EP0870922A1 - Bremse für einen Innenzahnradmotor - Google Patents

Bremse für einen Innenzahnradmotor Download PDF

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Publication number
EP0870922A1
EP0870922A1 EP98105403A EP98105403A EP0870922A1 EP 0870922 A1 EP0870922 A1 EP 0870922A1 EP 98105403 A EP98105403 A EP 98105403A EP 98105403 A EP98105403 A EP 98105403A EP 0870922 A1 EP0870922 A1 EP 0870922A1
Authority
EP
European Patent Office
Prior art keywords
brake disc
fluid pressure
disposed
endcap
relative
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Withdrawn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
EP98105403A
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English (en)
French (fr)
Inventor
Wayne Bernard Wenker
Sohan Lal Uppal
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 EP0870922A1 publication Critical patent/EP0870922A1/de
Withdrawn legal-status Critical Current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
    • 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
    • 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

Definitions

  • the present invention relates to rotary fluid pressure devices, and more particularly, to such devices of the type including a fluid displacement mechanism which comprises a gerotor gear set.
  • the present invention may be included in a gerotor type device being utilized as a pump, it is especially adapted for use in a low-speed, high-torque gerotor motor, and will be described in connection therewith.
  • gerotor motors made and sold commercially both by the assignee of the present invention as well as by others, have had the motor valving disposed "forwardly" of the gerotor gear set (i.e., toward the output shaft end of the motor), thus having nothing disposed “rearwardly” of the gerotor gear set, except for an endcap.
  • the present invention is not limited to gerotor motors of this type, although it is especially adapted for use with gerotor motors of this type, and will be illustrated and 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, and in certain vehicle applications, it is desirable for the motor to have some sort of dynamic brake which can be applied while the vehicle is still moving, to bring the vehicle to a stop.
  • dynamic brake means a brake having dynamic capabilities, i.e., one which can begin to be applied while the vehicle is still moving, but “dynamic” does not mean a true service-type brake which would be applied when the vehicle is traveling at its normal operating speed.
  • a rotary fluid pressure device of the type including housing means defining a fluid inlet port and a fluid outlet port.
  • the device includes a rotary fluid displacement mechanism including an internally toothed ring member and an externally toothed star member eccentrically disposed within the ring member for orbital movement relative thereto. Either the ring member or the star member has rotational movement, and the teeth of the ring member and the star member interengage to define expanding and contracting fluid volume chambers in response to the orbital and rotational movements.
  • a valve means cooperates with the housing means to provide fluid communication from the inlet port to the expanding volume chambers, and from the contracting volume chambers to the outlet port.
  • the device includes output means and means operable to transmit torque from the member having rotational movement to the output means.
  • An endcap is disposed rearwardly of the fluid displacement mechanism.
  • the improved rotary fluid pressure device is characterized by the endcap defining an internal chamber.
  • a first means defines at least a first braking surface fixed to be non-rotatable relative to the endcap.
  • a second means defines at least a second braking surface fixed to be non-rotatable relative to one of the star member and the ring member.
  • a lock piston is disposed in the internal chamber, and is movable between a retracted position and an applied position in which the lock piston causes engagement of the first and second braking surfaces to retard movement of the one of the star member and the ring member.
  • FIG. 1 is an axial cross-section of a gerotor motor including the dynamic brake mechanism of the present invention, in its engaged position.
  • FIG. 2 is a transverse cross-section, taken on line 2-2 of FIG. 1, illustrating one aspect of the present invention.
  • FIG. 3 is a transverse cross-section, taken on line 3-3 of FIG. 1, illustrating another aspect of the present invention.
