US3899957A - Radial piston fluid translating device with cylinder positioning means - Google Patents

Radial piston fluid translating device with cylinder positioning means Download PDF

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Publication number
US3899957A
US3899957A US408823A US40882373A US3899957A US 3899957 A US3899957 A US 3899957A US 408823 A US408823 A US 408823A US 40882373 A US40882373 A US 40882373A US 3899957 A US3899957 A US 3899957A
Authority
US
United States
Prior art keywords
race
cylinders
rotor
spokes
guide ring
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
US408823A
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English (en)
Inventor
Jr Guy C Carlson
Willard J Haak
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.)
Caterpillar Inc
Original Assignee
Caterpillar Tractor Co
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 Caterpillar Tractor Co filed Critical Caterpillar Tractor Co
Priority to US408823A priority Critical patent/US3899957A/en
Priority to GB4396774A priority patent/GB1426148A/en
Priority to JP49121298A priority patent/JPS5759915B2/ja
Application granted granted Critical
Publication of US3899957A publication Critical patent/US3899957A/en
Assigned to CATERPILLAR INC., A CORP. OF DE. reassignment CATERPILLAR INC., A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CATERPILLAR TRACTOR CO., A CORP. OF CALIF.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/068—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with an actuated or actuating element being at the inner ends of the cylinders
    • 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
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0641—Details, component parts specially adapted for such machines
    • F01B1/0655—Details, component parts specially adapted for such machines cylinders

