US3904318A - Fluid energy translating device - Google Patents
Fluid energy translating device Download PDFInfo
- Publication number
- US3904318A US3904318A US494696A US49469674A US3904318A US 3904318 A US3904318 A US 3904318A US 494696 A US494696 A US 494696A US 49469674 A US49469674 A US 49469674A US 3904318 A US3904318 A US 3904318A
- Authority
- US
- United States
- Prior art keywords
- barrel
- shaft
- translating device
- fluid energy
- energy translating
- Prior art date
- 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
Links
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
- F04B23/106—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being an axial piston pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2007—Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid pressure
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
Definitions
- the instant invention relates generally to axial piston type pumps and motors (genericly referred to as fluid energy translating devices) and more specifically to an axial piston pump having a device for driving a servo pump and clamping the main pump barrel against its port plate.
- a common type of axial piston pump includes a hous' ing having a rotatably mounted barrel with a plurality of axial cylinder bores.
- a port plate is interposed between the barrel and the inlet and working ports of the device to alternately connect each cylinder with the inlet and working ports as the device is rotated.
- Within each bore is a piston which is connected by shoes to a thrust plate assembly which reciprocates the pistons to pump fluid as the barrel is rotated.
- a fixed displace ment or servo pump is driven when the main pump barrcl is rotated to provide servo pressure fluid to operate the main pump controls.
- a disadvantage of driving a servo pump in this manner is that the servo pump must be large enough to accommodate the relatively large shaft necessary to drive the main pump or one end of the shaft must be of reduced diameter.
- a further disadvantage of driving a servo pump from the main pump drive shaft is that the drive shaft tends to bend. This shaft bending may cause misalignment of the servo pump components and thereby shorten the life of the servo pump.
- a servo pump is driven by a device which includes a shaft which is driven by the main pump barrel.
- the shaft has a spring and an axial adjustment which clamp the main pump barrel against its port plate and limit the distance the barrel can lift off of the port plate.
- the spring and the axial adjustment also clamp the stationary servo pump member against its port plate which establishes the clearance for the running members of the pump.
- FIGURE is an axial sectional view of a fluid energy translating device according to the instant invention.
- an axial piston pump having a case 11 which includes a central housing 12, an end cap 13 affixed by bolts, not shown,
- Case 11 has a cavity 16 in which a rotatable cylinder barrel 17 is mounted on rollers 18 of a bearing 19 which has its outer race 20 pressed against a housing shoulder 21.
- a drive shaft 22 passes through a bore 23 in end cap 13 and is rotatably supported in a bearing 24.
- the inner end 25 of drive shaft 22 is drivingly connected to a central bore 26 in barrel 17.
- Barrel 17 has a plurality of parallel axial bores 27 equally spaced circumferentially about the rotational axis of the barrel 17.
- a sleeve 28 in each bore 27 receives a piston 29.
- Each piston 29 has a ball-shaped head 30 which is received in a socket 31 of a shoe 32.
- Each shoe 32 is retained against a flat creep or thrust plate 33 mounted on a movable rocker cam 34 by a shoe retainer assembly 35.
- Assembly 35 includes a shoe retainer plate 36, with a number of equally spaced bores equal to the number of pistons 29, which passes over the body of each piston and engages a shoulder 37 on each shoe 32.
- the shoe retainer plate 36 has a central bore 38 which passes over a post 39 affixed to rocker cam 34 by a Snap ring 40.
- a spacer 41 is interposed between the shoe retainer plate 36 and a snap ring 42 which secures the shoe retainer plate 36 on the post 39 and prevents the shoes 32 from lifting off of thrust plate 33.
- Each cylinder bore 27 ends in a cylinder port 43 which conducts fluid between a port plate 44 and the bore 27.
- Port plate 44 is positioned between barrel 17 and port cap 14.
- a pair of kidney-shaped apertures, not shown, are formed in the plate 44. These apertures communicate with ports, P P in the port cap 14.
- One of the ports contains low pressure fluid and is the intake port while the other port contains high pressure or working fluid and is the exhaust port, depending upon the operating conditions of the pump.
- a second shaft 46 is drivingly connected to the central bore 26 of barrel 17 by a splined end 47.
- Shaft 46 rotates when barrel 17 is driven and drives a fixed displacement pump which is connected to shaft 46 through a key 45.
- Shaft 46 is rotatably supported in a first needle bearing 50 mounted in a bore 51 in port cap 14 and in a second needle bearing 52 mounted in a bore 53 in a spring and pressure loaded clamp member 54.
- Shaft 46 is retained in driving engagement with barrel I7.
- Barrel ]7 is prevented from moving axially by a snap ring 55, an axially split collar 56 and a spring 57.
