EP0124299B1 - Hydraulic gerotor motor and parking brake for use therein - Google Patents
Hydraulic gerotor motor and parking brake for use therein Download PDFInfo
- Publication number
- EP0124299B1 EP0124299B1 EP19840302283 EP84302283A EP0124299B1 EP 0124299 B1 EP0124299 B1 EP 0124299B1 EP 19840302283 EP19840302283 EP 19840302283 EP 84302283 A EP84302283 A EP 84302283A EP 0124299 B1 EP0124299 B1 EP 0124299B1
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- European Patent Office
- Prior art keywords
- lock member
- toothed
- movement
- internally
- disposed
- 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.)
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- 239000012530 fluid Substances 0.000 claims description 42
- 230000007246 mechanism Effects 0.000 claims description 28
- 238000006073 displacement reaction Methods 0.000 claims description 18
- 238000013459 approach Methods 0.000 claims description 6
- 230000004044 response Effects 0.000 claims description 6
- 230000000452 restraining effect Effects 0.000 claims 1
- 238000007789 sealing Methods 0.000 claims 1
- 238000004891 communication Methods 0.000 description 6
- 230000004323 axial length Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Images
Classifications
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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
- F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
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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
- 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
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
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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
- 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 hydraulic motors of the gerotor type, and more particularly, to a parking brake for use in such motors.
- the present invention may be utilized in hydraulic devices functioning as pumps, it is especially advantageous when used with a device operating as a motor, and will be described in connection therewith.
- Hydraulic motors utilizing gerotor displacement mechanisms have been popular for many years for low speed high torque applications.
- Such motors typically include a housing defining a fluid inlet and a fluid outlet and a gerotor gear set associated with the housing.
- the gerotor gear set normally includes an internally-toothed ring fixed to the housing, and an externally-toothed star eccentrically disposed within the ring for orbital and rotational movement relative to the ring.
- the teeth of the ring and star interengage to define expanding and contracting volume chambers during the relative movement.
- a valve means within the housing operates in response to the relative movement to communicate fluid from the fluid inlet to the expanding fluid chambers, and from the contracting fluid chambers to the fluid outlet.
- An output shaft extends from the housing and is rotatably supported thereby, and a shaft member has a first end connected to the star and a second end connected to the output shaft, to transmit the orbital and rotational movements of the star into a low speed high torque rotational movement of the output shaft.
- Low speed high torque gerotor motors are frequently used to propel the drive wheels of vehicles, thus making it desirable for the motor to include some form of parking brake.
- Another major use of such motors is to drive vehicle accessories, such as hoists and winches, and in this type of application it is desirable for the motor to have a "load holding" capability.
- a disc pack Another approach to the need for a positive acting brake has been the use of a disc pack, with some of the discs being splined to the fixed housing, and alternating discs being splined to the rotating output shaft.
- the discs are spring biased into engagement (braking) and hydraulic pressure is required to disengage the discs.
- the disc pack is disposed within the housing of the gerotor motor and is operable to lock the motor output shaft to the motor housing. This approach requires almost total redesign of the motor housing and output shaft, thus making it economically impractical to offer a parking brake as a motor option.
- a separate parking brake package engages the motor output shaft and has its own housing and separate output shaft which can be locked together by engagement of a disc pack. This separate parking brake has the advantage that it can be added as an option, because no-major modification of the motor is required, but the cost of the commercially available parking brake may be as much or more than the gerotor motor itself.
- the above and other objects of the present invention are accomplished by the provision of an improved rotary fluid pressure device of the type described.
- the device is characterized by a lock member operably associated with the internally-toothed member and disposed at least partially within one of the volume chambers.
- the device includes actuation means operably associated with the lock member and operable to move the lock member between first and second positions. In the first position the lock member is disposed to permit normal orbital and rotational movement of the tooth members. In the second position, the lock member extends a sufficient distance into the volume chamber to engage one of the external teeth of the externally-toothed member as the volume chamber approaches a minimum chamber volume, to prevent further orbital movement of the member having orbital movement, thereby preventing rotation of the member having rotational movement.
- FIG. 1 illustrates a low speed high torque gerotor motor of the type to which the present invention may be applied and which is illustrated and described in greater detail in U.S. Pat. Nos. 3,572,983 and 4,343,600, both of which are assigned to the assignee of the present invention, and are incorporated herein by reference.
- the hydraulic motor shown in FIG. 1 comprises a plurality of sections secured together, such as by a plurality of bolts 11 (shown in only in FIG. 2).
- the motor includes a shaft support casing 13, a wear plate 15, a gerotor displacement mechanism 17, a port plate 19, and a valve housing portion 21.
- the gerotor displacement mechanism 17 is well known in the art, is shown and described in great detail in the incorporated patents, and will be described only briefly herein. More specifically, the displacement mechanism 17 is a Geroler@ mechanism comprising an internally-toothed ring 23 defining a plurality of generally semi-cylindrical openings, with a cylindrical member 25 disposed in each of the openings. Eccentrically disposed within the ring 23 is an externally-toothed star 27, typically having one less external tooth than the number of cylindrical members 25, thus permitting the star 27 to orbit and rotate relative to the ring 23. The relative orbital and rotational movement between the ring 23 and star 27 defines a plurality of expanding and contracting volume chambers 29.
- the motor includes an output shaft 31 positioned within the shaft support casing 13 and rotatably supported therein by suitable bearing sets 33 and 35.
- the shaft 31 includes a set of internal, straight splines 37, and in engagement therewith is a set of external, crowned splines 39 formed on one end of a main drive shaft 41.
