EP1158165A2 - Moteur hydraulique du type gerotor - Google Patents

Moteur hydraulique du type gerotor Download PDF

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Publication number
EP1158165A2
EP1158165A2 EP01112161A EP01112161A EP1158165A2 EP 1158165 A2 EP1158165 A2 EP 1158165A2 EP 01112161 A EP01112161 A EP 01112161A EP 01112161 A EP01112161 A EP 01112161A EP 1158165 A2 EP1158165 A2 EP 1158165A2
Authority
EP
European Patent Office
Prior art keywords
fluid
stationary valve
fluid communication
passage portion
stationary
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.)
Withdrawn
Application number
EP01112161A
Other languages
German (de)
English (en)
Other versions
EP1158165A3 (fr
Inventor
Donald M. Haarstad
Gary R. Kassen
Jarett D. Millar
Marvin L. 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
Application filed by Eaton Corp filed Critical Eaton Corp
Publication of EP1158165A2 publication Critical patent/EP1158165A2/fr
Publication of EP1158165A3 publication Critical patent/EP1158165A3/fr
Withdrawn legal-status Critical Current

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    • 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
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • 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
    • F04C2/104—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 having an articulated driving shaft

Definitions

  • the present invention relates to rotary fluid pressure devices of the type in which a gerotor gear set serves as the fluid displacement mechanism, and more particularly, to such devices which are provided with multiple speed ratio capability.
  • LSHT low-speed, high-torque
  • One common application for low-speed, high-torque gerotor motors is vehicle propulsion, wherein the vehicle includes an engine driven pump which provides pressurized fluid to a pair of gerotor motors, with each motor being associated with one of the drive wheels.
  • vehicle propulsion wherein the vehicle includes an engine driven pump which provides pressurized fluid to a pair of gerotor motors, with each motor being associated with one of the drive wheels.
  • gerotors will be understood to mean and include both conventional gerotors, as well as roller gerotors.
  • a gerotor motor may be operated as a two speed ratio device by providing valving which can effectively "recirculate" fluid between expanding and contracting fluid volume chambers of the gerotor gear set. In other words, if the inlet port communicates with all of the expanding chambers, and all of the contracting chambers communicate with the outlet port, the motor operates in the normal low-speed, high-torque mode.
  • each volume chamber within the gerotor gear set has the opportunity to be a "recirculating" volume chamber, both as the volume chamber expands and as it contracts, while the motor is operating in the high-speed, low-torque mode.
  • a recirculating volume chamber is a condition referred to as "oddly spaced" recirculating volume chambers which, it is believed, has led to an uneven torque ripple when operating in the high-speed, low-torque mode.
  • each recirculating volume chamber is put in fluid communication with a recirculation chamber (hence the term "external" recirculation) during operation in the high-speed low-torque mode.
  • the recirculation chamber contains relatively high pressure fluid, and thus, all of the recirculating volume chambers contain relatively high-pressure, thus substantially eliminating the tendency for cavitation to occur during operation in the HSLT mode.
  • the "ratio" in the LSHT mode is, by definition, 1.0:1
  • the ratio in the HSLT mode is determined by the number of volume chambers which don't recirculate (such that the "ratio" in the HSLT mode is the total number of volume chambers divided by the number of volume chambers which are "active", i.e., don't recirculate).
  • the shift between the low speed and high speed modes has, in many cases, occurred fairly abruptly and the prior art design has effectively dictated that operation of the motor can occur in only the low speed and high speed modes.
  • control of flow to and from all of the recirculating volume chambers is controlled by a single control valve spool, such that typically, the change (shift) between the LSHT and HSLT modes will occur simultaneously for all of the recirculating volume chambers.
  • a fluid pressure operated device comprising housing means defining a fluid inlet port and a fluid outlet port.
  • a fluid pressure displacement mechanism is associated with the housing means and includes an internally-toothed ring member and an externally-toothed star member eccentrically disposed within the ring member.
  • the ring member and the star member have relative orbital and rotational movement, and inter-engage to define a plurality of expanding and contracting fluid volume chambers in response to the orbital and rotational movement.
  • a motor valve means cooperates with the housing means to provide fluid communication between the fluid inlet port and the expanding volume chambers and between the contracting volume chambers and the fluid outlet port.
  • the motor valve means comprises a stationary valve member fixed to be non-rotatable relative to the housing means, and a moveable valve member operable to move relative to the stationary valve member in synchronism with one of the orbital and rotational movements.
  • the stationary valve member defines a plurality N of stationary valve passages, each of the stationary valve passages including an upstream passage portion adapted for commutating fluid communication with the moveable valve member, and further including a downstream passage portion in continuous fluid communication with one of the plurality N of fluid volume chambers.
  • the upstream passage portion and the downstream passage portion are in direct, relatively unrestricted, continuous fluid communication.
  • the improved fluid pressure operated device is characterized by, in a plurality M of the stationary valve passages, the upstream and the downstream passage portions are blocked from direct fluid communication.
  • a plurality M of control valve members is provided, each operably associated with the stationary valve member, and with one of the plurality M of the stationary valve passages.
  • Each of the control valve members is operable in a first position to provide relatively unrestricted fluid communication between each upstream passage portion and its respective downstream passage portion, and operable in a second position to block fluid communication between each upstream passage portion and its respective downstream passage portion.
  • FIG. 1 is an axial cross-section of a low-speed, high-torque gerotor motor made in accordance with the teachings of the present invention.
  • FIG. 2 is a transverse cross-section taken on line 2-2 of FIG. 1, and on a somewhat larger scale than FIG. 1.