- Spring 57 acting through collar 56 and snap ring 55, biases barrel 17 against port plate 44 which is clamped against port cap 14.
- the maximum distance barrel 17 can move away from port plate 44 during operation of the pump is the distance between an end face 58 on collar 56 and a shoulder 59 on splined end 47. This distance can be varied by a nut 60 on the threaded other end 61 of shaft 46.
- a spacer 62 is inserted between nut 60 and a thrust bearing 63 which engages clamp member 54.
- Clamp member 54 engages an outer housing 64 of the fixed displacement pump which is a rotor type having a gear 67 rotating within a gear 68, commonly referred to as a gerotor pump. This pump provides servo pressure fluid to operate pump controls, not shown, which control the inclination of the rocker cam.
- Clamp member 54 secures housing 64 against a port plate 65 which is clamped against port cap 14.
- a pair of kidney-shaped apertures, not shown, are formed in plate 65. These apertures communicate with ports P,,, S, in the port cap 14.
- One of the ports S contains low pressure servo fluid and is the intake port while the other port P, contains high pressure servo fluid and is the discharge port.
- Housing 64 is prevented from rotating by a pin 66. Clamping outer housing 64 between member 54 and port plate 65 establishes the proper operating clearance for the rotating members 67, 68.
- high pressure servo fluid is conducted through a passage 73 into a chamber 69 sandwiched between a retainer 74 and clamp member 54.
- Retainer 74 is prevented from moving axially away from member 54 by an end cover 70 secured by a snap ring 71 in port cap 14.
- the servo pressure fluid acts on the member 54 and assists in clamping outer housing 64 against port plate 65. As the pressure of the servo discharge fluid increases, it exerts a greater force on member 54.
- spring 57 which biases barrel 17 against port plate 44 also provides the force on member 54 to clamp outer housing 64 against port plate 65.
- servo pressure fluid assists in urging housing 64 against port plate 65.
- a fluid energy translating device having a housing, a barrel rotatably supported in the housing, a plurality of cylinders in the barrel, a piston mounted for reciprocation in each cylinder, a main drive shaft drivingly connected to the barrel, a surface containing inlet and outlet porting to receive and exhaust fluid to and from said barrel in the housing at one end of the barrel, means for reciprocating the pistons within the cylinders when the barrel is rotated, the improvement comprising: a fixed displacement servo pump, a second shaft to drive said servo pump when said barrel is rotated, a second surface containing inlet and outlet ports in the housing for receiving and exhausting fluid to and from said servo pump, and spring means acting between said second shaft and said barrel for simultaneously biasing said barrel against the first surface and the servo pump against said second surface.
- the fluid energy translating device recited in claim 4 including drive means on said second shaft for connecting said second shaft to said barrel, said biasing means being located between said drive means and said barrel.
- An axial piston type fluid energy translating device comprising a housing, a main barrel rotatably supported in the housing and carrying a plurality of pistons, a main drive shaft drivingly connected to the barrel and providing power to rotate the barrel, a main 4port plate mounted in the housing immediately adja cent one end of the barrel, a servo pump having a servo pump member, a second shaft drivingly connected to said barrel and to said servo pump to drive said servo pump when said barrel is rotated by said main drive shaft, a servo port plate immediately adjacent one end of said servo pump member, a spring biasing said main barrel against said main port plate, and said spring also acting against said second shaft and biasing said servo pump member against said servo port plate by a force transmitted axially through said second shaft.
- An axial piston type fluid energy translating device as defined in claim 13 wherein said spring acts between said main barrel and said second shaft to bias said main barrel in one direction and to bias said second shaft and servo pump member in a direction opposite said first direction.
- An axial piston type fluid energy translating device as set forth in claim 13, including an axially facing surface operatively connected to said second shaft, and another axially facing surface operatively connected to barrel against the bias of said spring.
