EP0276680B1 - Two-speed valve in-star motor - Google Patents

Two-speed valve in-star motor Download PDF

Info

Publication number
EP0276680B1
EP0276680B1 EP88100323A EP88100323A EP0276680B1 EP 0276680 B1 EP0276680 B1 EP 0276680B1 EP 88100323 A EP88100323 A EP 88100323A EP 88100323 A EP88100323 A EP 88100323A EP 0276680 B1 EP0276680 B1 EP 0276680B1
Authority
EP
European Patent Office
Prior art keywords
fluid
fluid pressure
star
pressure chamber
rotary
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
EP88100323A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0276680A3 (en
EP0276680A2 (en
Inventor
Marvin Lloyd Bernstrom
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.)
Eaton Corp
Original Assignee
Eaton Corp
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
Priority claimed from US07/007,882 external-priority patent/US4715798A/en
Application filed by Eaton Corp filed Critical Eaton Corp
Publication of EP0276680A2 publication Critical patent/EP0276680A2/en
Publication of EP0276680A3 publication Critical patent/EP0276680A3/en
Application granted granted Critical
Publication of EP0276680B1 publication Critical patent/EP0276680B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/08—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the rotational speed
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/105—Details concerning timing or distribution valves

Definitions

  • the present invention relates to rotary fluid pressure devices, and more particularly, to such devices which include gerotor displacement mechanisms utilizing low-speed commutating valving.
  • valve-in-star a gerotor motor in which a portion of the gerotor star itself comprises the rotary valve member. It has been recognized that a valve-in-star design should substantially eliminate valve timing errors because of the fixed relationship between the star and the rotaryvalve ports. In addition having fewer elements surrounded by leakage clearances and fewer elements requiring some sort of pressure balancing results in a motor capable of achieving both higher volumetric efficiency as well as higher mechanical efficiency.
  • U.S. Patent No. 4,411,606 A more recent attempt to provide a satisfactory valve-in-star gerotor motor is illustrated in U.S. Patent No. 4,411,606, in which the "manifold valving" or directional valving occurs between the star and the endcap while the commutating valving occurs at the axially opposite end face of the star at the interface of the star and an adjacent valve plate.
  • Such an arrangement effectively requires that the valving be "fixed clearance", as opposed to being pressure balanced or pressure overbalanced.
  • the arrangement in U.S. 4,411,606 requires a plurality of axial bores extending through the star to communicate between the opposite ends of the star. If such bores are fairly small, there is too much flow restriction and too large a pressure drop within the motor, which reduces mechanical efficiency of the motor. On the other hand, if such bores are large enough to avoid excessive flow restriction, the result is a weakening of the star.
  • Low-speed, high-torque gerotor motors of the type to which this invention relates have typically been utilized in systems in which the relief valve would be set at approximately 3,500 psi (240 Bar), and in which the motor would operate at approximately 3,000 psi (206 Bar). More recently, there has been increasing demand in the marketplace for motors capable of operating at relatively higher pressures at least intermittently in systems in which the relief valve may be set as high as 4,500 psi (310 Bar) or even 5,000 psi (345 bar).
  • valve-in-star motor shown in above-cited 3,825,376, the variation in the number of volume chambers communicating with the ports, and the resulting torque ripple, make the motor shown therein unsuitable for high-pressure applications.
  • two-speed means that for any given rate of fluid flow into the motor, it is possible to select between two different motor output speeds; a high-speed (low-torque), and the conventional low-speed (high-torque).
  • U.S. Patent No. 3,778,198 discloses the basic concept for achieving two-speed operation of a gerotor motor.
  • the motor shown in the reference patent is of the spool valve type which has been limited to relatively lower pressures and torques, because of the fixed diametral clearance between the rotating spool valve and the adjacent cylindrical housing surface.
  • U.S. Patent No. 4,480,971 assigned to the assignee of the present invention, teaches a two-speed gerotor motor of the disk valve type which, therefore, is more suited for applications requiring relatively higher pressures and torques. Although it is believed that the device shown in U.S. 4,480,971 will result in a commercially successful two-speed gerotor motor, the design disclosed therein is somewhat large and complex, and is subject to the pressure and torque limitations inherent in disk valve gerotor motors.
  • an improved rotary fluid pressure device of the general type set forth in U.S. Patent No. 4,411,606 wherein the device comprises a housing means including an endcap member defining a fluid inlet port and a fluid outlet port; a gerotor gear set associated with said housing means and including an internally-toothed ring member and an externally-toothed star member eccentrically disposed within the ring member; either the ring member or the star member has orbital movement relative to the other of the members, and the star member has rotational movement relative to the ring member and the housing means; the internal teeth of the ring member and the external teeth of the star interengage to define a plurality N + 1 of expanding and contracting fluid volume chambers during the relative orbital and rotational movements; the device includes a shaft means and means operable to transmit the rotational movement of the star member to the shaft means; the endcap member defines a first fluid pressure chamber in continuous communication with either the inlet or outlet port, and a second fluid pressure
