US3800673A - Wear equalizing arrangement for the valve plate of an axial piston machine - Google Patents

Wear equalizing arrangement for the valve plate of an axial piston machine Download PDF

Info

Publication number
US3800673A
US3800673A US00288001A US3800673DA US3800673A US 3800673 A US3800673 A US 3800673A US 00288001 A US00288001 A US 00288001A US 3800673D A US3800673D A US 3800673DA US 3800673 A US3800673 A US 3800673A
Authority
US
United States
Prior art keywords
grooves
face
slots
arrangement
wear
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
Application number
US00288001A
Other languages
English (en)
Inventor
G Lutz
K Veil
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Application granted granted Critical
Publication of US3800673A publication Critical patent/US3800673A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0055—Valve means, e.g. valve plate
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2042—Valves

Definitions

  • Fluid flowing through the slots and leaking between the control faces contains impurities so that annular sealing face portions of the stationary control face adjacent the slots, tend to be more worn than the annular supporting face portions located radially inward and radially outward of the sealing face portions.
  • Radial grooves, or grooves slanted in the direction of rotation connect the slots directly with the outer and- /or inner supporting face portions so that'the impurities produce wear of the supporting face portions, substantially equal to the wear of the sealing face portions, whereby a constant clearance is maintained between the eontrol faces.
  • the present invention relates to an axial piston machine which has a rotary cylinder block containing reciprocating pistons, and having a rotary control face cooperating with a stationary control face of a valve plate which has a pair of part-circular control slots connected with the inlet and outlet of the machine, and being swept by the cylinder ports.
  • the region of the worn sealing face portions is greater than at the outer and inner annular supporting face portions which are located in the region of the smallest and greatest diameter along which the rotary control face of the cylinder block still abuts the stationary control face of the valve plate.
  • the uneven width of the clearance causes an increase of the leakage, which may result in failure of the pump.
  • German DAS 1,142,481 discloses an axial piston machine in which the control face of the valve plate is provided with recesses concentric to the control slots and located outward of the same. Throttle grooves connect the recesses with the control slots so that the pressure fluid in the recesses produces high pressure areas. Furthermore, the impurities carried along by the pressure fluid cause wear in the region of the recesses, similar to the wear of thesealingface portions adjacent the control slots. A uniform wear of the entire stationary control face of the valve plate cannot be obtained by the prior art, since the outer and inner supporting face portions are subjected to lesser wear.
  • Another object of the invention is to control the wear of the control face of the valve plate in such a manner that the width of the clearance between the stationary and rotary control faces remains constant.
  • Another objectof the invention is to conduct fresh pressure fluid containing impurities from the high pressure control slot directly to a supporting face portion of the stationary control face so that the same is worn off.
  • the present invention provides passages, preferaby grooves, in the stationary control face of the valve plate in accordance with the invention.
  • the grooves are connected at one end with the control slots, and at the other end with the annular supporting face portions located in the region of the greatest and/or smallest diameter of the stationary valve control face which is in contact with the rotary control face of the cylinder block.
  • FIG. 1 is an axial sectional view illustrating an axial piston machine in which the invention is embodied
  • FIG. 2a is a fragmentary cross-section view taken on line IIaIIa in FIG. 1;
  • FIG. 2b is a fragmentary sectional view taken on line IIb-Ilb in FIG. 2a;
  • FIG. 3 is a fragmentary view illustrating a portion of a valve plate in accordance with a modified embodiment of the invention.
  • FIG. 4 is a fragmentary view illustrating a portion of a valve plate in accordance with another modification.
  • FIG. 1 An axial piston machine as shown in FIG. 1 has a housing 1 closed by a cover 2.
  • Cylinder block 4 has cylinder bores 5 opening in cylinder ports 5a, and containing pistons 7 whose slide shoes 7a slide on a stationary swash plate 6.
  • the other end of cylinder block 4 has a rotary control face 4a in which the cylinder ports 5a open.
  • a spring 8 urges the cylinder block, and more particularly the rotary control face 4a, into sliding engagement with the stationary control face 9 of a valve plate 10 which is secured to housing 2.
  • Valve plate 10 has part-circular slots 11 and 12, best seen in FIG. 2a, and respectively communicating with inlet and outlet openings 13, 14 in housing 2 so that fluid is supplied through the part-circular slots 11 and 12 to the cylinder ports 5a.
  • FIG. 2a shows the stationary control face 9 of the stationary valve plate 10
  • the two part-circular slots 11 and 12 have ends spaced from each other and located on opposite sides of a plane of symmetry.
  • the respective cylinder is disconnected from the inlet and connected with the outlet in a dead center position.
  • annular sealing face portions 15 and 16 are formed, on which corresponding face portions of the rotary control face 4a of cylinder block 4 slide.
  • Recesses 17, 18, 19 and 20 are formed in the control face 9 and have a part-circular configuration so that the four recesses 17 to 20 are located along a circle concentric with the axis of rotation of the machine and the center of the control face 9.
  • Ducts 21, 22, 23, 24 connect the recesses 17 to 20 with the interior of housing 1, 2.
  • annular supporting face portion 25 is located which cooperates with the corresponding annular supporting face portion on the control face 4a of the cylinder block 4.