  • FIG. 3 is a transverse cross-section taken on line 3-3 of FIG. 1, and on a somewhat larger scale than FIG. 1.
  • FIG. 4 is a transverse cross-section taken on line 4-4 of FIG. 1, and on a somewhat larger scale than FIG. 1.
  • FIG. 5 is a transverse cross-section taken on line 5-5 of FIG. 1, and on a somewhat larger scale than FIG. 1.
  • FIG. 6 is a transverse cross-section through the control valve plate, taken on line 6-6 of FIG. 1, and on a somewhat larger scale than FIG. 1.
  • FIG. 1 illustrates a valve-in-star (VIS) type of low speed, high torque (LSHT) motor, made generally in accordance with the above-incorporated patent, and in accordance with the above-incorporated application, and also, in accordance with U.S. Patent No. 5,211,551, also assigned to the assignee of the present invention, and incorporated herein by reference.
  • VIS valve-in-star
  • LSHT low speed, high torque
  • the VIS motor shown in FIG. 1 comprises a plurality of sections secured together such as by a plurality of bolts 11, only one of which is shown in FIG. 1, but all of which are shown in FIGS. 2 through 6.
  • the motor includes an end cap 13, a spacer plate 15, a shifter plate 17 (which may also be referred to as a "selector plate”), a stationary valve plate 19, a gerotor gear set, generally designated 21, a balancing plate assembly 23 and a flange member 25.
  • the gerotor gear set 21 is well known in the art, is shown and described in greater detail in the above-incorporated patents, and therefore will be described only briefly herein.
  • the gear set 21 is preferably a Geroler® gear set comprising an internally toothed ring member 27 defining a plurality of generally semicylindrical openings, with a cylindrical roller member 29 disposed in each of the openings, and serving as the internal teeth of the ring member 27.
  • Eccentrically disposed within the ring member 27 is an externally-toothed star member 31, typically having one less external tooth than the number of internal teeth or rollers 29, thus permitting the star member 31 to orbit and rotate relative to the ring member 27.
  • each volume chamber is in a state of "transition", between expanding and contracting, twice during each orbit of the star 31, and in FIG. 2, those volume chambers in transition are merely designated "33". In the subject embodiment, and by way of example only, there is a total often volume chambers 33.
  • the star 31 defines a plurality of straight, internal splines which are in engagement with a set of external, crowned splines 35, formed on one end of a main drive shaft 37. Disposed at the opposite end of the shaft 37 is another set of external, crowned splines 39, adapted to be in engagement with another set of straight, internal splines defined by some form of rotary output member, such as a shaft or wheel hub (not shown).
  • the star 31 in the subject embodiment, comprises an assembly of two separate parts, including a main star portion 41, which includes the external teeth, and an insert or plug 43 (the relationship therebetween being best shown in FIG. 1).
  • the main portion 41 and the insert 43 cooperate to define the various fluid zones, passages, and ports which will be described subsequently.
  • the star member 31 defines a central manifold zone 45, defined by an end surface 47 of the star 31, the end surface 47 being disposed in sliding, sealing engagement with an adjacent surface 49 (see FIGS. 1 and 6) of the stationary valve plate 19.
  • the end surface 47 of the star 31 defines a set of fluid ports 51, each of which is in continuous fluid communication with the manifold zone 45 by means of a fluid passage 53 (see also FIG. 1) defined by the insert 43.
  • the end surface 47 further defines a set of fluid ports 55 which are arranged alternately with the fluid ports 51, each of the fluid ports 55 including a portion 57 which extends radially inward, about halfway to the manifold zone 45.
  • the portions 57 together define an "outer" manifold zone, surrounding the inner or central manifold zone 45.
  • the end cap 13 includes a fluid inlet port 59 and a fluid outlet port 61, although those skilled in the art will recognize that most motors of the type to which the invention relates are meant to be "bi-directional" in operation, such that the ports may be reversed.
  • the end cap 13 defines an annular chamber 63 which is in open, continuous fluid communication with the inlet port 59.
  • the end cap 13 also defines a cylindrical chamber 65 which is in open, continuous fluid communication with the outlet port 61.
  • annular chamber 67 (also referred to hereinafter as the "recirculation region” or “recirculation chamber”), which is also in continuous, open fluid communication with whichever of the ports 59 or 61 contains high pressure, which, as the motor has been described herein is the inlet port 59.
  • the annular chamber 67 communicates with either the annular chamber 63 or the chamber 65 by means of a passage and shuttle valve arrangement, not shown herein, which are well known to those skilled in the art, the details of which are not essential features of the present invention. It is considered a desirable feature of the present invention for the annular chamber 67 to be in continuous fluid communication with a source of relatively high pressure fluid, such as the motor inlet port 59, for reasons which are explained in greater detail in the above-incorporated application.
  • the fluid port 59 is the inlet port, containing high pressure, which is then communicated into the annular chamber 63, and from there, through openings in the spacer plate 15 to a series of bores 69 defined by the shifter plate 17 (see FIGS. 4, 5 and 6).
  • the stationary valve plate 19 defines a central opening 71, which is in open communication with the cylindrical chamber 65.
  • the surface 49 of the stationary valve plate 19 also defines an annular groove 73, and in communication therewith, a series of openings 75, each of which is in fluid communication with one of the bores 69.
  • the stationary valve plate would, in a conventional VIS motor be either immediately adjacent the end cap 13, or may even be formed integrally with the end cap.
  • the stationary valve plate 19 is, in the present invention, separated from the end cap 13 by the spacer plate 15 and the shifter plate 17, in order to accomplish the multiple speed valving of the invention.
  • the stationary valve plate 19 defines a plurality of stationary valve passages 77, also referred to in the art as "timing slots".
  • each of the stationary valve passages 77 would typically comprise a radially-oriented slot, each of which would be disposed in continuous, open fluid communication with an adjacent one of the volume chambers, either an expanding volume chamber 33E, or a contracting volume chamber 33C.