- An axial piston type fluid energy translating device as set forth in claim 15, including adjustment means on said second shaft for regulating the amount said main barrel and engageable with said first men- 5 of axial movement allowed.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Reciprocating Pumps (AREA)
- Hydraulic Motors (AREA)
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US494696A US3904318A (en) | 1974-08-02 | 1974-08-02 | Fluid energy translating device |
CA229,858A CA1020809A (en) | 1974-08-02 | 1975-06-20 | Fluid energy translating device |
GB26778/75A GB1510998A (en) | 1974-08-02 | 1975-06-24 | Pump assembly |
IT50460/75A IT1040917B (it) | 1974-08-02 | 1975-07-10 | Perfezionamento nelle pompe a stantuffi assiali |
FR7522598A FR2280805A1 (fr) | 1974-08-02 | 1975-07-18 | Dispositif de translation d'energie fluide |
JP50089997A JPS5138102A (it) | 1974-08-02 | 1975-07-23 | |
DE19752534539 DE2534539B2 (de) | 1974-08-02 | 1975-08-01 | Axialkolbenmaschine |
JP1980191707U JPS56149078U (it) | 1974-08-02 | 1980-12-30 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US494696A US3904318A (en) | 1974-08-02 | 1974-08-02 | Fluid energy translating device |
Publications (1)
Publication Number | Publication Date |
---|---|
US3904318A true US3904318A (en) | 1975-09-09 |
Family
ID=23965580
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US494696A Expired - Lifetime US3904318A (en) | 1974-08-02 | 1974-08-02 | Fluid energy translating device |
Country Status (7)
Country | Link |
---|---|
US (1) | US3904318A (it) |
JP (2) | JPS5138102A (it) |
CA (1) | CA1020809A (it) |
DE (1) | DE2534539B2 (it) |
FR (1) | FR2280805A1 (it) |
GB (1) | GB1510998A (it) |
IT (1) | IT1040917B (it) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4336003A (en) * | 1980-08-11 | 1982-06-22 | Abex Corporation | Crane swing control |
US4550645A (en) * | 1984-04-27 | 1985-11-05 | Sundstrand Corporation | Thin valve plate for a hydraulic unit |
EP0543601A2 (en) * | 1991-11-18 | 1993-05-26 | Hobourn Automotive Limited | Rotary assemblies |
US5326232A (en) * | 1993-04-20 | 1994-07-05 | General Motors Corporation | Two stage pump assembly with mechanical disconnect |
US5354180A (en) * | 1992-07-31 | 1994-10-11 | Linde Aktiengesellschaft | Hydrostatic assembly having multiple pumps |
US5498140A (en) * | 1994-03-16 | 1996-03-12 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US6289878B1 (en) | 1999-07-15 | 2001-09-18 | Caterpillar Inc. | Engine having multiple pumps driven by a single shaft |
US6682315B2 (en) * | 2001-11-28 | 2004-01-27 | Caterpillar Inc | Axial piston pump barrel with a cast high pressure collection cavity |
US20090013861A1 (en) * | 2006-03-10 | 2009-01-15 | Brueninghaus Hydromatik Gmbh | Combined pump housing for several rated quantities |
US11236736B2 (en) * | 2019-09-27 | 2022-02-01 | Honeywell International Inc. | Axial piston pump with port plate having balance feed aperture relief feature |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4111103A (en) * | 1977-02-14 | 1978-09-05 | Commercial Shearing, Inc. | Thrust rings for swash plate pumps and motors |
DD245011B1 (de) * | 1985-12-23 | 1989-07-19 | Karl Marx Stadt Ind Werke | Hydrostatische axialkolbenmaschine |
DE102007032103B4 (de) * | 2007-05-16 | 2022-02-24 | Robert Bosch Gmbh | Pumpeneinheit mit einer Hauptpumpe und einer in ihrem Fördervolumen verstellbaren Ladepumpe |
DE102015101655B3 (de) * | 2015-02-05 | 2016-01-21 | I.S.T. Industrie Service Technologie Beratungs- Und Beteiligungsgesellschaft Mbh | Molchbare Kolbenpumpe |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1486836A (en) * | 1923-04-28 | 1924-03-11 | Hill Compressor & Pump Company | Rotary-pump pressure control |
US2484337A (en) * | 1943-05-01 | 1949-10-11 | Oilgear Co | Hydrodynamic machine |
US2495685A (en) * | 1945-06-08 | 1950-01-31 | Beaman Bernard | Two-stage hydraulic pressure pump |
US2604047A (en) * | 1945-09-19 | 1952-07-22 | Hulman | Two-stage hydraulic pressure pump |
US2945449A (en) * | 1954-06-03 | 1960-07-19 | Bendix Aviat Corp | Hydraulic control pump |
US3160109A (en) * | 1961-05-18 | 1964-12-08 | William L Kline | Hydraulic unit |