  • the improved device is characterized by: (a) the end surface of the star member is in sliding, sealing engagement with an adjacent surface of the endcap member; (b) the endcap member defines a third fluid pressure chamber and a control fluid passage in communication with the third fluid pressure chamber; (c) the star member defines a third manifold zone in continuous fluid communication with the third fluid pressure chamber; (d) the end surface of the star member defines a third set of fluid ports in continuous fluid communication with the third manifold zone; (e) the adjacent surface of the endcap member defines a plurality N + 1 of valve passages, each of the valve passages being in continuous fluid communication with one of the expanding and contracting fluid volume chambers; (f) the first, second and third sets of fluid ports are in commutating fluid communication with the plurality N + 1 of valve passages defined by the endcap member in response to the relative rotational movement of the star member; and (g) a valve means is selectively operable between a first condition communicating the control fluid passage to the first fluid pressure chamber and a second condition communicating the control
  • FIG. 1 illustrates a low-speed, high-torque gerotor motor.
  • the hydraulic motor shown in FIG. 1 comprises a plurality of sections secured together, such as by a plurality of bolts 11.
  • the sections of the motor include a shaft housing portion 13, a gerotor displacement mechanism 15, and an endcap member 17.
  • the gerotor displacement mechanism 15 (best seen in FIG. 3) is well known in the art, is shown and described in great detail in U.S. Patent No. 4,343,600, which is assigned to the assignee of the present invention, is incorporated herein by reference, and therefore will be described only briefly herein. More specifically, the displacement mechanism 15 is a Geroler O gear set comprising an internally-toothed ring member 19 defining a plurality of generally semi-cylindrical openings, with a cylindrical roller member 21 disposed in each of the openings, and serving as the internal teeth of the ring member 19.
  • Eccentrically disposed within the ring 19 is an externally-toothed star 23, typically having one less external tooth than the number of internal teeth 21, thus permitting the star 23 to orbit and rotate relative to the ring member 19.
  • the relative orbital and rotational movement between the ring 19 and the star 23 defines a plurality of expanding fluid volume chambers 25 and a plurality of contracting fluid volume chambers 27, as is well known in the art.
  • the star 23 defines a plurality of straight, internal splines 29, which are in engagement with a set of external crowned splines 31 formed on one end of a main drive shaft 33. Disposed at the opposite end of the main drive shaft 33 is another set of external, crowned splines 35, adapted to be in engagement with another set of straight, internal splines defined by some form of rotary output such as a shaft or wheel hub.
  • gerotor motors of the type to which the invention relates may include a rotary output shaft, supported by suitable bearings, such as is illustrated in U.S. 4,343,600, and it will be understood that the invention is not limited to any particular configuration of output shaft. It is essential only that the device include some form of shaft means operable to transmit the rotary motion of the star 23.
  • the ring member 19 includes nine internal teeth 21 and the star 23 includes eight external teeth, eight orbits of the star 23 result in one complete rotation thereof and one complete rotation of the output end of the main drive shaft 33 as is well known in the art.
  • the endcap member 17 includes a fluid inlet port 37 and a fluid outlet port 39.
  • the endcap member 17 includes an end surface 41 in sliding sealing engagement with an end surface 42 (see FIG. 1) of the star 23 and disposed adjacent the gerotor gear set 15.
  • the end surface 41 defines a fluid pressure chamber 43 which is in fluid communication with the fluid inlet port 37, through a fluid passage 36, by means of a tubular member 45 which is pressed into a circular opening defined by the endcap 17.
  • the end surface 41 further defines an annular fluid pressure chamber 47 which is preferably disposed to be concentric with the fluid pressure chamber 43.
  • the pressure chamber 47 is in fluid communication with the fluid outlet port 39 by means of a passage 49.
  • annular fluid pressure chamber 51 Disposed radially between the fluid pressure chambers 43 and 47 is an annular fluid pressure chamber 51, which is in fluid communication with a cored passage 53, defined by the endcap member 17, by means of a generally tubular member 55.
  • the tubular member 55 is pressed into a circular opening in the endcap member 17 and serves to separate the annular fluid pressure chambers 47 and 51.
  • each of the valve passages 57 would typically comprise a radially oriented, milled slot, each of which would be disposed in permanent, continuous fluid communication with an adjacent one of the volume chambers 25 or 27.
  • the valve passages 57 are disposed in a generally annular pattern which is concentric relative to the annular fluid pressure chambers 43, 47 and 51, as is illustrated in FIG. 2.
  • the star 23 comprises an assembly of two separate parts.
  • the star 23 comprises two separate powdered metal parts, including a main portion 59, which includes the external teeth, and an insert or plug 61.
  • the main portion 59 and the insert 61 cooperate to define the various fluid zones, passages and ports which will be described subsequently.
  • the star 23 defines a central manifold zone 63, which is in continuous fluid communication with the pressure chamber 43.
  • Concentric with the manifold zone 63 is another outer manifold zone 65, which is in continuous fluid communication with the annular pressure chamber 47.