  • the valve passages 77 are disposed in a generally annular pattern which is concentric relative to the central opening 71. If the stationary valve plate 19 were made in accordance with conventional VIS motor teachings, there would be ten of the valve passages 77, one for each volume chamber 33.
  • the stationary valve passages 77 there are five of the stationary valve passages 77 and five other, different stationary valve passages, generally designated 79A, 79B, 79C, 79D and 79E.
  • the stationary valve passages 79A through E differ from the conventional valve passages 77 in a manner to be described.
  • passages 77 and passages 79 can, within the scope of the invention, vary somewhat, although the total number of passages 77 and 79 together will be determined by the particular gerotor gear set utilized.
  • the roller gerotor gear set 21 is a "nine-ten" gerotor, i.e., the ring member 27 has ten internal teeth (rollers 29) and the star member 31 has nine external teeth. Therefore, there are a total often volume chambers (33,33E, and 33C), and for each volume chamber, there is provided either a passage 77 or a passage 79 (A through E), thus a total often passages.
  • each of the valve passages 77 is in commutating communication with the fluid ports 51 and 55, whereas the radially outer portion of each valve passage 77 is in permanent, continuous communication with the respective volume chamber 33 (or 33E or 33C).
  • communication from one of the fluid ports 51 or 55 to the adjacent volume chamber 33 is effected through the radially oriented passage 77 in which the radially inner portion and the radially outer portion are in direct, open communication (as may be seen in FIG. 3).
  • each of the valve passages 79A through 79E there is a radially inner (upstream) portion 81 and a separate, radially outer (downstream) portion 83. Therefore, in accordance with an important aspect of the present invention, in each of the stationary valve passages 79A through 79E, the radially inner portion 81 and the radially outer portion 83 are not in direct, open fluid communication. Instead, the radially inner and outer portions are in communication with each other through the control valving in the shifter plate 17, in the normal, LSHT mode, but are blocked from communication with each other by the valving in the HSLT mode. The two modes will be described in greater detail subsequently, in connection with the description of the operation of the invention.
  • FIGS. 4, 5 and 6 the shifter plate 17, and the control valving of the present invention, will be described.
  • FIG. 5 is looking toward the left in FIG. 1, i.e., toward the end cap 13
  • FIGS. 4 and 6 are views looking to the right in FIG. 1, i.e., toward the shaft 37.
  • the shifter plate 17 defines a central opening 85 which provides open communication between the cylindrical chamber 65 and the central opening 71 of the stationary valve plate 19 (FIG. 3).
  • the shifter plate 17 also defines an annular groove 87 (see also FIG. 1), and in communication therewith is a series of bores 89, the function of which will be described in greater detail subsequently.
  • the shifter plate 17 defines a plurality of recirculation bores 91, each of which is in open fluid communication with the annular chamber (recirculation chamber) 67.
  • FIGS. 3 and 5 are views taken in the same direction, and therefore, at locations corresponding to the stationary valve passages 79A through E, the shifter plate 17 defines port arrangements 93A through 93E.
  • Each of the port arrangements 93A through 93E comprises a radially inner recess 95 which is in open communication with an adjacent upstream portion 81 defined by the stationary valve plate 19.
  • each port arrangement 93A through 93E includes a radially outer recess 97, which is generally L-shaped, and includes an outer, tangentially-oriented portion which is in open communication with each of the downstream portions 83 defined by the stationary valve plate 19.
  • the shifter plate 17 defines a plurality of radially-extending bores 99, each of which is sealed at its radially outer end by a threaded plug 101 (shown only in FIG. 1).
  • a valve spool 103 Disposed within each bore 99 is a valve spool 103 including an inner land 105 and an outer land 107.
  • a reduced diameter bore 109 also referred to hereinafter as a "shift pressure chamber”
  • Each of the recirculation bores 91 shown in FIG. 4 extends axially part way through the shifter plate 17 and intersects its respective bore 99 at a location which, in FIG. 6 is covered by the outer land 107.
  • each of the radially inner recesses 95 is in communication with a short axially extending bore 111 which opens into the radially extending bore 99 as shown in FIG. 6.
  • each of the radially outer recesses 97 is in communication with a short axially extending bore 113 which opens into the radially extending bore 99 as shown in FIG. 6.
  • Each of the valve spools 103 is biased radially inward to the position shown in FIG. 6 by a compression spring 115, which has its radially outer end seated against the threaded plug 101.
  • the valve spools 103 will all be biased radially inward to the position shown in FIG. 6, in which the bores 111 and 113 are in open communication with each other, and therefore, the inner and outer recesses 95 and 97 are in open communication with each other.
  • each of the stationary valve passages 79A through E are also in open communication with each other, such that each of the stationary valve passages 79A through 79E functions in substantially the same manner as each of the conventional stationary valve passages 77.
  • the gerotor motor will operate in the normal, low-speed, high-torque mode.
  • volume chambers are no longer in communication with the fluid inlet port 59 or the fluid outlet port 61, by means of the commutating valving. Instead, those five "recirculating" volume chambers are each in communication with the pressurized recirculation chamber 67, by means of the recirculation bores 91, the bores 113, the radially outer recesses 97, and the downstream portions 83.
  • the five remaining volume chambers i.e., those in communication by means of the stationary valve passages 77
  • one of the objects of the invention is to have true multi speed capability, i.e., a minimum (1.0:1) speed ratio (LSHT), a maximum (2.0:1) speed ratio (HSLT), and at least one speed ratio in between the minimum and maximum ratios.
  • the present invention by valving each of the recirculating volume chambers separately, makes it possible to have less than five of the volume chambers recirculate fluid. For example, in the subject embodiment, if three of the valve spools 103 were shift radially outward by pressure in the respective bores 109, but the other two valve spools 103 remained in the radially inward position of FIG.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
EP01112161A 2000-05-25 2001-05-17 Moteur hydraulique du type gerotor Withdrawn EP1158165A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US57916400A 2000-05-25 2000-05-25
US579164 2000-05-25