  • Annular control face portion 25 is bounded on the outside by the circular edge of the control plate 10.
  • the rotary control face 4a has the same diameter.
  • the annular sealing face portion 16 is located in the same plane as the annular supporting face portion 25.
  • recesses 26, 27, 28, 29 are provided which are connected by passages 30, 31, 32, 33 with the interior of housing 2.
  • Recesses 26 to 29 are located inward of the annular sealing face portion 15, and outward of an inner annular supporting face portion 34.
  • control slots 11 and 12 communicate with passages or grooves 35, 36, 37, 38 which project outward in radial direction and have outer ends opening on the annular supporting face portion 25.
  • passages or grooves 39, 40, 41, 42 project inward from the control slots 11 and 12 in radial direction toward the smallest diameter over which the control face 4a of the cylinder block passes, so that the passages or grooves 39 to 42 open on the inner annular face portion 34.
  • the grooves 35 to 38, and the grooves 39 to 42 have the greatest cross section at the ends communicating with the control slots 1 1 and 12, and the smallest cross section in the region of the inner and outer annular supporting face portions 34 and 25.
  • the grooves Preferably, the grooves have a constant width, as shown in the FIG. 2a, and a depth gradually reduced toward the supporting face portions 25 and 34, as best seen in FIG. 2b.
  • the grooves 35 to 38 and 39 to 42 form pairs in radial direction, and each pair of grooves is spaced an angle of 45'from the plane of symmetry of the control slots 11 and 12 where the dead center of the piston movement is located.
  • cylinder block 4 is pressed by the fluid pressure so that its control face 4a moves away from the control face 9, increasing the clearance or gap between the control faces so that a leakage flow takes place through the clearance, as is required for lubricating and cooling the valve plate 10.
  • the impurities contained in the fluid enter into the clearance and cause substantial wear of the annular sealing face portions 15 and 16.
  • the inner supporting face portion 34 can be omitted, together with the recesses 26 to 29 and the grooves 39 to 42.
  • the substantially radial grooves 38, 42 are replaced with grooves 48 and 49 which are slanted toward the direction of rotation of the rotary cylinder block.
  • Groove 48 defines in the direction of rotation an acute angle with a tangent at the point where the end of groove 48 communicates with the control slot 46, and the groove 49 is slanted the same acute angle to the tangent at the point where the end of groove 49 communicates with the slot 46.
  • the slanted position of grooves 49 and 48 has the advantagethat during rotation in one direction of the cylinder block 4 a greater volume of pressure fluid with impurities is supplied to the outer and inner annular supporting face portions 47 and 47 so that the wear of these face portions is increased.
  • two slanted grooves 51 and 52 cross each other and project in opposite circumferential directions so that pressure fluid with impurities directly flows through one of the grooves from control slot 43, dependent on the direction of rotation so that the direction of rotation of cylinder block 3 can be reversed, and sufficient pressure fluid flows to the outer annular supporting face portion 54, irrespective of the direction of rotation.
  • Wear equalizing arrangement for a valve plate of an axial piston machine comprising a housing having an inlet and an outlet; cylinder block means mounted in said housing for rotation about an axis and having a rotary control face; and valve plate means secured in said housing and having two part-circular slots communicating with said inlet and outlet, respectively, said valve plate having a stationary control face in sliding contact with said rotary control face so that impurities in a fluid leaking from said slot causes greater wear on said annular sealing face portions of said stationary control face located on opposite sides of, and adjacent said slots than on at least one annular supporting face portion of said stationary control face separated in radial direction by one of said sealing face portions from said slots, said valve plate being provided in said stationary control face with grooves extending from said slots through at least one of said sealing face portions and ending distant from said slots at said supporting face portion, each of said gooves being substantially closed by said rotary control face so that fluid containing impurities flows through said grooves to said supporting face portion for increasing the wear thereof to be substantially equal to the wear of
  • each of said grooves is slanted to the tangent on the respective part-circular slot at the point where one end of the respective groove communicates with the respective slot so that the direction of said grooves have compo- 6 nents in the direction of rotation of said cylinder block whereby a great volume of fluid enters the other end of said grooves.
  • each slanted groove forms a pair with another groove in said stationary control face slanted in the opposite direction and connecting the respective slot with said supporting face portion whereby fluid flows mainly through one or the other groove depending on the direction of rotation of said cylinder block.
  • annular supporting face portion of said stationary control face is located adjacent and radially outward of the radially outer annular sealing face portion of said stationary control face.
  • said stationary control face includes another annular supporting face portion located within the radially inner sealing face portion; and wherein said valve plate means is formed with other grooves connecting said slots with said annular inner supporting face portion for increasing the wear thereof.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US00288001A 1971-09-09 1972-09-11 Wear equalizing arrangement for the valve plate of an axial piston machine Expired - Lifetime US3800673A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2145056A DE2145056A1 (de) 1971-09-09 1971-09-09 Kolbenmaschine

