Search Images Maps Play YouTube News Gmail Drive More »
Sign in
Screen reader users: click this link for accessible mode. Accessible mode has the same essential features but works better with your reader.

Patents

  1. Advanced Patent Search
Publication numberUS3292554 A
Publication typeGrant
Publication dateDec 20, 1966
Filing dateJan 12, 1965
Priority dateFeb 15, 1964
Publication numberUS 3292554 A, US 3292554A, US-A-3292554, US3292554 A, US3292554A
InventorsHessler Erwin
Original AssigneeHydraulik Gmbh
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Axial piston device
US 3292554 A
Abstract  available in
Images(2)
Previous page
Next page
Claims  available in
Description  (OCR text may contain errors)

1956 E. HESSLER AXIAL PISTON DEVICE Filed Jan. 12. 1965 2 Sheets-Sheet 1 W n/r09 ERWN HESSLER Dec. 20, 1966 I E. HESSLER 3,292,554

AXIAL PISTON DEVICE Filed Jan. 12. 1965 2 Sheets-Shet 2 ERWIN HESSLVER 3 mwwd M ME Wy United States Patent Claims. ((31. 103-173 This invention relates in general to pump construction, and in particular to a new and useful high speed, high pressure axial piston pump in which the delivery fluid is separated from the lubricating fluid of the drive and including a control piston for simultaneously shifting a wobble plate for varying the stroke of the pistons of the pump and for shifting an inertial mass for maintaining the balance of the pump parts.

The present invention is particularly applicable for a pump in which the delivered fluid is separated from the operating fluid of the pump drive. Such a system is used, for example, when emulsified water is to be delivered. as a medium for the operation of a hydraulic machine, press, and the like, which machine operates at high pressures and where the medium is not suitable as the operating fluid for the drive mechanism of the pump. In such a construction, the operating fluids and the delivered fluids must be separated from each other and there should be no leakage so that the one fluid would come into contact with the other fluid.

For high pressure axial piston pumps with a direct drive of a hydraulic press it is necessary that the delivery be variable rapidly and infinitely between 0 and a maximum. This can be done by displacement of a swash plate mounted on a cradle by means of a servo drive unit which varies the position of the swash plate and thus the stroke of the pistons. Such a pump, due to its high speed, also requires as complete as possible a compensation of the inertia forces of the revolving parts in every rotative position. Prior to the present invention, inertial compensation of such pumps was done by means of counterweights provided on the side of the swash plate facing the cylinder block which were shifted separately by complicated mechanism in order to maintain the center of gravity of the pump along the pump axis to as great an extent as possible. Such constructions, however, were possible only with small pumps or engines. Larger pumps require, due to their power and due to the larger forces which act, a better inertia compensation in every cradle position. In addition, the axial piston pump construction cannot be employed Where the operating fluid is separated from the lubricating fluid.

At the present time, there are axial piston pumps or machines having separate operating fluid and lubricating fluid systems where longitudinally extendingsbores of the working pistons are closed on the disc of the displacement zone by longitudinally displaceable diflerential pistons. The large working surface of the pistons is loaded by the flow medium, for example an oil emulsion, while the small working surfaces can push luricating oil from the closed off bore portion of the longitudinal bore to the points of lubrication and to the relief zones of the working pistons. Structural apparatus necessary for such a construction is extremely expensive. While it largely. prevents the passage of flow medium into the zone of the lubrication points, it does not necessarily prevent the passage of lubricating oil into the flow liquid. An adjustable inertia compensation of the revolving machine parts is not provided in such a pump construction.

In accordance with the invention there is provided a high speed, infinitely variable high pressure axial piston pump having ideal inertia compensation and a practically complete separation of the working or operating fluids 3,292,554 Patented Dec. 20, 1966 ice and the delivered fluids. In accordance with the. invention, the pump includes a partition tightly sealing the flow medium or delivered fluid from the drive fluid in the interior of the pump with which the working pistons are guided. The construction includes a servo piston or control piston which is guided centrally in the partition and may be moved to adjust the counterweight and the swash plate for piston displacement simultaneously so that inertial compensation is automatically made. The principal advantage of the pump construction is that despite a relatively small structural size of pump the intertial compensation in every cradle position is improved as compared with the known pump constructions, and, in addition, the separation of the liquids within the pump is accomplished by means of the partition flange. A feature of the construction is that the same partition wall which is provided for the separation of the liquids is used as a supporting wall and guide member for the working pistons and for the control piston. The wall divides the pump interiorly into two tightly closed compartments, one for the drive mechanism and the transmission oil and one for the cylinder block and the flow medium and any leakage liquid of the flow medium which can flow off unhindered. The central guidance of the control piston permits a construction to provide for a movement of the swash plate for varying piston displacement as well as for simultaneously adjusting the counterweight in a simple and easy manner.