  • FIG. 4 is a fragmentary, axial cross section, similar to FIG. 1, illustrating an alternative embodiment of the present invention.
  • FIG. 1 is an axial cross-section of a low-speed, high-torque gerotor motor of the type with which the dynamic brake mechanism of the present invention is especially advantageous.
  • the gerotor motor shown in FIG. 1 may be of the general type illustrated and described in U.S. Patent No. 4,592,704, assigned to the assignee of the present invention and incorporated herein by reference.
  • the gerotor motor of FIG. 1 comprises a valve housing section 11, and a fluid energy-translating displacement mechanism, generally designated 15, which, in the subject embodiment, is a roller gerotor gear set.
  • the motor includes an endcap assembly 17, held in tight sealing engagement with the valve housing section 11 by means of a plurality of bolts 19, the endcap assembly 17 including an endcap member 21 disposed immediately adjacent the gerotor gear set 15, and an endcap member 23, held in fluid sealing engagement with the endcap member 21 by means of the plurality of bolts 19.
  • the endcap assembly 17 will be described in greater detail subsequently.
  • the valve housing section 11 includes a fluid inlet port 25, and a fluid outlet port 27, shown only schematically in FIG. 1. It is understood by those skilled in the art that the ports 25 and 27 may be reversed, thus reversing the direction of operation of the motor.
  • the gerotor gear set 15 includes an internally toothed ring member 29, through which the bolts 19 pass (only one of the bolts 19 being shown in FIG. 1), and an externally toothed star member 31.
  • the internal teeth of the ring member 29 comprise a plurality of cylindrical rollers 33, as is now well known in the art.
  • the teeth 33 of the ring 29 and the external teeth of the star 31 interengage to define a plurality of expanding volume chambers 35, and a plurality of contracting volume chambers 37, as is also well known in the art.
  • the valve housing section 11 defines a spool bore 39, and rotatably disposed therein is a spool valve 41. Formed integrally with the spool valve 41 is an output shaft 43, shown only fragmentarily in FIG. 1.
  • an axial passage 45 formed in the valve housing section 11. Each of the axial passages 45 communicates with the spool bore 39 through an opening 49.
  • the housing section 11 also defines fluid passages 25p and 27p, providing fluid communication between the spool bore 39 and the inlet port 25 and outlet port 27, respectively.
  • a main drive shaft 51 Disposed within the hollow, cylindrical spool valve 41 is a main drive shaft 51, commonly referred to as a dog bone shaft.
  • the spool valve 41 defines a set of straight internal splines 53, and the star 31 receives an insert member 54 which will be described in greater detail subsequently, but which defines a set of straight internal splines 55.
  • the drive shaft 51 includes a set of external crowned splines 57 in engagement with the internal splines 53, and a set of external crowned splines 59 in engagement with the internal splines 55.
  • the valve housing section 11 defines an annular groove 61 in continuous fluid communication with the inlet port 25, through the passage 25p, and defines an annular groove 63, which is in continuous fluid communication with the outlet port 27, through the passage 27p.
  • the spool valve 41 defines a plurality of axial slots 65 in communication with the annular groove 61, and a plurality of axial slots 67 in communication with the annular groove 63.
  • the axial slots 65 and 67 are also frequently referred to as feed slots or timing slots.
  • the axial slots 65 provide fluid communication between the annular groove 61 and the openings 49, disposed on one side of the line of eccentricity of the gerotor set 15, while the axial slots 67 provide fluid communication between the annular groove 63 and the openings 49, which are on the other side of the line of eccentricity.
  • the resulting commutating valve action between the axial slots 65 and 67 and the openings 49, as the spool valve 41 rotates, is well known in the art and will not be described further herein.
  • the endcap members 21 and 23 cooperate to define a relatively larger, rearward internal chamber 71, and a relatively smaller, forward internal chamber 73.
  • both of the chambers 71 and 73 are generally cylindrical.
  • a generally cylindrical lock piston 75 Disposed within the chamber 71 is a generally cylindrical lock piston 75, which includes an O-ring seal 77 disposed about its outer periphery and in sealing engagement with the internal surface of the chamber 71.