Publications (1)

Publication Number Publication Date
US3800673A true US3800673A (en) 1974-04-02

Family

ID=5819068

Family Applications (1)

Application Number Title Priority Date Filing Date
US00288001A Expired - Lifetime US3800673A (en) 1971-09-09 1972-09-11 Wear equalizing arrangement for the valve plate of an axial piston machine

Country Status (5)

Country Link
US (1) US3800673A (en])
JP (1) JPS4836703A (en])
CH (1) CH543668A (en])
DE (1) DE2145056A1 (en])
FR (1) FR2152158A5 (en])

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3929112A (en) * 1973-01-31 1975-12-30 Gkn Transmissions Ltd Fuel injection apparatus for internal combustion engines
US3980003A (en) * 1975-02-07 1976-09-14 Caterpillar Tractor Co. Variable hydrostatic bearing between barrel and head of axial piston units
US4945817A (en) * 1989-10-24 1990-08-07 General Motors Corporation Axial piston device
US5172623A (en) * 1990-07-10 1992-12-22 Messier-Bugatti Hydraulic rotary machine with pre-discharge opening for lubrication supply
GB2274491A (en) * 1993-01-21 1994-07-27 Hamworthy Hydraulics Ltd Axial piston pump
EP0832348A1 (en) * 1994-02-17 1998-04-01 Kesol Production Ab A valve system in a rotary radial-piston engine
WO2006040090A1 (de) * 2004-10-08 2006-04-20 Stabilus Gmbh Linearantrieb
US20250012262A1 (en) * 2023-07-07 2025-01-09 Robert Bosch Gmbh Integrated electro-hydraulic unit

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52144444A (en) * 1976-05-27 1977-12-01 Unitika Ltd Spun yarnnlike composite yarn and its manufacture
JPS52144445A (en) * 1976-05-27 1977-12-01 Unitika Ltd Linennlike composite yarn and its manufacture
JPS6345079U (en]) * 1986-09-11 1988-03-26
US5105723A (en) * 1990-04-06 1992-04-21 Zexel Corporation Swash plate type axial piston pump
JPH075255Y2 (ja) * 1990-06-26 1995-02-08 株式会社豊田自動織機製作所 アキシャルピストンポンプ
JP4611232B2 (ja) * 2006-03-30 2011-01-12 三菱重工業株式会社 流体機械およびそのバルブプレート

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20026A (en) * 1858-04-27 Improvement in revolving retorts for distilling coal
US1867308A (en) * 1931-04-04 1932-07-12 Waterbury Tool Co Hydraulic speed transmission
GB767213A (en) * 1954-04-15 1957-01-30 Thoma Hans Prof Dr Ing Improvements in or relating to axial piston gear
US2847938A (en) * 1955-12-01 1958-08-19 John T Gondek Hydraulic pump
US2972962A (en) * 1956-07-16 1961-02-28 Oilgear Co Hydraulic thrust bearing
US3040672A (en) * 1955-10-05 1962-06-26 Daimler Benz Ag Lubricating system for control surfaces of a hydrostatic transmission
US3232239A (en) * 1962-01-26 1966-02-01 Lely Nv C Van Der Hydraulic pumps and motors
US3487788A (en) * 1969-02-25 1970-01-06 Jean Thoma Hydraulic unit
US3669568A (en) * 1970-03-14 1972-06-13 Dowty Technical Dev Ltd Pump