Accordingly, it is an object of this invention to provide a high speed, infinitely variable high pressure axial piston pump having means for separating the pump operating and delivery fluids and for providing for inertial compensation during a change in the output of the pump.

A further object of the invention is to provide a high speed axial piston pump having a partition wall dividing the pump so that the pump operating fluid and the delivery fluid are maintained separate and with a control piston slidable in the partition wall for simultaneously adjusting the stroke of the piston and the location of balancing Weights for insuring that the pump is inertially balanced at all speeds and outputs.

A further object of the invention is to provide a pump which is simple in design, rugged in construction and economical to manufacture.

The various features of novelty which characterize the invention are pointed out with particularity in the claims annexed to and forming a part of this specification. For a better understanding of the invention, its operating advantages and specific objects attained by its use, reference should be had to the accompanying drawings and descriptive matter in which there is illustrated and 'described a preferred embodiment of the invention.

In the drawings:

FIG. 1 is a longitudinal section through a pump constructed in accordance with the invention; and

FIG. 2 is a section taken along the line 22 of FIG. 1.

Referring to the drawings in particular, the invention embodied therein comprises a pump with a valve block or cylinder head 1 which is firmly connected to a spacer ring 2 which, in turn, is connected at its opposite end with a flange plate or disk member 3. The drive mechanism for the pump comprises a shaft journal 4 having a shaft head 5 rotatable within the interior of the spacer ring 2. The inner end of the shaft head 5 is provided with a semicircular recess 6 in which is pivotal a cradle 7 which. carries a swash plate 8 mounted axially and radially on rolls or roller bearings for rotation about its axis within the cradle. The swash plate 8 carries piston shoes 9 which slide in an elliptical path according to the pivotal position of the cradle 7.

A pullback disk 10 is rotatably mounted on rollers tions 12 in the spherical shoes 9 and are guided in bushings 13 of partition wall 15, The bushings 13 are provided with low pressure packings 14 which seal the space 16 formed by the partition 15 in accordance with the invention.

' The partition 15 also function as .a guiding plate or flange for the drive mechanism. The space 16 serves as a collecting chamber for any leakage fluid of the flow or delivering medium and it communicates with a drain bore 41 defined in the cylinder block 1.

In accordance with a further feature of the invention, the partition wall 15 is provided with a central guiding bushing 17 which is also held in the cylinder block 1. The partition wall 15 insures that the drive mechanism containing the transmission oil or operating fluid is tightly separated from the cylinder block 1 containing the emulsified fluid medium or delivery fluid so that in practice there are two compartments formed within the interior of the pump.

The pistons .11 move in bushings 18 provided with high pressure packings 19. The bushings 18 define valve cages 20 and a valve seat for an inlet valve 21 which is disposed for axial movement parallel to the axis of the pump. The valves 21 can be easily replaced by releasing a threaded closure 22 without disassembly of the pump. All the inlet valves (only one being indicated) are connected by a ring channel or annular passageway 23 with a suction passage 24 which is connected to a suction line (not shown). A pressure line (not shown) is connected to a discharge passage 25 which, in turn, connects through an annular channel or ring channel 26 to discharge valve cages 27 which are defined in radially extending passages of the cylinder block 1. A discharge valve 28 may be removed in the manner similar to the inlet valve by removing a threaded closure 29. This closure may also be removed for the replacement of packings without disassembly of the pump.

In accordance with a further feature of the invention, in the center of the .cylinder block 1 there is arranged a guide bushing 17 in which is axially displaceable a servo piston or control piston 30. The control piston 30 is displaced by fluid pressure in accordance with the positioning of a control piston element or rod member 31 having control portions 31a and 31b of relatively large diameter separated by a flat or small-diameter portion 316.

