US3461809A - Radial-piston pump with improved cooling and lubrication - Google Patents

Radial-piston pump with improved cooling and lubrication Download PDF

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Publication number
US3461809A
US3461809A US712817A US3461809DA US3461809A US 3461809 A US3461809 A US 3461809A US 712817 A US712817 A US 712817A US 3461809D A US3461809D A US 3461809DA US 3461809 A US3461809 A US 3461809A
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US
United States
Prior art keywords
sleeve
shaft
radial
fluid
suction chamber
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
US712817A
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English (en)
Inventor
Ludwig Budecker
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.)
Continental Teves AG and Co oHG
Original Assignee
Alfred Teves 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 Alfred Teves GmbH filed Critical Alfred Teves GmbH
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Publication of US3461809A publication Critical patent/US3461809A/en
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    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves

Definitions

  • the invention relates to a radial-piston pump supplying hydraulic pressure by means of an eccentric shaft which-rotates in a cylinder housing in which the pumping pistons are radially disposed.
  • Hydraulic pumps of this type preferably employed when high pressures are involved, demand very fine machining of the component parts, extremely close tolerances and the maintenance of constant lubrication between the moving parts.
  • the latter task in particular requires continuous removal of the heat associated with high pressures and the correlated friction between moving parts.
  • the efficiency of other pump com ponents is liable to be aflected by a thermal distortion of the lubricating means or by their decomposition into substances which are ineffectual as lubricants or incompatible with the metallic and non-metallic parts with which they are in contact.
  • the circuitous flow pattern leads fresh cool hydraulic fluid in and out of the rotor shaft which carries the slidable sleeve designed to displace the piston and past and through the jacket or sleeve surrounding the eccentric.
  • the eccentric shaft is rotatably received in a blind bore of the pump or cylinder housing which communicates, at its closed end, with the intake port of the pump and delivers hydraulic fluid to an annular suction chamber within the housing communicating with the pumping cylinders. At least part of the fluid delivered from the intake portion to the suction chamber is passed through an axial bore formed in the eccentric shaft at its end proximal to the closed end of the axial bore of the housing. Spaced from this end of the shaft, there is provided and eccentric portion around which a bearing sleeve or jacket is disposed with peripheral clearance, the axial bore of the shaft opening within the sleeve via one or more radial ports formed in the eccentric portion of the shaft.
  • the sleeve is, according to another feature of this in- 3,461,809 Patented Aug. 19, 1969 "ice vention, formed with openings communicating between its interior (with which the radial ports communicate) and the annular space in the axial bore of the housing surrounding the sleeve and into which the pistons project tocontact the sleeve.
  • This annular space is, in turn, connected with the suction chamber of the housing by one or more channels.
  • Still another feature of this invention provides, between the suction pump and the annular space surrounding the sleeve or in the sleeve itself, one or more constrictions adapted to apply a pressure drop between the suction chamber and the fluid passage through the sleeve and axial bore of the shaft to ensure fluid flow through this passage for-lubrication of the co-operating surfaces of the eccentric portion and the sleeve as well as the cooperating portions of the sleeve and the pistons.
  • the system may be embodied in various ways, namely, by providing the intake portion or side of the pump in fluid communication with the closed end of the axial bore so that the lubricant and cooling fluid also passes axially through the bore from the closed end into the suction compartment.
  • the annular space surrounding the ring or sleeve may communicate with the suction chamber via the axial bore at the closed end of the latter while the intake port or side of the pump communicates with the space surrounding the ring.
  • the coolant and lubricant flows initially through and around the bearing ring or sleeve, thence through the radial bores or bore of the eccentric portion of the shaft and the axial bore of the latter into the suction compartment.
  • the system may be provided with a throttle or constriction between the intake side or port and the suction component so that a path of lower pressure loss is provided along the passageway around the bearing ring or sleeve and through the shaft, then is formed between the intake port and the suction compartment; alternatively, a throttle or constriction may be formed in the channel communicating between the space surrounding the bearing ring or sleeve while the suction compartment is connected with the intake port via another channel to partition fluid flow between the lubricating and cooling passageway and direct flow to the suction compartment.
  • the system described generally above has the advantage that at least part of the hydraulic fluid displaced by the pump traverses the eccentric shaft and the bearing surfaces of the sleeve therearound before passage into the suction compartment and thus provides a constant stream of cool fresh lubricant and coolant.
  • FIG. 1 is an axial cross-sectional view, in part, showing another embodiment of my invention
  • FIG. 1A is an end view, with the cover plate removed, of the embodiment of FIG. 1;
  • FIG. 2 is an axial cross-sectional View, in part, of another embodiment.
