03-25 Otfried Schwarzkopf Reciprocating Compressor, in Particular CO2 Compressor for Vehicle Air-Conditioning Units
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US803149A (en) * 1905-02-03 1905-10-31 Edward S Clark Parallel adjustable-stroke mechanism.
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US1825691A (en) * 1927-09-08 1931-10-06 Hall Edwin Sydney Internal combustion engine
US1869189A (en) * 1929-09-20 1932-07-26 Gustav B Eggert Transmission
US2031346A (en) * 1932-10-17 1936-02-18 Rystrom Charles H Fuel injection pump
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US2337511A (en) * 1940-08-01 1943-12-21 Gunnar A Wahlmark Antifriction bearing
US2451453A (en) * 1944-08-14 1948-10-12 Blaine M Tuxhorn Apparatus for controlling rotation of vehicle wheels
US2513083A (en) * 1945-05-24 1950-06-27 Samuel B Eckert Wobbler drive mechanism
US2520632A (en) * 1945-03-22 1950-08-29 Torq Electric Mfg Company Hydraulic pump or motor
US2706384A (en) * 1950-09-29 1955-04-19 Schott Transmission Co Direct drive variable ratio hydraulic transmission of the automatic or manual type
US2737900A (en) * 1952-06-06 1956-03-13 Albert P Smith Variable displacement pump unit

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US803149A (en) * 1905-02-03 1905-10-31 Edward S Clark Parallel adjustable-stroke mechanism.
FR605215A (en) * 1924-12-06 1926-05-21 Transmission
GB276072A (en) * 1926-05-18 1927-08-18 Richard Rutherford Improvements in and relating to crankless engines, pumps, compressors and the like
US1825691A (en) * 1927-09-08 1931-10-06 Hall Edwin Sydney Internal combustion engine
US1869189A (en) * 1929-09-20 1932-07-26 Gustav B Eggert Transmission
US2031346A (en) * 1932-10-17 1936-02-18 Rystrom Charles H Fuel injection pump
US2231100A (en) * 1938-05-09 1941-02-11 Gunnar A Wahlmark Fluid motor and pump
US2337511A (en) * 1940-08-01 1943-12-21 Gunnar A Wahlmark Antifriction bearing
US2451453A (en) * 1944-08-14 1948-10-12 Blaine M Tuxhorn Apparatus for controlling rotation of vehicle wheels
US2520632A (en) * 1945-03-22 1950-08-29 Torq Electric Mfg Company Hydraulic pump or motor
US2513083A (en) * 1945-05-24 1950-06-27 Samuel B Eckert Wobbler drive mechanism
US2706384A (en) * 1950-09-29 1955-04-19 Schott Transmission Co Direct drive variable ratio hydraulic transmission of the automatic or manual type
US2737900A (en) * 1952-06-06 1956-03-13 Albert P Smith Variable displacement pump unit

Cited By (64)

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