The ring surface or annular surface 33 of the servo piston 30 is continuously loaded with a control oil pressure through a connection 32 defined in the .cylinder block 1. If the control piston element 31 is displaced in the direction of the arrow, the control channels 34 and 35 are connected together and the control oil flows into the pressure zone behind the servo piston 30 to displace the piston in the direction of the arrow'until the control edges of the piston 31a and 31b interrupt the connection of the control channels 34 and 35. When displacement of the control piston is opposite to the di'? rection of the arrow, the control channel 34 is closed by the control surface 31a and the control pressure loads only the annular surface 33 of thepiston 30. The fluid from the pressure zone 34 then flows off through the control channel 35 and the central bore 36 of the piston 30 until the piston is displaced conuter to the direction of the arrow to-move the control surfaces 31a and 31b back to the position indicated in FIG. 1.

In accordance with a further provision of the invention, a rack 37 is rotatably mounted and axially displaceable within the spacer ring 2 and the shaft head 5. It is rotatably connected with the servo piston 30 by radial and axial bearings and 46. The rack 37 ,is engaged with a toothed segment 38 which is rigidly connected with a pinion 39. The pinion 39 meshes with serations 42 formed on the surface of the cradle 7 and also with serations 43 formed on the surface of a counterweight 40 so that each is displaced correspondingly by adjustment of the position of the rack 37. If the servo piston 30 is moved in the direction of the arrow, the rack 37 is displaced axially in the same direction and thus rotates the toothed segment 38 and the pinion 39 clockwise. Thus, at the same time the cradle 7 is pivoted and the counterweights 40 are shifted to a compensating degree. The weights are guided in grooves 44 and are displaced toward or away from the center or axis of the pump. The shifting is such that in every position of the cradle 7 the weights 4%} are moved by an amount to compensate as perfectly as possible for the shifting of the inertial mass in the pump structure.

While a specific embodiment of the invention has been shown and described in detail to illustrate the application of the inventive principles, it will be understood that the invention may be embodied otherwise without departing from such principles.

What is claimed is:

1. A high pressure axial piston pump comprising a pump housing including a cylinder block having a plurality of concentrically arranged axially extending pump cylinders therein, a piston axially slidable in each of said pump cylinders, a swash plate pivotally mounted within said pump housing for tilting away from a plane normal to the pump axis, said swash plate including a rotatable member articulated to said pistons for displacing said pistons during rotation thereof in accordance with the amount of tilt of said swash plate, inlet and discharge valve means connected to said piston cylinders in said.

cylinder block for the drawing in and discharging of a delivery fluid, a partition dividing said pump housing and separating the operating fluid for said swash plate from the delivery fluid in said cylinder block, counterweight means within said housing mounted for displacement, and

control'piston means slidable in said housing and connected to said counterweight means and said swash plate for shifting said counterweight and said swash plate.

2. A high pressure axial piston pumpcomprising a cylinder block having a plurality of concentrically ar discharge of a delivery fluid, a partition dividing said" pump housing and separating the operating fluid for said swash plate from the delivery'fluid in said cylinder block, said partition having a central guide bushing with a bore therein for said piston control means, counterweight means within said housing mounted for displacement, and control piston means slidable in said housing and connected to said, counterweight means and said swash plate for shifting said counterweight and said swash plate simultaneously. i

3. A high pressure axial'piston pump comprising a cylinder block having a plurality of concentrically arranged pump cylinders therein, a piston axially slidable in each of said pump cylinders, a swash plate pivotally mounted within said pump, a pump housing, said swash plate including a rotatable member articulated to said pistons for displacing said pistons during rotation thereof in accordance with the amount of tilt of said swash plate, inlet and discharge valve means connected to said piston cylinders in said cylinder block for the drawing in and discharge of a delivery fluid, a partition dividing said pump housing and separating the operating fluid for said swash plate from the delivery fluid in said cylinder 'block, counterweight means within said housing mounted for dis: placement, and control piston means slidable in said housing and connected to said counterweight means and said swash plate for shifting said counterweight and said swash plate simultaneously and including :a rack slidable in said housing, a toothed segment rotatably mounted within said housing in operative engagement with said rack, a pinion carried by said toothed segment and rotatable therewith upon displacement of said rack, said swash plate having a cradle with a tooth portion thereon in engagement with said pinion and being displaceable upon rotation of said pinion.