Definitions

  • TRACT 21 1 APPL 403 23 A fluid pump or motor of the type having a rotor with hollow radially directed spokes each extending into a separate one of a series of cylinders that ride against [52] US. Cl z 91/490 an eccentricany positioned circular race as the rotor [51 l lilt- Cl. F018 13/06 tunfls is provided with resilient means f maintaining [58] Field of Search 91/490, 491', 417/273 the Cylinders adjacent the race and in propel. Orienta tion relative thereto.
  • Certain mechanisms may be caused to function either as a pump or as a motor according to the external connections made to the mechanism. If externally driven, such mechanisms can draw fluid from a source and discharge the fluid under pressure thereby acting as a pump. Conversely, if fluid from a source is supplied under pressure, the mechanism may function as a motor. Accordingly, the structure of the present invention will hereinafter be referred to as a fluid translating device and this term should be understood to refer to either a pump or a motor or to a device which mayserve both functions at different times.
  • Radial piston pumps or motors constitute a compact and highly efficient class of fluid translating devices. These mechanisms employ a rotor having hollow radial spokes, each of which extends into a separate one of a plurality of cylinders. The cylinders in turn ride against a stationary circular race which is eccentrically positioned relative to the axis of rotation of the rotor. Ac cordingly. as the rotor turns, each cylinder reciprocates relative to the associated spoke and a pumping or motor action is realized depending on the nature of the fluid and mechanical connections made to the device.
  • Frictional forces resulting from the cylinders riding against the race and other effects as well may generate considerable heat. As a consequence, thermal expansion effects must be provided for to avoid binding, extreme wear and other adverse effects. If the guide ring were to be positioned to hold the cylinders tightly against the race while the device is in a relatively cold condition such as at start-up, then thermal expansion of such elements as the cylinders race and the like could cause tight clamping of the cylinder flanges against the race. To avoid this, it has been the practice to provide a small clearance between the race and the guide rings additional to the spacing needed to accommodate the cylinder flanges therebetween in a cold condition. Typically, at least several thousandths of an inch clearance are required for this purpose.
  • This amount of clearance is sufficient to allow significant tipping of a cylinder relative to the race and the spoke upon which it is carried. Accelerated wear or other damage may sometimes occur upon start-up of the device in a cold condition. Most notably, gouging of the leading edge of the cylinder into the adjacent race surface may occur.
  • This invention provides a means for holding the cylinders of a radial piston fluid translating device adjacent the race thereof and in proper orientation relative thereto under all conditions while enabling self adjustment of the mechanism to accommodate to thermal expansion and contraction of components.
  • the circular guide means which hold the cylinder flanges at the race is spaced a substantial distance inward from the cylinder flanges and resilient means are disposed between the guide means and the flanges to continually urge the cylinders towards the race.
  • FIG. I is a cross-section view, with portions of internal elements broken out, of a radial piston fluid translating device embodying the invention
  • FIG. 2 is an angled axial section view of the mechanism of FIG. 1 taken along angled line 11-" thereof,
  • FIG. 3 is a partial radial section view of the cylinder region of a first modification of the fluid translating device
  • FIG. 4 is a fragmentary section view of the structure of FIG. 3 taken along line lV-IV thereof, and
  • FIG. 5 is a partial radial section view of the cylinder region of a second modification of the fluid translating device.
  • a fluid translating device 11 of the type to which the invention is applicable may typically have an annular outer housing 12 including an integral end member 13 and is closed at the other end by an end plate I4 secured to the housing by bolts 16. Housing 12 and end plate 14 define a chamber 17 which has semicircular portions 19 and 19' at opposite sides thereof connected by a short straight section 18.
  • rotor support element 21 is secured to the center of housing end member 13 and extends axially into chamber 17 through an opening 22 in end member 13.
  • a rotatably shaft 23 extends into the chamber 17, in coaxial relationship to rotor support 21, through an opening 24 in end plate 14 and in journaled therein by a bearing 26.
  • the inner end of shaft 23 is journaled in a well 27 in the inner end of member 21 by an additional bearing 28.
  • the rotor 29 of the device 11 has an inner annular hub portion 31 which fits coaxially on the inner end of rotor support 21 within chamber 17 for rotation thereon.
  • a spline coupling 32 at one end of the sleeve portion 31 links the rotor 29 to shaft 23 for rotation therewith.
  • Rotor 29 is provided with a plurality of radially directed spokes 33, of which there are seven in this example, and each of which has a central passage 34 extending therethrough.
  • Each such spoke is further provided with a piston ring 36 secured coaxially to the radially outermost end of the spoke, the piston rings each having a convex outer surface 37 which enables each cylinder to tilt relative to the associated spoke.
  • annular outer race member 38 and a relatively thin inner race member 39 fitted into the circular inner surface thereof is disposed in chamber 17 in position to encircle the rotor 29 in spaced relation therefrom. While the inner surfaces of race members 38 and 39 are strictly circular, the outer surface of race member 38 has a curvature conforming to that of the circular portions 19 and 19' of chamber 17, but has a flattened portion 41 at the center adjacent the flat straight portion 18 of chamber 17. Accordingly, for purposes to be hereinafter described, the race members 38 and 39 may be shifted diametrically within chamber 17 between ends 19 and 19' of the chamber. To provide for shifting of the race members in this manner and to hold such members at the selected position, circular seals 42 are disposed between outer race member 38 and housing end portion 13 and cover plate 16.
  • sealing means 43 are disposed between such circular seals and the adjacent flat surfaces 18 and 41 of housing 12 and outer race 38 to extend along a plane which includes the rotational axis of rotor 29 and bisects the flat housing surfaces 18.
  • One of a pair of bores 44 extends through housing 12 at each side of the sealing means 43.
  • the race 38 may be shifted as described above and held at the selected position by forcing high pressure fluid into one of the bores 44 while venting the other bore 44.
  • each spoke 33 extends into a cylindrical skirt portion 46 of an associated separate one of a plurality of cylinders 47.
  • the radially outermost end of each such cylinder 47 has a slipper pad flange 48 having an arcuate outer surface 49 for riding against the inner surface of inner race member 39 as the hub 29 revolves.
  • the outer surface of each slipper pad may have a shallow recess 51 communicated with the interior of the cylinder through an aperture 52.
  • each cylinder 47 reciprocates relative to the associated rotor spoke 33 as the rotor revolves.
  • four passages 53, 54, 56 and 57 extend within rotor support 21. Passages 53 and 54 both communicate with a first port 58 at the exterior surface of rotor support 21 while passages 56 and 57 both communicate with a second port 59 thereat, the two ports being connectable with an external source of fluid and a discharge for such fluid as will hereinafter be described in more detail.
  • passages 53 and 54 terminate at radial openings 61 and 62 respectively that are in communication with the internal passages 34 of the particular spokes which at any given time are in passage between opposite ends of housing chamber 17 at the side thereof at which the cylinders are being urged radially inwardly on the associated spokes 33.
  • passages 56 and 57 terminate at radially directed openings 63 and 64 respectively which communicate with the internal passages of the particular rotor spokes 33 that at any given time are moving between the ends of chamber 17 at the other side wherein the cylinders 47 are moving radially outward relative to the associated spokes 33.
  • shaft 23 is forcibly turned (e.g., clockwise) by an external motor.
  • Port 59 may be connected to a source of fluid to be pumped while port 58 is communicated with the means which is to receive the discharge of the pump.
  • the expanding volume within those of the cylinders 47 which are communicated with passages 63 and 64 at any given time causes fluid to be drawn into port 59 by suction while the decreasing volume within those of the cylinders which are communicated with openings 61 and 62 at any given time causes fluid to be forcibly discharged from port 58.
  • the direction of rotor rotation while functioning as a motor or the direction of flow between the two ports 58 and 59 in the pumping mode can be controlled by shifting the race member 38 from one end of housing chamber 17 to the other in the manner previously described.
  • the direction of the eccentricity of the path of cylinders 47 relative to the axis of rotation of hub 29 is thereby shifted in such a manner that the motor or pumping action reverses.
  • one of a pair of guide rings 66 is disposed at each side of cylinders 47 within the region encircled by inner race member 39 and in coaxial relationship therewith.
  • An annular collar 67 encircles each cylinder 47 adjacent the slipper pad flange 48 of the cylinder and each such collar overlaps and rides against the guide rings 66, the guide rings and collars being proportioned to provide a clearance space 68 between the collars and flanges 48 to allow for thermal expansion without binding.
  • each cylinder 47 is continuously urged towards the inner race 39 while enabling adjustment to thermal expansion effects.
  • FIGS. 3 and 4 illustrate a modification of the invention wherein such means is a single annular wave washer 72 encircling cylinder 47' between collar 67' and slipper pad flange 48'.
  • Such washers 72 are formed of resilient material and, as best seen in FIG. 4, have an undulated curvature whereby the washers may be compressed between collars 67 and flanges 48' to exert the desired outward force on the cylinders.
  • FIG. 5 illustrates still another modification in which the resilient force exerting means is a Belleville spring 73 encircling cylinder 47" between collar 67" and slipper pad flange 48".
  • Such springs 73 are also formed of resilient material and have a truncated conical configuration so that compression of the spring between the collar and flange causes a force to be exerted therebetween.
  • a fluid translating device comprising:
  • resilient means for urging each of said cylinders outwardly from the rotational axis of said rotor and towards said inner surface of said race, said resilient, means being disposed between said flanges and said guide ring to act against said flanges and to react against said guide ring.
  • said rotor having hollow spokes extending radially towards the inner surface of said race and having means for admitting fluid to said spokes during a first portion of the angular movement thereof and for releasing fluid from said spokes during another portion of the angular movement thereof,
  • each of said collars has a plurality of wells therein opening at the surface of the collar which faces said flange of the associated one of said cylinders, and wherein said resilient means comprises a plurality of coil compression springs each being disposed in one of said wells of said collars and extending therefrom towards said flange of the associated one of said cylinders.
  • said resilient means comprises a plurality of annular wave washers each encircling one of said cylinders between said flange thereof and said collar thereon, said washers being formed of resilient material and having an undulated configuration.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US408823A 1973-10-23 1973-10-23 Radial piston fluid translating device with cylinder positioning means Expired - Lifetime US3899957A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US408823A US3899957A (en) 1973-10-23 1973-10-23 Radial piston fluid translating device with cylinder positioning means
GB4396774A GB1426148A (en) 1973-10-23 1974-10-10 Radial piston fluid translating device with cylinder positioning means
JP49121298A JPS5759915B2 (enrdf_load_stackoverflow) 1973-10-23 1974-10-21