  • the lock piston 75 includes a forward, transverse surface 79 and a centrally disposed, generally cylindrical recess 81.
  • a brake disc pack Disposed immediately forward of the lock piston 75 is a brake disc pack, generally designated 89, which comprises a set of outer brake discs 91, and a set of inner brake discs 93. One disc of each of the sets is at least partly visible in FIG. 3.
  • the outer brake discs 91 are in engagement with the endcap member 21 by means of a plurality of tangs 95, which are received within mating, milled axial slots in the endcap member 21.
  • the discs 91 are non-rotatable relative to the endcap member 21, but are permitted to move axially relative thereto, in a manner common in the brake and clutch art.
  • the inner brake discs 93 are in engagement with a generally cylindrical disc mounting portion 97 of the insert member 54 by means of a set of splines 99.
  • the discs 93 are non-rotatable relative to the insert member 54, but are permitted to move axially relative thereto.
  • each of the outer brake discs 91 comprises a stamped steel disc, wherein each side of the disc serves as a friction or braking surface 101.
  • Each of the inner discs 93 preferably comprises a stamped steel disc as a substrate, to which a layer of friction material 103, such as paper or pyrolytic carbon, is bonded to each side to serve as a braking surface.
  • the endcap member 21 includes a forward wall portion 105 which is disposed immediately adjacent the gerotor gear set 15, thus sealing the rearward side of the volume chambers 35 and 37.
  • the wall portion 105 defines the forward internal chamber 73, and also defines an enlarged forward recess 107, the function of which will be described subsequently. It should be apparent that one purpose of the wall portion 105 is as a reaction member, whenever a load is applied to the brake disc pack 89 to achieve engagement thereof.
  • the insert member 54 includes an insert portion 109 which, as may best be seen in FIG. 2, is received within the star member 31, and is fixed to rotate therewith by means of a set of splines 111.
  • the insert portion 109 defines, about its inner periphery, the set of straight, internal splines 55 which are normally defined by the star member, in a conventional gerotor motor. Therefore, the insert member 54 orbits and rotates with the star member 31, and as a result, the disc mounting portion 97 and the inner brake discs 103 also orbit and rotate with the star member 31, and are always disposed eccentrically relative to the endcap member 21 and the outer discs 91.
  • the insert member 54 includes a shoulder portion disposed axially between the insert portion 109 and the disc mounting portion 97. The shoulder portion is disposed within the recess 107, such that the entire insert member 54 is thereby restrained in the axial direction.
  • the case drain region is generally the volume within the spool valve 41.
  • the disc mounting portion 97 defines an axial fluid passage 113 which permits fluid communication from the case drain region, through the passage 113, and into the recess 81.
  • the area of the recess 81 is selected, relative to the typical case drain pressure for the motor, such that, whenever the motor is operating and case pressure is present, the lock piston 75 is biased rearwardly, in opposition to the force of the Belleville washers 85 and 87.
  • the outer brake discs 91 and the inner brake discs 93 are "unloaded' or disengaged, thus permitting the insert member 54 and the star member 31 to orbit and rotate in a normal manner.
  • the disengagement of the brake disc pack 89 is controlled by case pressure which, in turn, is determined by controlling the return pressure, downstream of whichever of the ports 25 or 27 is the return port.
  • the spool valve 41 is provided with a pair of check valves 115 and 117 which permit communication of fluid from the case drain region to the annular grooves 61 and 63, respectively. Therefore, assuming that the port 25 is the inlet port and the port 27 is the return port, an increasing pressure in the return line, downstream of the port 27 will result in an increasing case pressure, which will be communicated through the axial passage 113 into the recess 81, building a force tending to bias the piston 75 to the right in FIG.
  • the return pressure is decreased (which may be done manually or “automatically” in response to some vehicle criteria such as speed, etc.) and case pressure decreases until the pressure in the recess 81 is overcome by the force of the Belleville washers 85 and 87.