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EP1158165A2 true EP1158165A2 (fr) 2001-11-28
EP1158165A3 EP1158165A3 (fr) 2001-12-12

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EP01112161A Withdrawn EP1158165A3 (fr) 2000-05-25 2001-05-17 Moteur hydraulique du type gerotor

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EP (1) EP1158165A3 (fr)
JP (1) JP2001336472A (fr)
CN (1) CN1326048A (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
JP5734007B2 (ja) * 2011-02-09 2015-06-10 豊興工業株式会社 回転式液圧装置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4480971A (en) 1983-01-17 1984-11-06 Eaton Corporation Two-speed gerotor motor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4767292A (en) * 1987-07-20 1988-08-30 Trw Inc. Electrical commutation apparatus
US5137438A (en) * 1991-04-18 1992-08-11 Trw Inc. Multiple speed fluid motor
US5624248A (en) * 1996-02-21 1997-04-29 Eaton Corporation Gerotor motor and improved balancing plate seal therefor
US6099280A (en) * 1999-04-14 2000-08-08 Eaton Corporation Two speed geroter motor with external pocket recirculation

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4480971A (en) 1983-01-17 1984-11-06 Eaton Corporation Two-speed gerotor motor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11493018B2 (en) 2020-01-03 2022-11-08 Parker-Hannifin Corporation Hydraulic motor with anti-cogging features

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Publication number Publication date
JP2001336472A (ja) 2001-12-07
EP1158165A3 (fr) 2001-12-12
CN1326048A (zh) 2001-12-12

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