4. A high pressure axial piston pump according to claim 3, wherein said toothed segment and said rack and said pinion and said gear portion of said cradle are connected to said counterweight such that said counterweight is shifted upon shifting of the position of said cradle.

5. A high pressure pump according to claim 3, including means mounting said counterweight for radial movement toward and away from the axis of said pump, said means including a T-shaped groove, said counterweights having an end with a portion that fits in said groove and is slidable therein.

6. A pump comprising a cylinder block having a central axially extending bore for a control piston defined therein, said cylinder block having a plurality of :angularly spaced axially extending pump cylinders defined around the central bore, a pump piston slidable in each of said pump cylinders, inlet and outlet valveand passage means defined in said cylinder block for the suction of a circulating fluid into each of said pump cylinders and for the discharge of said circulating fluid during operation of said pump pistons, wall means defining with said cylinder block a housing, a shaft rotatably mounted in said housing, a swash plate, a partition wall located between said swash plate and said pump cylinders and dividing the interior of said housing into an operating fluid chamber and a delivery fluid chamber, a swash plate cradle carrying said swash plate and connected to said shaft for rotation therewith, said swash plate cradle being mounted on said shaft for pivotal movement for shifting said swash plate out of a plane normal to the axes of said pump cylinders for varying the strokes of said pistons, a control piston slidable in the central bore of said cylinder block, a balancing mass displaceably mounted in said housing, and means movable by said control piston to pivot said cradle and to shift said balancing mass.

7. A pump comprising a cylinder block having a central axially extending bore for a control piston defined therein, said cylinder block having a plurality of angularly spaced axially extending pump cylinders defined around the central bore, a pump piston slidable in each of said pump cylinders, inlet and outlet valve and passage means defined in said cylinder block for the suction of a circulating fluid into each of said pump cylinders and for the discharge of said circulating fluid during operation of said pump pistons, wall means defining with said cylinder block a housing, a shaft rotatably mounted in said housing, a swash plate, a partition wall located between said swash plate and said pump cylinders and dividing the interior of said housing into an operating fluid chamber and a delivery fluid chamber, a swash plate cradle carrying said swash plate and connected to said shaft for rotation therewith, said swash plate cradle being mounted on said shaft for pivotal movement for shifting said swash plate out of a plane normal to the axes of said pump cylinders for varying the strokes of said pistons, a control piston slidable .in the central bore of said cylinder block, a balancing mass displaceably mounted in said housing, and means movable by said control piston to pivot said cradle and to shift said balancing mass, said control piston having a bore defined therethrough, means for directing a control fluid to one side of said control piston, said control piston having passages defined therethrough and communicating with said bore for directing the control fluid against an end of said control piston for displacing said control piston, and a control rod element slidable in the bore of said control piston for regulating the flow of the control fluid in said passages.

8. A pump comprising a cylinder block having a cen tral axially extending bore for a control piston defined therein, said cylinder block having a plurality of angularly spaced axially extending pump cylinders defined around the central bore, a pump piston slidable in each of said pump cylinders, inlet and outlet valve and passage means defined in said cylidner block for the suction of a circulating fluid into each of said pump cylinders and for the discharge of said circulating fluid during operation of said pump pistons, wall means defining with said cylinder block a housing, a shaft rotatably mounted in said housing, a swash plate, a partition wall locate-d between said swash plate and said pump cylinders and dividing the interior of said housing into an operating fluid chamber and a delivery fluid chamber, a swash plate cradle carrying said swash plate and connected to said shaft for rotation therewith, said swash plate cradle being mounted on said shaft for pivotal movement for shifting said swash plate out of a plane normal to the axes of said pump cylinders for varying the strokes of said pistons, a control piston slidable in the central bore of said cylinder block, a balancing mass displaceably mounted in said housing, and means movable by said control piston to pivot said cradle and to shift said balancing mass including a rack having teeth thereon, a segment pivotally mounted in said housing and having teeth in engagement with said rack and being pivotable upon displacement of said rack with said control piston, said segment having pinion means engageable with said weight and cradle for shifting said weight and said cradle simultaneously.