  • the lock piston 75 is biased forwardly (to the left in FIG. 1), it begins to load or compress the disc pack 89, thus retarding the orbiting and rotating of the star member 31.
  • the case pressure required to disengage the brake disc pack 89 should be less than the "starting torque", i.e., the operating pressure in the motor required to initiate orbital and rotational movement of the star member 31, and rotation of the output shaft 43.
  • the motor could be provided with a separate signal line, for example, with a port being located in the end cap member 21 or the end cap member 23 and communicating with the recess 81. Then, the operator would control the release pressure in the recess 81 in a more direct manner, by controlling the pressure of the external signal. It should be understood by those skilled in the art that the specific method of controlling the release pressure is not an essential feature of the invention. All that is essential is that there be some means provided for releasing the brake disc pack 89.
  • each of the sets of discs 91 and 93 can be left out, with the axial space being filled by some sort of spacer member. In this way, only the amount of braking torque actually required will be provided, there will be a cost savings from the reduced number of friction discs, but no overall change in the design is needed.
  • FIG. 4 there is illustrated an alternative embodiment of the present invention, in which like elements bear like numerals and modified elements bear the same numerals, plus a prime mark, and new elements bear a reference numeral in excess of "120".
  • the primary difference in the embodiment of FIG. 4 is that it includes a gerotor gear set 15' which includes an internally toothed ring member 29', an externally toothed star member 31', and a plurality of rollers 33' which are all substantially longer, axially, than in the embodiment of FIG. 1.
  • the star member 31' defines the straight internal splines 55' in the conventional manner and, disposed axially adjacent thereto, there is an insert member 121.
  • the insert member 121 includes an externally splined insert portion 123, in splined engagement with the internal splines 55', and an externally splined disc mounting portion 125.
  • the portions 123 and 125 still define the axial fluid passage 113 (only a portion of which is shown in FIG. 4).
  • the insert member 121 will still orbit and rotate with the star member 31' in the same manner as in the FIG. 1 embodiment, causing the inner brake discs 93 to orbit and rotate relative to the outer brake discs 91.
  • the insert member 121 In order to prevent axial movement of the insert member 121, it may be desirable to press the splines of the portion 123 into the internal splines 55', or alternatively, to provide a snap ring or other suitable retainer, about the outer periphery of the insert member 121.
  • the disc mounting portion formed integrally with the star member, for example, if the star comprises a PM (powdered metal) part.
  • the subject embodiment includes spool valving
  • the invention is not so limited, and the present invention may be utilized with gerotor motors having various types of disc valving, as long as the disc valving is disposed either forwardly of the gerotor gear set 15, or disposed rearwardly of the gerotor set, but with the valving action occurring far enough radially outward that the valving does not interfere with the brake disc pack 89.
  • the present invention provides a dynamic brake which is not located such that the dynamic brake is required to hold the full output torque of the motor.
  • the torque required to prevent orbital and rotational motion of the star 31 is only one-sixth the torque required to prevent rotational motion of the output shaft 43. The reason for this is well understood by those skilled in the art of gerotor gear sets.
  • the present invention provides a dynamic brake which does not engage the profile of the star 31, thus eliminating potential damage to the profile, and does not require any substantial redesign of any portion of the motor disposed forwardly of the endcap 21.
  • the dynamic brake of the present invention could be an optional feature for a standard motor in which the only change would be to replace the conventional endcap with the endcap assembly 17 shown herein and provide the insert member 54.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
EP98105403A 1997-04-10 1998-03-25 Bremse für einen Innenzahnradmotor Withdrawn EP0870922A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US83167397A 1997-04-10 1997-04-10
US831673 1997-04-10