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US408823A US3899957A (en) 1973-10-23 1973-10-23 Radial piston fluid translating device with cylinder positioning means

Publications (1)

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US3899957A true US3899957A (en) 1975-08-19

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US (1) US3899957A (enrdf_load_stackoverflow)
JP (1) JPS5759915B2 (enrdf_load_stackoverflow)
GB (1) GB1426148A (enrdf_load_stackoverflow)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4048907A (en) * 1975-12-08 1977-09-20 Caterpillar Tractor Co. Radial piston pump or motor with unrestricted inlet means
US4074615A (en) * 1976-10-07 1978-02-21 Caterpillar Tractor Co. Orbiting motor gear drive
US4147092A (en) * 1977-02-28 1979-04-03 Caterpillar Tractor Co. Self-filling fluid device
US4185521A (en) * 1975-03-10 1980-01-29 Caterpillar Tractor Co. Hydraulic control system for a hydrostatic-mechanical transmission
US4237774A (en) * 1979-07-16 1980-12-09 Caterpillar Tractor Co. Displacement control valving for a radial piston device
US20090060758A1 (en) * 2004-06-30 2009-03-05 S.A.I. Societa' Apparecchiature Idrauliche Spa Fluid machine with radial cylinders
US20100094517A1 (en) * 2007-03-20 2010-04-15 Yoshihiro Takei Flow control valve for clutch control device
CN102172829A (zh) * 2011-01-15 2011-09-07 中山市美捷时喷雾阀有限公司 一种锁弯咀机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57141216A (en) * 1981-02-25 1982-09-01 Nippon Shokusei Kk Increasing method of keeping fertilizer effect