9. A pump comprising a cylinder block having a central axially extending bore for a control piston defined therein, said cylinder block having a plurality of angularly spaced axially extending pump cylinders defined around the central bore, a pump piston slidable in each of said pump cylinders, inlet and outlet valve and passage means defined in said cylinder block for the suction of a circulating fluid into each of said pump cylinders and for the discharge of said circulating fluid during operation of said pump pistons, wall means defining with said cylinder block a housing, a shaft rotatably mounted in said housing, a swash plate, a swash plate cradle carrying said swash plate and connected to said shaft for rotation therewith, said swash plate cradle being mounted on saidshaft for pivotal movement for shifting said swash plate out of a plane normal to the axes of said pump cylinders for varying the strokes of said pistons, a control piston slidable in the central bore of said cylinder block, a balancing mass displaceably mounted in said housing, and means movable by said control piston to pivot said cradle and to shift said balancing mass, a partition wall separation the interior of said housing into two separate portions and defining an operating fluid chamber and a delivery fluid chamber between said wall and said block for isolating the delivery fluid on the same side of said wall as said block and in said block.

10. A pump comprising a cylinder block having a central axially extending bore for a control piston defined therein, said cylinder block having a plurality of angularly spaced axially extending pump cylinders defined around the central bore, a pump piston slidable in each of said pump cylinders, inlet and outlet valve and passage means defined in said cylinder block for the suction of a circulating fluid into each of said pump cylinders and for the discharge of said circulating fluid during operation of said pump pistons, wall means defining with said cylinder block a housing, a shaft rotatably mounted in said housing, a swash plate, a swash plate cradle carrying said swash plate and connected to said shaft for rotation therewith, said swash plate cradle being mounted on said shaft for pivotal movement for shifting said swash plate out of a plane normal to the axes of said pump cylinders for varying the strokes of said pistons, a control piston slidable in the central bore of said cylinder block, a balancing mass displaceably mounted in said housing, and means movable by said control piston to pivot said cradle and to shift said balancing mass, a spacer ring connected to said cylinder block at one end, a flanged disk closing the opposite end of said spacer ring, the interior of said spacer ring with said flanged disk on one side and said block on the other defining a housing, and a partition Wall on the interior of said housing spaced from, said block and separating the interior of said spacer ring into a compartment for operating fluid and a compartment for delivery fluid and having a bushing for each piston, and a References Cited by the Examiner UNITED STATES PATENTS 2,344,565 3/ 1944 Scott et al. 103173 2,737,895 3/1956 Ferris 103173 2,957,421 10/1960 Mock 103l73 FOREIGN PATENTS 22,306 g 1913 Great Britain.

MARK NE\VMAN, Primary Examiner.

