EP1070847A2 - Hydraulischer Gerotor-Motor und Feststellbremse - Google Patents

Hydraulischer Gerotor-Motor und Feststellbremse Download PDF

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Publication number
EP1070847A2
EP1070847A2 EP00115130A EP00115130A EP1070847A2 EP 1070847 A2 EP1070847 A2 EP 1070847A2 EP 00115130 A EP00115130 A EP 00115130A EP 00115130 A EP00115130 A EP 00115130A EP 1070847 A2 EP1070847 A2 EP 1070847A2
Authority
EP
European Patent Office
Prior art keywords
actuation piston
rotary fluid
fluid pressure
pressure device
pressure chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP00115130A
Other languages
English (en)
French (fr)
Inventor
Jennifer Jean Szymanski
Michael Jerome Gust
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 EP1070847A2 publication Critical patent/EP1070847A2/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0084—Brakes, braking assemblies
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • 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, and more particularly, to such devices of the type including a fluid displacement mechanism, and even more particularly, to such devices in which the fluid displacement mechanism comprises a gerotor gear set.
  • the present invention may be included in a rotary fluid pressure device being utilized as a pump, it is primarily adapted for use in a motor, and especially for use in a low-speed, high-torque motor, and will be described in connection therewith. Also, even though the present invention may be utilized in axial piston motors, radial cam lobe motors, and other types of motors, it is especially suited for use in gerotor motors, and will be described in connection therewith.
  • the motor In many vehicle applications for low-speed, high-torque gerotor motors, it is desirable for the motor to have some sort of parking brake or parking lock, the term “lock” being preferred in some instances because it is intended that the parking lock be engaged only after the vehicle is stopped. In other words, such parking lock devices are not intended to be dynamic brakes, which would be engaged while the vehicle is moving, to bring the vehicle to a stop.
  • the term “brake” will generally be used hereinafter to mean and include both brakes and locks. The term “brake” is somewhat preferred to distinguish from a device which would operate either fully engaged or fully disengaged. In fact, the device of the present invention provides at least two different, distinct, engaged conditions.
  • gerotor motor One of the trends associated with the use of low-speed, high-torque gerotor motors is for the motor to be designed to operate at higher pressures, and therefore, at higher output torques.
  • gerotor motor which is especially adapted for higher pressures and torques is the VIS series of motors, sold commercially by the assignee of the present invention, such motors being illustrated and described in U.S. Patent Nos. 4,741,681 and 5,211,551, both of which are assigned to the assignee of the present invention and are incorporated herein by reference.
  • the substantially higher motor output torques, coupled with the friction disc pack being conveniently associated with the output shaft, would result in a brake assembly having a torque capacity requirement which may make the brake assembly not feasible economically in many vehicle applications.
  • the brake discs are provided with some sort of friction material which, while effective in increasing the braking torque, also adds further to the cost of the brake discs.
  • a rotary fluid pressure device of the type including housing means, a rotary fluid displacement mechanism, and an output member having a movement corresponding to an output movement of the device.
  • a first brake disc (which may also be referred to as a "stator") is fixed relative to the housing means, and a second brake disc is fixed to rotate with the output member, the first and second brake discs being disposed for operable engagement by means of an actuation piston to brake rotation of the output member relative to the housing means.
  • the actuation piston is moveable between an engaged position and a disengaged position, and spring means biases the actuation piston toward the engaged position.
  • the improved rotary fluid pressure device is characterized by the actuation piston cooperating with the housing means to define a first pressure chamber and a second pressure chamber disposed on axially opposite sides of the actuation piston.
  • the spring biasing means is disposed in the first pressure chamber.
  • a first source of pressurized fluid is in fluid communication with the first pressure chamber and is selectively operable to apply a biasing force to the actuation piston, in addition to the spring biasing means, tending to move the actuation piston toward the engaged position.
  • a second source of pressurized fluid is in fluid communication with the second pressure chamber and selectively operable to apply a biasing force to the actuation piston, tending to move the actuation piston toward the disengaged position.
  • FIG. 1 is an axial cross-section of a low-speed, high-torque gerotor motor of the type with which the brake assembly of the present invention is especially advantageous.