  • Cooling accompanied by high pumping efiiciency is provided, according to the embodiment of FIGS. 1 and 1A through constrictions interposed in the fluid flow which are designed to create a pressure difference.
  • FIGS. 1 and 1A there is shown a radial-piston pump whose housing 101 has a cylinder block 101b and a pair of cover plates 101a and 101s bolted to the cylinder block and defining the fluid conduits as will be apparent hereinafter.
  • a fluid-intake port 114 is provided in the cylinder block 101b and communicates with a radially extending chamber 115 defined in the axial bore 128 of the cylinder housing 101b between the front face 111 of the shaft 102 and the cover 1010, this compartment lying in a plane perpendicular to the axis of rotation of the shaft 102.
  • the second conduit connecting the port 114 with the annular suction chamber 121 is completed by an axially extending channel 115' surrounding a boss 10112 at the end of the shaft and a further annular chamber 115" defined between the cover 1010 and the cylinder body 101b.
  • the first conduit is here constituted by the axial bore 110 in the shaft 102 and a plurality of axially spaced radial orifices 113, 113a opening into the annular clearance 122 within the bearing sleeve 103.
  • the latter is formed with notches 124 along its opposite annular ends and with radial apertures 124', all equispaced about the bearing sleeve, to connect the annular clearance 122 with the annular space 125 surrounding the sleeve.
  • a passage 126 connects the space 125 with the suction chamber 121 via an annular chamber 126' which also serves to collect leakage fluid behind the bearing seal 127.
  • the pistons 104 are here applied by fluid pressure against the bearing sleeve 103 and are axially shiftable in the cylinder 119.
  • a plate-type check valve 120 is employed and the plugs 120 close the heads of the cylinders 119.
  • Bores 107 collect the fluid under pressure from cylinders 119 and deliver this fluid to the high-pressure discharge port 103 via an annular discharge chamber 107.
  • the clearance 122 may constitute a constriction forcing the fluid flow from the intake port 114 to the suction chamber 121 to be split between the first conduit 114, 115, 110, 113, 122, 124, 124, 125, 126, 126 and the second conduit 114-, 115, 115', 115", 121, thereby providing high pumping efficiency and appropriate lubrication and cooling.
  • the constriction can additionally or alternatively be formed by apertures 124 and 124'.
  • the cylinder body 201 is flanked by a pair of cover plates 201a and 201a but has an intake port 214 connected by a passage 214a directly to the annular space 225 surrounding the bearing sleeve 203.
  • the bearing sleeve 203 surrounds the eccentric portion 215 of the shaft 202 and is provided with apertures 224 and 224' as previously described.
  • the sleeve 203 is mounted upon the eccentric portion 215 with an annular clearance 222 from which the cooling and lubricating fluid is delivered to the axial bore 210 of the shaft by radial orifices 213 and 213a.
  • the sleeve 203 also displaces the pistons 204 in the bores 219 while the suction chamber is formed at 221 and each piston co-operates with the check valve 220, a channel 207 and a chamber 207 for the high-pressure fluid as previously described.
  • the constriction is here provided at 226 in a passage 226 conmeeting space 225 with the annular chamber 226' and the suction chamber 221.
  • the constriction or throttle 226" thus creates a split flow between the first conduit 214, 214a, 225, 224, 224', 213, 213a, 210, 215, 215', 221 and a second conduit 214, 214a, 225, 226, 226", 226', 221.
  • Chambers 126' and 226 also connect a leakage path around the shafts 102, 202 just behind the bearing seals 127, 227 with the suction chamber, the leakage path extending from the spaces 125, 225.
  • the pistons 104 and 204 which are shown in their most outwardly extreme positions, represent a plurality of similar pistons disposed along common radial planes P and P of the pumps and angularly equispaced about the axis A and A thereof.
  • the pistons may be springbiased against the bearing sleeve 103, 203 as, for example, described in the commonly assigned concurrently filed copending application Ser. No. 712,461 and bearing the same title as the present application.
  • the fluid pressure applied to the pistons 104i and 204 at the surfaces 104a and 204a retain the pistons against the bearing sleeves.
  • a radial-piston pump having a housing formed with an axially extending housing bore; an eccentric shaft rotatably received in said housing bore and provided with an eccentric portion therealong; at least one cylinder formed in said housing and slidably receiving a piston driven by said shaft; a suction chamber and a fluid-discharge chamber formed in said housing and communicating with said cylinder for displacement of fluid from said suction chamber to said discharge chamber upon rotation of said shaft and reciprocation of said piston; a fluidintake port formed in said housing and communicating with said suction chamber, a sleeve surrounding said eccentric portion of said shaft and acting upon said piston for displacing same upon rotation of said shaft; means forming at least one passageway having at least a portion extending through said shaft and communicating with one of said chambers while opening within said sleeve and between said sleeve and said eccentric portion for cooling the pump and lubricating said sleeve, said passageway connecting said fluid-intake port with said suction chamber, said shaft having an extremity terminat
  • said second conduit includes a passage formed in said housing and connecting said space with said suction chamber, said constriction being constituted as a throttle orifice provided along said passage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US712817A 1967-06-22 1968-03-13 Radial-piston pump with improved cooling and lubrication Expired - Lifetime US3461809A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DET0034154 1967-06-22