Publications (1)

Publication Number Publication Date
EP0870922A1 true EP0870922A1 (de) 1998-10-14

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ID=25259588

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98105403A Withdrawn EP0870922A1 (de) 1997-04-10 1998-03-25 Bremse für einen Innenzahnradmotor

Country Status (3)

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EP (1) EP0870922A1 (de)
JP (1) JPH10325386A (de)
CN (1) CN1216346A (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0931936A1 (de) * 1998-01-23 1999-07-28 Eaton Corporation Innenzahnradmotor und Verteilerventil und Feststellbremse
EP1058007A2 (de) * 1999-06-03 2000-12-06 Eaton Corporation Innenzahnradmotor und Feststellbremse
DE102005043855A1 (de) * 2005-09-13 2007-03-22 Sauer-Danfoss Aps Hydraulische Maschine
DE102008035088A1 (de) 2008-07-28 2010-02-04 Av Hydraulikmotoren Gmbh Hydraulikaggregat, insbesondere Hydraulikmotor
WO2022243968A1 (en) * 2021-05-21 2022-11-24 Danfoss Power Solutions Ii Technology A/S Hydraulic drive device comprising a gerotor type motor with a friction brake

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7363851B2 (en) * 2006-01-20 2008-04-29 Fisher Controls International, Llc Spacers for use with actuator casings
US7695258B2 (en) * 2006-05-08 2010-04-13 White Drive Products, Inc. Gerotor motor and brake assembly
CN101839209A (zh) * 2010-05-11 2010-09-22 镇江大力液压马达有限责任公司 内置式制动摆线液压马达
CN101915204B (zh) * 2010-08-18 2012-08-08 镇江大力液压马达有限责任公司 内置集成阀式制动摆线液压马达
CA2966535C (en) * 2014-11-17 2022-11-29 Eaton Corporation Rotary fluid pressure device with drive-in-drive valve arrangement
CN105003196A (zh) * 2015-07-27 2015-10-28 王乐康 一种全液压反循环钻机的动力总成
CN111980913A (zh) * 2019-05-23 2020-11-24 镇江大力液压马达股份有限公司 一种液压制动马达装置
CN114249256B (zh) * 2020-09-23 2023-01-31 中联重科股份有限公司 旋转驱动机构、臂架组件及工程机械

Citations (7)

* 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
US3960470A (en) * 1975-03-17 1976-06-01 Trw Inc. Hydraulic motor brake
DE3125087A1 (de) * 1981-06-26 1983-01-13 Danfoss A/S, 6430 Nordborg "bremse fuer einen hydraulischen motor"
JPS5885370A (ja) * 1981-11-17 1983-05-21 Sumitomo Eaton Kiki Kk 油圧モ−タにおけるブレ−キ装置
US4592704A (en) 1984-03-05 1986-06-03 Eaton Corporation Motor with improved low-speed operation
US4981423A (en) 1989-10-03 1991-01-01 Trw Inc. Hydraulic motor with wobble-stick and brake assembly
EP0442031A1 (de) * 1990-02-13 1991-08-21 Kinshofer Greiftechnik Gmbh Bremse für einen Hydromotor

Patent Citations (7)

* 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
US3960470A (en) * 1975-03-17 1976-06-01 Trw Inc. Hydraulic motor brake
DE3125087A1 (de) * 1981-06-26 1983-01-13 Danfoss A/S, 6430 Nordborg "bremse fuer einen hydraulischen motor"
JPS5885370A (ja) * 1981-11-17 1983-05-21 Sumitomo Eaton Kiki Kk 油圧モ−タにおけるブレ−キ装置
US4592704A (en) 1984-03-05 1986-06-03 Eaton Corporation Motor with improved low-speed operation
US4981423A (en) 1989-10-03 1991-01-01 Trw Inc. Hydraulic motor with wobble-stick and brake assembly
EP0442031A1 (de) * 1990-02-13 1991-08-21 Kinshofer Greiftechnik Gmbh Bremse für einen Hydromotor

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 7, no. 183 (M - 235)<1328> 12 August 1983 (1983-08-12) *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0931936A1 (de) * 1998-01-23 1999-07-28 Eaton Corporation Innenzahnradmotor und Verteilerventil und Feststellbremse
EP1058007A2 (de) * 1999-06-03 2000-12-06 Eaton Corporation Innenzahnradmotor und Feststellbremse
EP1058007A3 (de) * 1999-06-03 2001-12-12 Eaton Corporation Innenzahnradmotor und Feststellbremse
DE102005043855A1 (de) * 2005-09-13 2007-03-22 Sauer-Danfoss Aps Hydraulische Maschine
DE102005043855B4 (de) * 2005-09-13 2007-12-13 Sauer-Danfoss Aps Hydraulische Maschine
DE102008035088A1 (de) 2008-07-28 2010-02-04 Av Hydraulikmotoren Gmbh Hydraulikaggregat, insbesondere Hydraulikmotor
WO2022243968A1 (en) * 2021-05-21 2022-11-24 Danfoss Power Solutions Ii Technology A/S Hydraulic drive device comprising a gerotor type motor with a friction brake

Also Published As

Publication number Publication date
JPH10325386A (ja) 1998-12-08
CN1216346A (zh) 1999-05-12

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