  • the motor shown in FIG. 1 may be of the general construction illustrated and described in above-incorporated U.S. 5,211,551.
  • the motor assembly shown in FIG. 1 comprises a modular motor assembly, generally designated 11, and a forward bearing package, generally designated 13.
  • the brake assembly of the present invention is disposed within the forward bearing package 13.
  • the modular motor 11 which will be described only briefly herein in view of the incorporation of the above-cited patent, includes an end cap 15, a stationary valve plate 17, a gerotor gear seat, generally designated 19, and a flange member 21.
  • the elements 15 through 21 are held in tight sealing engagement by means of a plurality of bolts 23, each of the bolts 23 including a head 27 disposed in engagement with a forward surface 29 of the flange member 21.
  • the gerotor gear set 19 may be of the type well known in the art, and includes an internally-toothed ring member 31 defining a plurality of generally semi-cylindrical openings, with a cylindrical roller member 33 being disposed in each of the openings, and serving as the internal teeth of the ring member 31.
  • Eccentrically disposed within the ring member 31 is an externally-toothed star member 35, which typically has one less external tooth than the number of the internal teeth 33, thus permitting the star 35 to orbit and rotate relative to the ring 31, as is well known to those skilled in the art.
  • the orbital and rotational movement of the star 35 within the ring 31 defines a plurality of expanding and contracting fluid volume chambers, not shown herein, also well known to those skilled in the art.
  • the forward bearing package 13 includes a bearing housing assembly 41, which, in the subject embodiment, comprises two separate housing members joined together by any suitable means, not shown herein.
  • the bearing housing assembly 41 is provided with a pair of tapered roller bearing sets 43 and 45 which receive, and rotatably support the output shaft 39.
  • the bearing housing 41 defines a disc chamber 49, and disposed within the disc chamber 49 is a plurality of externally splined friction discs 51, which are in splined engagement with the bearing housing 41, and a plurality of internally splined friction discs 53 which are in splined engagement with a set of external splines 55 defined by the output shaft 39. It should be understood by those skilled in the art from a reading and understanding of this specification that the particular construction details of the friction discs 51 and 53 are not essential features of the invention.
  • brake disc will be understood to mean and include any sort of members which, upon frictional engagement, are effective to achieve a braking torque of the output shaft 39 relative to the stationary part of the motor, e.g., the bearing housing assembly 41.
  • the motor typically includes a case drain region which, in the subject embodiment, comprises the generally cylindrical space 57 (see FIG. 1) surrounding the main drive shaft 37. It is into this case drain region 57 that leakage fluid from the gerotor gear set 19 flows and the fluid in the case drain region 57 serves various lubrication functions, such as lubricating the spline connections of the shaft 37.
  • the disc chamber 49 is in open fluid communication with the case drain region 57, and as is typical, both the chamber 49 and the case drain region 57 are maintained at relatively low fluid pressure, for example, in the range of about 0 to 200 psi.
  • a generally annular actuation piston 59 disposed within the bearing housing 41 and including a radially outer seal member 61 and a radially inner seal member 63.
  • the outer seal member 61 is in sealing engagement with an internal, generally cylindrical surface 62 of the bearing housing 41, while the inner seal member 63 is in sealing engagement with a cylindrical outer surface 64 of a cylindrical, axially extending portion 65 of the bearing housing 41.
  • a separation member 67 Disposed adjacent the actuation piston 59 is a separation member 67, the primary function of which is to seal or separate the low pressure disc chamber 49 from the relatively higher pressure chamber in which the actuation piston 59 is disposed.
  • the separation member 67 has an outside diameter and associated therewith, a seal member 68 which is in sealing engagement with an inside surface of the bearing housing 41.
  • the separation member 67 also has an inside diameter 69 defining an opening, the opening also being referred to hereinafter by the reference numeral "69".
  • a seal member 70 Associated with the inside diameter 69 is a seal member 70 which is in sealing engagement with a cylindrical, outer surface of a generally cylindrical, axially extending engagement portion 71.
  • the engagement portion 71 is formed integrally with the actuation piston 59 and is dimensioned such that, with the actuation piston 59 in the disengaged position shown in FIG. 2, the engagement portion 71 may be touching the adjacent friction disc 51, but is not applying any substantial biasing force to the pack of friction discs 51 and 53.
  • the actuation piston 59 cooperates with the bearing housing 41 and the adjacent separation member 67 to define a first pressure chamber 73 and a second pressure chamber 75.