Publications (1)

Publication Number Publication Date
US3461809A true US3461809A (en) 1969-08-19

Family

ID=7558306

Family Applications (1)

Application Number Title Priority Date Filing Date
US712817A Expired - Lifetime US3461809A (en) 1967-06-22 1968-03-13 Radial-piston pump with improved cooling and lubrication

Country Status (5)

Country Link
US (1) US3461809A (ja)
JP (1) JPS5547226B1 (ja)
BR (1) BR6896158D0 (ja)
DE (1) DE1653636C3 (ja)
ES (1) ES349422A2 (ja)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4265165A (en) * 1979-08-27 1981-05-05 Caterpillar Tractor Co. Radial piston fluid translating device with power conserving scavenging means
US5683228A (en) * 1996-04-18 1997-11-04 Caterpillar Inc. Oil pump cavitation relief
WO2013037545A1 (de) * 2011-09-15 2013-03-21 Robert Bosch Gmbh Kraftstoffhochdruckpumpe für ein kraftstoffeinspritzsystem sowie pumpenanordnung

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR902097A (fr) * 1943-09-28 1945-08-17 Freins Hydrauliques Sa Des Pompe hydraulique
US2394285A (en) * 1944-07-27 1946-02-05 Bendix Aviat Corp Pump
US2612837A (en) * 1946-05-21 1952-10-07 American Eng Co Ltd Pump
US2693150A (en) * 1949-07-29 1954-11-02 Smith S Jacking Systems Ltd Pump
US2801596A (en) * 1953-04-02 1957-08-06 Sewell Ronald Percival Multi-cylinder pump
US2818816A (en) * 1954-12-06 1958-01-07 Gen Motors Corp Radial piston pump
US2836120A (en) * 1954-09-14 1958-05-27 Navarro Miguel Variable capacity pump
US2851952A (en) * 1957-06-27 1958-09-16 Lane Edwin Leonard Hydraulic pumps
US3125034A (en) * 1964-03-17 Pump with radial cylinders

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125034A (en) * 1964-03-17 Pump with radial cylinders
FR902097A (fr) * 1943-09-28 1945-08-17 Freins Hydrauliques Sa Des Pompe hydraulique
US2394285A (en) * 1944-07-27 1946-02-05 Bendix Aviat Corp Pump
US2612837A (en) * 1946-05-21 1952-10-07 American Eng Co Ltd Pump
US2693150A (en) * 1949-07-29 1954-11-02 Smith S Jacking Systems Ltd Pump
US2801596A (en) * 1953-04-02 1957-08-06 Sewell Ronald Percival Multi-cylinder pump
US2836120A (en) * 1954-09-14 1958-05-27 Navarro Miguel Variable capacity pump
US2818816A (en) * 1954-12-06 1958-01-07 Gen Motors Corp Radial piston pump
US2851952A (en) * 1957-06-27 1958-09-16 Lane Edwin Leonard Hydraulic pumps

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4265165A (en) * 1979-08-27 1981-05-05 Caterpillar Tractor Co. Radial piston fluid translating device with power conserving scavenging means
US5683228A (en) * 1996-04-18 1997-11-04 Caterpillar Inc. Oil pump cavitation relief
WO2013037545A1 (de) * 2011-09-15 2013-03-21 Robert Bosch Gmbh Kraftstoffhochdruckpumpe für ein kraftstoffeinspritzsystem sowie pumpenanordnung

Also Published As

Publication number Publication date
DE1653636C3 (de) 1974-01-31
ES349422A2 (es) 1969-09-16
DE1653636B2 (de) 1973-07-05
BR6896158D0 (pt) 1973-04-12
DE1653636A1 (de) 1972-04-20
JPS5547226B1 (ja) 1980-11-28

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