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2503614A (en) * 1944-03-25 1950-04-11 Eynard Elysee Hydraulic pump
US2818816A (en) * 1954-12-06 1958-01-07 Gen Motors Corp Radial piston pump
US3274946A (en) * 1964-04-13 1966-09-27 Edward E Simmons Pump
US3514224A (en) * 1967-06-24 1970-05-26 Teves Gmbh Alfred Radial piston pump with piston-coupling means
US3742818A (en) * 1971-06-01 1973-07-03 Caterpillar Tractor Co Piston and retaining assemblies for a radial piston pump or motor
US3777622A (en) * 1972-03-24 1973-12-11 Gen Motors Corp Pumps and motors

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5032279Y2 (enrdf_load_stackoverflow) * 1971-04-02 1975-09-20

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2503614A (en) * 1944-03-25 1950-04-11 Eynard Elysee Hydraulic pump
US2818816A (en) * 1954-12-06 1958-01-07 Gen Motors Corp Radial piston pump
US3274946A (en) * 1964-04-13 1966-09-27 Edward E Simmons Pump
US3514224A (en) * 1967-06-24 1970-05-26 Teves Gmbh Alfred Radial piston pump with piston-coupling means
US3742818A (en) * 1971-06-01 1973-07-03 Caterpillar Tractor Co Piston and retaining assemblies for a radial piston pump or motor
US3777622A (en) * 1972-03-24 1973-12-11 Gen Motors Corp Pumps and motors

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4185521A (en) * 1975-03-10 1980-01-29 Caterpillar Tractor Co. Hydraulic control system for a hydrostatic-mechanical transmission
US4048907A (en) * 1975-12-08 1977-09-20 Caterpillar Tractor Co. Radial piston pump or motor with unrestricted inlet means
US4074615A (en) * 1976-10-07 1978-02-21 Caterpillar Tractor Co. Orbiting motor gear drive
US4147092A (en) * 1977-02-28 1979-04-03 Caterpillar Tractor Co. Self-filling fluid device
US4237774A (en) * 1979-07-16 1980-12-09 Caterpillar Tractor Co. Displacement control valving for a radial piston device
WO1981000287A1 (en) * 1979-07-16 1981-02-05 Caterpillar Tractor Co Displacement control valving for a radial piston device
US20090060758A1 (en) * 2004-06-30 2009-03-05 S.A.I. Societa' Apparecchiature Idrauliche Spa Fluid machine with radial cylinders
US8382449B2 (en) * 2004-06-30 2013-02-26 S.A.I. Societa' Apparecchiature Idrauliche Spa Fluid machine with radial cylinders
US20100094517A1 (en) * 2007-03-20 2010-04-15 Yoshihiro Takei Flow control valve for clutch control device
US8265844B2 (en) * 2007-03-20 2012-09-11 Isuzu Motors Limited Flow control valve for clutch control device
CN102172829A (zh) * 2011-01-15 2011-09-07 中山市美捷时喷雾阀有限公司 一种锁弯咀机
CN102172829B (zh) * 2011-01-15 2013-01-02 中山市美捷时喷雾阀有限公司 一种锁弯咀机

Also Published As

Publication number Publication date
JPS5759915B2 (enrdf_load_stackoverflow) 1982-12-16
GB1426148A (en) 1976-02-25
JPS5073203A (enrdf_load_stackoverflow) 1975-06-17

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Legal Events

Date Code Title Description
AS Assignment

Owner name: CATERPILLAR INC., 100 N.E. ADAMS STREET, PEORIA, I

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905

Effective date: 19860515

Owner name: CATERPILLAR INC., A CORP. OF DE.,ILLINOIS

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905

Effective date: 19860515