  • the bearing housing 41 defines a fluid port 77 and a fluid port 79.
  • the first pressure chamber 73 is in communication, by means of the fluid port 77, with a first source 81 of pressurized fluid, while the second pressure chamber 75 is in communication, by means of the fluid port 79, with a second source 83 of pressurized fluid.
  • the sources of pressurized fluid 81 and 83 are illustrated herein schematically as each comprising a fixed displacement pump and a simple solenoid valve.
  • each of the valves shown in FIG. 2 includes a flow "blocked" position, whereas it would be likely that the valve, when not energized, would be spring biased to a position in which the valve would drain the respective port and chamber.
  • the valves shown in FIG. 2 each merely have two discrete positions, it would be apparent to those skilled in the art that the valves could be of the "infinitely variable" type, operable to modulate the fluid pressure in the respective chamber 73 or 75, thus gradually applying or releasing the brake.
  • the brake assembly 47 of the present invention is generally of the "spring-applied, pressure-released" type. Therefore, disposed within the first pressure chamber 73 is a set of Belleville washers (or springs) 85, tending to bias the actuation piston 59 from the disengaged position shown in FIG. 2 toward an engaged position. As is understood by those skilled in the brake and clutch art, there is frequently very little difference apparent between the disengaged and engaged positions of a set of friction discs. For example, in the disengaged position of FIG.
  • the friction discs 51 and 53 may actually be in contact with each other, but without sufficient actuation or biasing force applied to the discs, the contact of the discs does not generate any substantial braking torque.
  • the actuation piston 59 is maintained in the disengaged position of FIG. 2 by draining pressurized fluid from the first pressure chamber 73 and communicating pressurized fluid to the second pressure chamber 75, thus exerting sufficient biasing force on the actuation piston 59 to bias it to the left in FIG. 2 until the piston 59 engages a shoulder surface 87 defined by the bearing housing 41.
  • both of the pressure chambers 73 and 75 are drained, such that the only biasing force on the actuation piston 59 is that of the Belleville washers 85, thus moving the actuation piston 59 slightly to the right in FIG. 2 such that the engagement portion 71 applies an engagement load to the friction discs 51 and 53.
  • the result is sufficient frictional engagement of the discs 51 and 53 to provide a predetermined, standard level of braking torque applied to the output shaft 39.
  • pressurized fluid is communicated to the first pressure chamber 73, while the second pressure chamber 75 is drained, such that the actuation piston 59 is now biased by both the Belleville washers 85 and the pressurized fluid in the chamber 73.
  • the Belleville washers 85 and the dimensions of the various other elements of the brake assembly 47, in order to achieve the desired levels of braking torque.
  • the greater level of braking torque would correspond approximately to the maximum, continuous torque rating of the motor, whereas the normal braking torque would be, by way of example only, that torque required to prevent a fully loaded vehicle from rolling downhill on a twenty-five degree slope.
  • FIG. 3 there is illustrated an alternative embodiment of the invention, in which the same, or similar elements, bear like numerals, and new or greatly modified elements bear reference numerals in excess of "90".
  • an actuation piston 91 which is generally similar to the piston 59 in the main embodiment, but differs from the piston 59 in that the piston 91 moves rearwardly (to the left in FIG. 3) whenever the brake is being applied, and moves forwardly (to the right in FIG. 3) whenever the brake is being released.
  • the flange member 21 includes a preferably integral separation portion 93.
  • the separation portion 93 carries the seal members 68 and 70, and serves the function of separating the second pressure chamber 75 from the chamber containing the friction discs 51 and 53, which is open to the case drain region 57, as was explained previously.
  • the FIG. 3 embodiment is substantially the same as the main embodiment, except for the opposite direction of movement of the actuation piston 91.
  • the pressure chamber 73 is drained, while the pressure chamber 75 receives high pressure, thus moving the piston 91 to the right in FIG. 3, to a disengaged condition.
  • both pressure chambers 73 and 75 are drained, and the Belleville washer 85 provides the only apply force to the piston 91.
  • the pressure chamber 73 is pressurized, while the pressure chamber 75 is drained, so that the piston 91 is biased toward the left in FIG. 3, to an engaged condition, by both the washer 85 and the pressure in the chamber 73.
  • FIG. 3 embodiment permits the entire forward bearing package and brake assembly to be substantially smaller and more compact than does the main embodiment.
  • the FIG. 3 embodiment requires fewer parts, thus having at least the potential to be somewhat less expensive to manufacture.
EP00115130A 1999-07-22 2000-07-12 Hydraulischer Gerotor-Motor und Feststellbremse Withdrawn EP1070847A2 (de)