  • zone in regard to the manifold zones 63, 65 and 67 will be understood by those skilled in the art to mean and include either a single opening (as in the case of the manifold zone 63), or a plurality of separate, circumferentially spaced openings (as in the case of the manifold zones 65 and 67).
  • the end surface 42 of the star 23 defines a set of fluid ports 69, each of which is in fluid communication with the central manifold zone 63 by means of a fluid passage 71 (see FIG. 5A).
  • a fluid passage 71 see FIG. 5A.
  • the end surface 42 of the star 23 further defines a set of fluid ports 73, each of which is in fluid communication with one of the openings of the outer manifold zone 65 by means of a fluid passage 75.
  • a fluid passage 75 there are eight of the fluid ports 73 and of the fluid passages 75.
  • the end surface 42 of the star 23 also defines a set of fluid ports 77, each of which is in continuous fluid communication with one of the openings of the intermediate manifold zone 67 by means of a fluid passage 79.
  • low pressure exhaust fluid is communicated from the contracting volume chambers 27 through those valve passages 57 which are instantaneously in communication therewith, and this exhaustfluid then flows into certain of the fluid ports 77 which are instantaneously in communication with the particular valve passages 57 containing exhaust fluid.
  • the shaft housing portion 13 defines a recess 81 and seated within the recess 81 is a pressure-balancing plate 83.
  • the balancing plate 83 defines a plurality of openings 85, each of which is in communication with one of the volume chambers 25 or 27.
  • Each of the openings 85 communicates with a pressure-balancing recess 87 which is disposed on the side of the plate 83 opposite the gerotor gear set 15. Items 81 through 87 have been recited herein primarily for the purpose of completeness.
  • pressure balancing is generally well known in the art of gerotor motors and forms no essential part of the present invention, there will be no further detailed description of the pressure-balancing plate 83 or of the size or shape of the recesses 87. It will be understood by those skilled in the art that the pressure-balancing plate 83 may be used either to "balance” the star 23 in the axial direction, such that the hydraulic forces acting on the star 23 in opposite directions are approximately the same, or alternatively, the pressure-balancing plate 83 may be used to "overbalance" the star 23 into tight sealing engagement with the end surface 41 of the endcap member 17.
  • FIG. 6 is a view partly in cross-section (on line 6-6 of FIG. 1) and partly in schematic.
  • the endcap member 17 defines a spool bore 91 which is intersected by the fluid passages 36, 49, and 53, at locations axially spaced apart as shown in FIG. 6.
  • the axially opposite ends of the spool bore 91 are closed by a pair of threaded fittings 93 and 95, and disposed within the spool bore 91 is a valve spool 97.
  • the valve spool 97 is biased toward the left in FIG. 6 by a spring member99, and is biased toward the right, to the position shown in FIG. 6 by fluid pressure in pressure chamber 101.
  • the fluid pressure needed to bias the valve spool 97 to the position shown in FIG. 6 may be communicated to the pressure chamber 101 in any one of several ways well known to those skilled in the art, and which form no part of the present invention.
  • high-pressure fluid will be present in all of the fluid ports 69 and fluid ports 77, from where high pressure will be communicated through the respective fluid passages 57 into the expanding volume chambers 25 (shading indicates high pressure fluid), causing the star 23 to orbit in a clockwise direction, while rotating in a counterclockwise direction, as viewed in FIG. 6.
  • low-pressure fluid is communicated from the contracting volume chambers 27 through the respective fluid passages 57 into certain of the fluid ports 73.
  • Exhaust fluid from the ports 73 is communicated through the outer manifold zone 65 to the pressure chamber 47, and from there through the fluid passage 49 to the outlet port 39. Therefore, with the valve spool 97 in the position shown in FIG. 6, high-pressure fluid is communicated to all four of the expanding volume chambers 25, while exhaustfluid is communicated from all four of the contracting volume chambers 27, and the gerotor motor operates in a normal low-speed, high-torque (LSHT) mode.
  • LSHT normal low-speed, high-tor
  • FIG. 7 the device of the present invention will be described in connection with operation in the high-speed, low-torque (HSLT) mode.
  • HSLT high-speed, low-torque
  • this mode of operation with high-pressure communicated to the inlet port 37, there will be high pressure in only pressure chamber 43, while both of the pressure chambers 51 and 47 are in communication with low-pressure fluid, by means of the fluid passages 53 and 49, respectively.
  • high-pressure fluid is communicated from the pressure chamber 43 through the central manifold zone 63 into the fluid ports 69. As may be seen in FIG. 7, this results in communication of high-pressure fluid into only two of the expanding volume chambers 25.
  • exhaust fluid from the contracting volume chambers 27 is communicated through the associated fluid ports 73, outer manifold zone 65, and pressure chamber 47 as described in connection with FIG. 6.
  • the fluid passages 49 and 53 are in open communication, a portion of the low-pressure exhaust fluid from the contracting volume chambers 27 is communicated through the fluid passage 53 and into the pressure chamber 51, and from there into the intermediate manifold zone 67 and through the fluid ports 77 into the other two of the expanding volume chambers 25.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP88100323A 1987-01-28 1988-01-12 Two-speed valve in-star motor Expired - Lifetime EP0276680B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US07/007,882 US4715798A (en) 1986-05-01 1987-01-28 Two-speed valve-in star motor
US7882 1987-01-28