US3188972A (en) * | 1963-03-04 | 1965-06-15 | Thoma Jean Ulrich | Axial piston hydraulic unit |
-
1974
- 1974-08-02 US US494696A patent/US3904318A/en not_active Expired - Lifetime
-
1975
- 1975-06-20 CA CA229,858A patent/CA1020809A/en not_active Expired
- 1975-06-24 GB GB26778/75A patent/GB1510998A/en not_active Expired
- 1975-07-10 IT IT50460/75A patent/IT1040917B/it active
- 1975-07-18 FR FR7522598A patent/FR2280805A1/fr active Granted
- 1975-07-23 JP JP50089997A patent/JPS5138102A/ja active Pending
- 1975-08-01 DE DE19752534539 patent/DE2534539B2/de active Granted
-
1980
- 1980-12-30 JP JP1980191707U patent/JPS56149078U/ja active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1486836A (en) * | 1923-04-28 | 1924-03-11 | Hill Compressor & Pump Company | Rotary-pump pressure control |
US2484337A (en) * | 1943-05-01 | 1949-10-11 | Oilgear Co | Hydrodynamic machine |
US2495685A (en) * | 1945-06-08 | 1950-01-31 | Beaman Bernard | Two-stage hydraulic pressure pump |
US2604047A (en) * | 1945-09-19 | 1952-07-22 | Hulman | Two-stage hydraulic pressure pump |
US2945449A (en) * | 1954-06-03 | 1960-07-19 | Bendix Aviat Corp | Hydraulic control pump |
US3160109A (en) * | 1961-05-18 | 1964-12-08 | William L Kline | Hydraulic unit |
US3188972A (en) * | 1963-03-04 | 1965-06-15 | Thoma Jean Ulrich | Axial piston hydraulic unit |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4336003A (en) * | 1980-08-11 | 1982-06-22 | Abex Corporation | Crane swing control |
US4550645A (en) * | 1984-04-27 | 1985-11-05 | Sundstrand Corporation | Thin valve plate for a hydraulic unit |
WO1985005147A1 (en) * | 1984-04-27 | 1985-11-21 | Sundstrand Corporation | Thin valve plate for a hydraulic unit |
GB2178489A (en) * | 1984-04-27 | 1987-02-11 | Sundstrand Corp | Thin valve plate for a hydraulic unit |
EP0543601A2 (en) * | 1991-11-18 | 1993-05-26 | Hobourn Automotive Limited | Rotary assemblies |
EP0543601A3 (en) * | 1991-11-18 | 1993-08-04 | Hobourn Automotive Limited | Rotary assemblies |
US5282446A (en) * | 1991-11-18 | 1994-02-01 | Hobourn Automotive Ltd. | Rotary pump assemblies |
US5354180A (en) * | 1992-07-31 | 1994-10-11 | Linde Aktiengesellschaft | Hydrostatic assembly having multiple pumps |
US5326232A (en) * | 1993-04-20 | 1994-07-05 | General Motors Corporation | Two stage pump assembly with mechanical disconnect |
US5498140A (en) * | 1994-03-16 | 1996-03-12 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US6289878B1 (en) | 1999-07-15 | 2001-09-18 | Caterpillar Inc. | Engine having multiple pumps driven by a single shaft |
US6682315B2 (en) * | 2001-11-28 | 2004-01-27 | Caterpillar Inc | Axial piston pump barrel with a cast high pressure collection cavity |
US20040064943A1 (en) * | 2001-11-28 | 2004-04-08 | Gens Thomas D. | Axial piston pump barrel with a cast high pressure collection cavity |
US7093341B2 (en) | 2001-11-28 | 2006-08-22 | Caterpillar Inc. | Method of making an axial piston pump barrel with a cast high pressure collection cavity |
US20090013861A1 (en) * | 2006-03-10 | 2009-01-15 | Brueninghaus Hydromatik Gmbh | Combined pump housing for several rated quantities |
US8608454B2 (en) * | 2006-03-10 | 2013-12-17 | Brueninghaus Hydromatik Gmbh | Combined pump housing for several rated quantities |
US11236736B2 (en) * | 2019-09-27 | 2022-02-01 | Honeywell International Inc. | Axial piston pump with port plate having balance feed aperture relief feature |
Also Published As
Publication number | Publication date |
---|---|
GB1510998A (en) | 1978-05-17 |
JPS56149078U (it) | 1981-11-09 |
CA1020809A (en) | 1977-11-15 |
DE2534539C3 (it) | 1978-10-19 |
FR2280805A1 (fr) | 1976-02-27 |
DE2534539A1 (de) | 1976-02-12 |
DE2534539B2 (de) | 1978-02-16 |
JPS5138102A (it) | 1976-03-30 |
FR2280805B1 (it) | 1980-04-18 |
IT1040917B (it) | 1979-12-20 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: HAGGLUNDS DENISON CORPORATION, 1220 DUBLIN ROAD, C Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:ABEX CORPORATION, A CORP. OF DE;REEL/FRAME:004737/0427 Effective date: 19870630 Owner name: HAGGLUNDS DENISON CORPORATION, OHIO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:ABEX CORPORATION;REEL/FRAME:004737/0427 Effective date: 19870630 |