Applications Claiming Priority (2)

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US35900199A 1999-07-22 1999-07-22
US359001 1999-07-22

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EP1070847A2 true EP1070847A2 (de) 2001-01-24

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JP (1) JP2001065607A (de)
KR (1) KR20010066936A (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002059482A1 (en) * 2001-01-26 2002-08-01 M+S Hydraulic An integral unit of a hydraulic brake/gerotor hydraulic motor a nd a control valve block
WO2004035438A1 (en) * 2002-10-21 2004-04-29 Sauer-Danfoss Aps Brake appliance for gerotor motors
EP3299656A1 (de) * 2016-09-23 2018-03-28 Poclain Hydraulics Industrie Verbessertes bremssystem für hydraulische maschine
EP3401540A1 (de) * 2017-04-13 2018-11-14 Eaton Intelligent Power Limited Bremse für einen hydraulikmotor
US10473166B2 (en) 2016-02-23 2019-11-12 Mazda Motor Corporation Frictional engagement element and automatic transmission
EP3587198A1 (de) * 2018-06-28 2020-01-01 J.C. Bamford Excavators Ltd Betätigungsmechanismus für eine mehrscheibenbremse
FR3094419A1 (fr) * 2019-03-28 2020-10-02 Poclain Hydraulics Industrie Machine hydraulique comprenant un frein perfectionné.

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100555683B1 (ko) * 2003-01-27 2006-03-03 조만수 생약 제재를 주원료로 한 건강보조 음료 및 그 제조방법
JP2008281102A (ja) * 2007-05-10 2008-11-20 Yamaha Motor Co Ltd 車両制動装置
JP5132251B2 (ja) * 2007-10-24 2013-01-30 株式会社小松製作所 ブレーキ装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3616882A (en) 1970-02-05 1971-11-02 Trw Inc Hydraulic motor-pump assembly with built-in brake
US4741681A (en) 1986-05-01 1988-05-03 Bernstrom Marvin L Gerotor motor with valving in gerotor star
US4981423A (en) 1989-10-03 1991-01-01 Trw Inc. Hydraulic motor with wobble-stick and brake assembly
US5211551A (en) 1992-09-10 1993-05-18 Eaton Corporation Modular motor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3616882A (en) 1970-02-05 1971-11-02 Trw Inc Hydraulic motor-pump assembly with built-in brake
US4741681A (en) 1986-05-01 1988-05-03 Bernstrom Marvin L Gerotor motor with valving in gerotor star
US4981423A (en) 1989-10-03 1991-01-01 Trw Inc. Hydraulic motor with wobble-stick and brake assembly
US5211551A (en) 1992-09-10 1993-05-18 Eaton Corporation Modular motor

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002059482A1 (en) * 2001-01-26 2002-08-01 M+S Hydraulic An integral unit of a hydraulic brake/gerotor hydraulic motor a nd a control valve block
WO2004035438A1 (en) * 2002-10-21 2004-04-29 Sauer-Danfoss Aps Brake appliance for gerotor motors
US10473166B2 (en) 2016-02-23 2019-11-12 Mazda Motor Corporation Frictional engagement element and automatic transmission
US10364792B2 (en) 2016-09-23 2019-07-30 Poclain Hydraulics Industrie Braking system for a hydraulic machine
CN107869534A (zh) * 2016-09-23 2018-04-03 波克兰液压工业设备公司 一种用于液压机的改进的制动系统
FR3056662A1 (fr) * 2016-09-23 2018-03-30 Poclain Hydraulics Ind Systeme de freinage ameliore pour machine hydraulique
EP3299656A1 (de) * 2016-09-23 2018-03-28 Poclain Hydraulics Industrie Verbessertes bremssystem für hydraulische maschine
CN107869534B (zh) * 2016-09-23 2021-06-29 波克兰液压工业设备公司 一种用于液压机的改进的制动系统
EP3401540A1 (de) * 2017-04-13 2018-11-14 Eaton Intelligent Power Limited Bremse für einen hydraulikmotor
US10781816B2 (en) 2017-04-13 2020-09-22 Eaton Intelligent Power Limited Hydraulic motor brake
EP3587198A1 (de) * 2018-06-28 2020-01-01 J.C. Bamford Excavators Ltd Betätigungsmechanismus für eine mehrscheibenbremse
US11287003B2 (en) 2018-06-28 2022-03-29 J.C. Bamford Excavators Limited Integral unit for service brake and fail-safe park brake
FR3094419A1 (fr) * 2019-03-28 2020-10-02 Poclain Hydraulics Industrie Machine hydraulique comprenant un frein perfectionné.

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Publication number Publication date
KR20010066936A (ko) 2001-07-11
JP2001065607A (ja) 2001-03-16

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