Publications (3)

Publication Number Publication Date
EP0276680A2 EP0276680A2 (en) 1988-08-03
EP0276680A3 EP0276680A3 (en) 1989-05-10
EP0276680B1 true EP0276680B1 (en) 1991-01-09

Family

ID=21728611

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88100323A Expired - Lifetime EP0276680B1 (en) 1987-01-28 1988-01-12 Two-speed valve in-star motor

Country Status (4)

Country Link
EP (1) EP0276680B1 (ja)
JP (1) JPH0751938B2 (ja)
DE (1) DE3861468D1 (ja)
DK (1) DK40388A (ja)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2764961B2 (ja) * 1988-11-18 1998-06-11 ヤマハ株式会社 電子楽器
US8821139B2 (en) * 2010-08-03 2014-09-02 Eaton Corporation Balance plate assembly for a fluid device
CN102959236B (zh) * 2010-12-07 2015-09-30 怀特(中国)驱动产品有限公司 用于双速摆线装置的分配器组件
US11493018B2 (en) 2020-01-03 2022-11-08 Parker-Hannifin Corporation Hydraulic motor with anti-cogging features

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2240632C2 (de) * 1972-08-18 1983-09-01 Danfoss A/S, 6430 Nordborg Rotationskolbenmaschine für Flüssigkeiten
US3892503A (en) * 1974-01-23 1975-07-01 Sperry Rand Corp Apparatus and method for multiple mode motor
JPS5941033B2 (ja) * 1979-03-09 1984-10-04 株式会社トキメック 可変容量型流体変換装置
US4480971A (en) * 1983-01-17 1984-11-06 Eaton Corporation Two-speed gerotor motor

Also Published As

Publication number Publication date
DK40388D0 (da) 1988-01-27
EP0276680A3 (en) 1989-05-10
DE3861468D1 (de) 1991-02-14
JPS63195386A (ja) 1988-08-12
EP0276680A2 (en) 1988-08-03
JPH0751938B2 (ja) 1995-06-05
DK40388A (da) 1988-07-29

Similar Documents

Publication Publication Date Title
US4715798A (en) Two-speed valve-in star motor
EP0116217B1 (en) Two-speed gerotor motor
EP0213154B1 (en) Rotary motion fluid apparatus
US4493622A (en) Variable displacement motor
EP0408011B1 (en) Gerotor motor and improved pressure balancing therefor
EP0054161B1 (en) Gerotor gear set device with integral rotor and commutator
US3452680A (en) Hydraulic motor-pump assembly
US6126424A (en) Transistion valving for gerotor motors
EP0756085B1 (en) Gerotor motor and commuting valve
US6099280A (en) Two speed geroter motor with external pocket recirculation
EP0394821A2 (en) Valve for gerotor motor
US3910732A (en) Gerotor pump or motor
EP0276680B1 (en) Two-speed valve in-star motor
US4756676A (en) Gerotor motor with valving in gerotor star
EP0412403B1 (en) Rotary fluid pressure device and improved stationary valve plate therefor
US3352247A (en) Fluid pressure device with dual feed and exhaust
US5593296A (en) Hydraulic motor and pressure relieving means for valve plate thereof
US4334843A (en) Gerotor machine with valve plates attached to wheel gear
EP0387713A3 (en) Gerotor type hydraulic motor or pump
US3591321A (en) Valving in combination with fluid pressure operating means
US4592704A (en) Motor with improved low-speed operation
JP3051238B2 (ja) 油圧モータ

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19890908

17Q First examination report despatched

Effective date: 19900509

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

ITF It: translation for a ep patent filed
REF Corresponds to:

Ref document number: 3861468

Country of ref document: DE

Date of ref document: 19910214

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19981211

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19990107

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19990128

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000112

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20000112

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000929

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20001101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050112