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20026A (en) * 1858-04-27 Improvement in revolving retorts for distilling coal
US1867308A (en) * 1931-04-04 1932-07-12 Waterbury Tool Co Hydraulic speed transmission
GB767213A (en) * 1954-04-15 1957-01-30 Thoma Hans Prof Dr Ing Improvements in or relating to axial piston gear
US3040672A (en) * 1955-10-05 1962-06-26 Daimler Benz Ag Lubricating system for control surfaces of a hydrostatic transmission
US2847938A (en) * 1955-12-01 1958-08-19 John T Gondek Hydraulic pump
US2972962A (en) * 1956-07-16 1961-02-28 Oilgear Co Hydraulic thrust bearing
US3232239A (en) * 1962-01-26 1966-02-01 Lely Nv C Van Der Hydraulic pumps and motors
US3487788A (en) * 1969-02-25 1970-01-06 Jean Thoma Hydraulic unit
US3669568A (en) * 1970-03-14 1972-06-13 Dowty Technical Dev Ltd Pump

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3929112A (en) * 1973-01-31 1975-12-30 Gkn Transmissions Ltd Fuel injection apparatus for internal combustion engines
US3980003A (en) * 1975-02-07 1976-09-14 Caterpillar Tractor Co. Variable hydrostatic bearing between barrel and head of axial piston units
US4945817A (en) * 1989-10-24 1990-08-07 General Motors Corporation Axial piston device
US5172623A (en) * 1990-07-10 1992-12-22 Messier-Bugatti Hydraulic rotary machine with pre-discharge opening for lubrication supply
GB2274491A (en) * 1993-01-21 1994-07-27 Hamworthy Hydraulics Ltd Axial piston pump
GB2274491B (en) * 1993-01-21 1996-09-04 Hamworthy Hydraulics Ltd Axial piston pump
EP0832348A1 (en) * 1994-02-17 1998-04-01 Kesol Production Ab A valve system in a rotary radial-piston engine
WO2006040090A1 (de) * 2004-10-08 2006-04-20 Stabilus Gmbh Linearantrieb
US20080289327A1 (en) * 2004-10-08 2008-11-27 Rolf Mintgen Linear Drive
US20250012262A1 (en) * 2023-07-07 2025-01-09 Robert Bosch Gmbh Integrated electro-hydraulic unit

Also Published As

Publication number Publication date
DE2145056A1 (de) 1973-03-22
JPS4836703A (en]) 1973-05-30
FR2152158A5 (en]) 1973-04-20
CH543668A (de) 1973-10-31

Similar Documents

Publication Publication Date Title
US3800673A (en) Wear equalizing arrangement for the valve plate of an axial piston machine
US5316391A (en) Squeeze film damper seal
US3478955A (en) Variable area diffuser for compressor
US3249061A (en) Pump or motor device
US2612110A (en) Pump and motor
US3852003A (en) Pressure-sealed compressor
US3255706A (en) Rotary radial piston machines with tangential balancing recesses for the pressure balance of the pistons
US3256831A (en) Rotary pump and fluid motor and sealing means therefor
US3657970A (en) Hydraulic pump or motor having a rotary cylinder barrel
US3292553A (en) Piston return mechanism
US3221665A (en) Hydraulic pump or motor with hydraulic pressure-responsive vane
US4135862A (en) Swash plate type compressor
US3187681A (en) Hydraulic ball pumps and motors
US3180271A (en) Variable volume pump
US3851669A (en) Control face arrangement for an axial piston machine
US3707169A (en) Hydrostatically balanced plate valve with low flow resistance
US3418942A (en) Contamination-resistant fuel pump with eccentrically located drive shaft
US2862455A (en) Hydrodynamic machine
GB1237739A (en) Improvements in or relating to power transmission
US3802321A (en) Rotor balancing arrangement for axial piston machines
US3468263A (en) Power transmission
US3810418A (en) Center ring arrangement for a radial piston machine
US3847057A (en) Precharging arrangement for a hydraulic displacement machine
US3800672A (en) Clearance adjusting arrangement for an axial piston machine
US3782245A (en) Pressure balanced radial piston machine