piston rod connected to each piston andto said swash 15 Assistant Examiner

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US2344565 *Jun 30, 1941Mar 21, 1944Scott Jr Wallace JFuel injector for diesel engines and the like
US2737895 *Nov 19, 1952Mar 13, 1956Oilgear CoAxial type pump
US2957421 *Mar 17, 1954Oct 25, 1960Bendix CorpFuel supply pump for prime movers
GB191322306A * Title not available
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3450058 *Dec 5, 1966Jun 17, 1969Applied Power Ind IncSegmented oil film bearing for fluid translator
US3507584 *Mar 27, 1968Apr 21, 1970Us NavyAxial piston pump for nonlubricating fluids
US3682572 *Jul 27, 1970Aug 8, 1972Yarger Donald LPiston type pump
US3739692 *Sep 6, 1968Jun 19, 1973Reyrolle Hydraulics LtdSwashplate and like hydraulic machines
US3821922 *Sep 18, 1972Jul 2, 1974Abex CorpQuick change connection apparatus
US3874523 *Dec 13, 1972Apr 1, 1975Cmi CorpAsphalt mix preparation and storage plant
US3879042 *Aug 29, 1973Apr 22, 1975Warszawskie Zaklady MechniczneInjection pump
US4030404 *Aug 4, 1975Jun 21, 1977U.S. Philips CorporationSwash-plate drive mechanism
US4235116 *May 10, 1978Nov 25, 1980U.S. Philips CorporationBalanced variable wobble plate drive
US4258590 *Aug 3, 1979Mar 31, 1981U.S. Philips CorporationWobble plate control for a variable piston displacement machine
US4342544 *Mar 28, 1980Aug 3, 1982Creusot-LoireReciprocating pump
US4443160 *Nov 4, 1981Apr 17, 1984Brueninghaus Hydraulik GmbhHigh-pressure piston pump for liquids, preferably for water
US4444093 *Oct 22, 1981Apr 24, 1984Honda Giken Kogyo Kabushiki KaishaSlant plate type hydraulic device
US4492527 *Feb 17, 1983Jan 8, 1985Diesel Kiki Co., Ltd. (Japanese Corp.)Wobble plate piston pump
US4533301 *Sep 17, 1984Aug 6, 1985Foster Leslie WPump
US4583921 *Dec 28, 1984Apr 22, 1986Speck-Kolbenpumpen-Fabrik Otto Speck KgPlunger pump
US4636146 *Jun 4, 1985Jan 13, 1987Kraenzle JosefAxial plunger pump
US4800801 *May 6, 1986Jan 31, 1989Multinorm B.V.Pump
US4815358 *Jan 27, 1988Mar 28, 1989General Motors CorporationBalanced variable stroke axial piston machine
US4836090 *Jun 13, 1988Jun 6, 1989General Motors CorporationBalanced variable stroke axial piston machine
US5063829 *Aug 7, 1990Nov 12, 1991Hitachi, Ltd.Variable displacement swash plate type compressor
US5127314 *Nov 30, 1990Jul 7, 1992General Motors CorporationCompensating cam socket plate torque restraint assembly for a variable displacement compressor
US6206650 *Apr 27, 1999Mar 27, 2001Tcg Unitech AktiengesellschaftVariable axial piston displacement machine with maximized swivel angle
US6829978Aug 15, 2002Dec 14, 2004R. Sanderson Management, Inc.Piston engine balancing
US6854377 *Nov 2, 2001Feb 15, 2005R. Sanderson Management, Inc.Variable stroke balancing
US6913447Jan 22, 2002Jul 5, 2005R. Sanderson Management, Inc.Metering pump with varying piston cylinders, and with independently adjustable piston strokes
US6915765Oct 25, 2000Jul 12, 2005R. Sanderson Management, Inc.Piston engine assembly
US6925973Feb 11, 2000Aug 9, 2005R. Sanderson Managment, Inc.Piston engine assembly
US6983680Feb 27, 2004Jan 10, 2006Torvec, Inc.Long-piston hydraulic machines
US7007589Mar 24, 2000Mar 7, 2006R. Sanderson Management, Inc.Piston assembly
US7011469Feb 7, 2001Mar 14, 2006R. Sanderson Management, Inc.Piston joint
US7040263Aug 16, 2004May 9, 2006R. Sanderson Management, Inc.Piston engine assembly
US7140343May 27, 2003Nov 28, 2006R. Sanderson Management, Inc.Overload protection mechanism
US7162948Oct 6, 2004Jan 16, 2007R. Sanderson Management, Inc.Variable stroke assembly balancing
US7185578Aug 6, 2004Mar 6, 2007R. Sanderson ManagementPiston assembly
US7325476May 26, 2005Feb 5, 2008R. Sanderson Management, Inc.Variable stroke and clearance mechanism
US7331271Mar 31, 2003Feb 19, 2008R. Sanderson Management, Inc.Variable stroke/clearance mechanism
US7334548Feb 28, 2006Feb 26, 2008R. Sanderson Management, Inc.Piston joint
US7416045Jun 15, 2005Aug 26, 2008Torvec, Inc.Dual hydraulic machine transmission
US7438029Sep 21, 2004Oct 21, 2008R. Sanderson Management, Inc.Piston waveform shaping
US7475617Jun 15, 2005Jan 13, 2009Torvec, Inc.Orbital transmission with geared overdrive
US7635255Aug 9, 2005Dec 22, 2009Torvec, Inc.Long piston hydraulic machines
CN1934354BOct 12, 2004Jun 8, 2011托维克公司Long-piston hydraulic machines
EP0005566A1 *May 3, 1979Nov 28, 1979Philips Electronics N.V.Balanced variable displacement drive
WO2003040559A1 *Nov 4, 2002May 15, 2003Sanderson Albert EVariable stroke balancing
WO2005093250A1 *Oct 12, 2004Oct 6, 2005Keith E GleasmanLong-piston hydraulic machines
Classifications
U.S. Classification417/269, 91/506, 92/12.2
International ClassificationF04B1/29, F04B53/16, F04B53/00, F04B1/12, F04B1/14
Cooperative ClassificationF04B53/164, F04B1/295, F04B1/14
European ClassificationF04B1/14, F04B1/29A, F04B53/16C2