EP0276680A2 - Ventil für Sternmotor mit zwei Geschwindigkeiten - Google Patents

Ventil für Sternmotor mit zwei Geschwindigkeiten Download PDF

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Publication number
EP0276680A2
EP0276680A2 EP88100323A EP88100323A EP0276680A2 EP 0276680 A2 EP0276680 A2 EP 0276680A2 EP 88100323 A EP88100323 A EP 88100323A EP 88100323 A EP88100323 A EP 88100323A EP 0276680 A2 EP0276680 A2 EP 0276680A2
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.)
Granted
Application number
EP88100323A
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English (en)
French (fr)
Other versions
EP0276680A3 (en
EP0276680B1 (de
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/de
Publication of EP0276680A3 publication Critical patent/EP0276680A3/en
Application granted granted Critical
Publication of EP0276680B1 publication Critical patent/EP0276680B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
  • a valve-in-star design should substan­tially eliminate valve timing errors because of the fixed re­lationship between the star and the rotary valve ports.
  • U. S. Patent No. 3,825,376 illustrates one fairly early attempt at a valve-in-star design.
  • each of the rotary ports associated with the gerotor star opened directly into the volume chamber, thus interrupting the star profile, which has long been recognized as being undesirable.
  • 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.
  • 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, and in which the motor would operate at approximately 3,000 psi. More recently, there has been increasing demand in the marketplace for motors capable of operating at relatively high pressures, at least intermittently, in systems in which the relief valve may be set as high as 4,500 psi or even 5,000 psi.
  • 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.
  • 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.
  • 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
  • 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
  • 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® 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 exhaust fluid 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 member 99, 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 exhaust fluid 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-torque
  • 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
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP88100323A 1987-01-28 1988-01-12 Ventil für Sternmotor mit zwei Geschwindigkeiten Expired - Lifetime EP0276680B1 (de)

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

Family

ID=21728611

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88100323A Expired - Lifetime EP0276680B1 (de) 1987-01-28 1988-01-12 Ventil für Sternmotor mit zwei Geschwindigkeiten

Country Status (4)

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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012075625A1 (en) * 2010-12-07 2012-06-14 White (China) Drive Products Co., Ltd Distributor assembly for two-speed gerotor device
WO2012018878A3 (en) * 2010-08-03 2013-09-19 Eaton Corporation Balance plate assembly for a fluid device
US11493018B2 (en) 2020-01-03 2022-11-08 Parker-Hannifin Corporation Hydraulic motor with anti-cogging features

Families Citing this family (1)

* 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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2196678A6 (de) * 1972-08-18 1974-03-15 Danfoss As
US3892503A (en) * 1974-01-23 1975-07-01 Sperry Rand Corp Apparatus and method for multiple mode motor
DE3008832A1 (de) * 1979-03-09 1980-09-18 Tokyo Keiki Kk Rotationskolbenmaschine mit umsteuerbarem arbeitsmitteldurchsatz
US4480971A (en) * 1983-01-17 1984-11-06 Eaton Corporation Two-speed gerotor motor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2196678A6 (de) * 1972-08-18 1974-03-15 Danfoss As
US3892503A (en) * 1974-01-23 1975-07-01 Sperry Rand Corp Apparatus and method for multiple mode motor
DE3008832A1 (de) * 1979-03-09 1980-09-18 Tokyo Keiki Kk Rotationskolbenmaschine mit umsteuerbarem arbeitsmitteldurchsatz
US4480971A (en) * 1983-01-17 1984-11-06 Eaton Corporation Two-speed gerotor motor

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012018878A3 (en) * 2010-08-03 2013-09-19 Eaton Corporation Balance plate assembly for a fluid device
US8821139B2 (en) 2010-08-03 2014-09-02 Eaton Corporation Balance plate assembly for a fluid device
WO2012075625A1 (en) * 2010-12-07 2012-06-14 White (China) Drive Products Co., Ltd Distributor assembly for two-speed gerotor device
US8684710B2 (en) 2010-12-07 2014-04-01 White (China) Drive Products Co., Ltd. Distributor assembly for two-speed gerotor device
US11493018B2 (en) 2020-01-03 2022-11-08 Parker-Hannifin Corporation Hydraulic motor with anti-cogging features

Also Published As

Publication number Publication date
DK40388D0 (da) 1988-01-27
DK40388A (da) 1988-07-29
JPS63195386A (ja) 1988-08-12
DE3861468D1 (de) 1991-02-14
JPH0751938B2 (ja) 1995-06-05
EP0276680A3 (en) 1989-05-10
EP0276680B1 (de) 1991-01-09

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