- Disposed at the opposite end of the main drive shaft 41 is another set of external, crowned splines 43, in engagement with a set of internal, straight splines 45, formed on the inside diameter of the star 27. Therefore, in the subject embodiment, because the ring 23 includes seven internal teeth 25, and the star 27 includes six external teeth, six orbits of the star 27 result in one complete rotation thereof, and one complete rotation of the main drive shaft 41 and the output shaft 31.
- the drive shaft 41 always has its axis disposed at an angle relative to the main axis of the motor, i.e., the axis of the ring 23 and of the output shaft 31.
- the primary function of the drive shaft 41 is to transmit torque from the gerotor star 27 to the output shaft 31. This is accomplished by translating the orbital and rotational movement of the star 27 into pure rotational motion of the output shaft 31.
- a set of external splines 47 formed about one end of a valve drive shaft 49 which has, at its opposite end, another set of external splines 51 in engagement with a set of internal splines 53 formed about the inner periphery of a valve member 55.
- the valve member 55 is rotatably disposed within the valve housing 2.
- the valve drive shaft 49 is splined to both the star 27 and the valve member 55 in order to maintain proper valve timing therebetween, as is generally well known in the art.
- the valve housing 21 includes a fluid port 57 in communication with an annular chamber 59 which surrounds the valve member 55.
- the valve housing 21 also includes an outlet port 61 which is in fluid communication with a chamber 63 disposed between the valve housing 21 and valve member 55.
- the valve member 55 defines a plurality of alternating valve passages 65 and 67, the passages 65 being in continuous fluid communication with the annular chamber 59, and the passages 67 being in continuous fluid communication with the chamber 63. In the subject embodiment, there are six of the passages 65, and six of the passages 67, corresponding to the six external teeth of the star 27.
- the port plate 19 defines a plurality of fluid passages 69 (only one of which is shown in FIG.
- the internally-toothed ring 23 includes a generally radially extending boss portion 71.
- the boss portion 71 defines a radially-extending opening 73, which extends radially inward and opens into one of the volume chambers 29.
- the opening 73 includes an inner, smooth bore portion 75, and an outer larger, threaded portion 77.
- the bore portion 75 is intersected by an axially oriented, upside down U-shaped recess 79 (see FIG. 3).
- the recess 79 preferably extends the entire axial length of the ring 23.
- Disposed within the recess 79 is an elongated, generally cylindrical lock member 81.
- the lock member 81 is retained within the recess 79 because the opening defined by the intersection of the recess 79 and volume chamber 29 has a circumferential width w which is less than the diameter of the lock member 81 (see FIG. 3).
- the recess 79 is disposed circumferentially between a pair of adjacent internal teeth 25. Also, it should be noted in FIG. 3 that the configuration of the recess 79 permits some radial movement of the lock member 81, the purpose of which will be described subsequently.
- the actuation mechanism 83 includes a generally cylindrical back-up member 85 disposed within the bore portion 75.
- the back-up member 85 includes an 0-ring member disposed between it and the bore portion 75 to prevent fluid leakage past the member 85 when the adjacent volume chamber 29 contains pressurized fluid.
- the back-up member 85 includes a surface 87 which defines a portion of a cylinder and engages the cylindrical lock member 81.
- the actuation mechanism 83 further includes an actuator 89 disposed in the opening 73, adjacent the end of the back-up member 85.
- the actuator 89 includes an externally-threaded portion 91 which is in threaded engagement with the threaded portion 77 of the opening 73.
- the actuator 89 also includes a serrated portion 93 which is adapted to receive a handle member (not shown), whereby movement of the handle member results in rotation of the actuator 89, and movement either radially inwardly, or radially outwardly, depending upon the direction of movement of the handle.
- the actuator 89 also includes another externally threaded portion 95, adapted to be in threaded engagement with a nut (not shown) for retention of the handle.
- the lock mechanism When it is desired to permit the motor to operate in its normal fashion, i.e., with the star 27 engaging in its normal orbital and rotational movement with respect to the ring 23, the lock mechanism is placed in an unactuated condition. This is accomplished by moving the handle (not shown) to rotate the actuator 89 in a direction which results in movement upward in FIG. 2, radially away from the star 27. Such movement of the actuator 89 will permit orbital movement of the star 27 to force the lock member 81 and back-up member 85 radially upward toward the actuator 89. Normally, because of the 0-ring surrounding the back-up member 85, the member 85 will then remain in this upward position, as described above.
- the lock member 81 will remain free to move radially within the recess 79, first moving radially upwardly whenever one of the teeth of the star 27 enters the volume chamber adjacent the lock member 81, causing that volume chamber to approach the minimum chamber volume (see FIG. 3). Then, as the star 27 continues to orbit, and the adjacent volume chamber increases in volume, the lock member 81 will be free to move radially inwardly, merely under the force of gravity, back to the position shown in FIG. 2.
- the handle When it is desired to actuate the lock mechanism, in the manner of a vehicle parking brake, or as a load holding device on a winch, the handle is moved the opposite direction to rotate the actuator 89 in the opposite direction, causing it to move radially inwardly.
- the inward movement of the actuator 89 by virtue of the threaded engagement between the portion 91 and threaded portion 77, forces the back-up member 85 radially inwardly.
- the inward movement of the member 85 moves the lock member 81 to its radially inner most position, as shown in FIG. 2.
- the lock member 81 is maintained fixed in the inward most position, and as the star 27 orbits, one of the external teeth of the star enters the adjacent volume chamber.
- the external tooth of the star 27 instead of the external tooth of the star 27 causing the volume chamber to reach the minimum chamber volume, as during normal operation, the external tooth engages the lock member 81, and is prevented from moving further into the volume chamber. Thus, further orbital movement of the star 27 is prevented, as is further rotational movement of the star, relative to the ring.
- the amount of radial movement of the lock member 81, actuation member 83 and back-up member 85, between the unactuated and actuated conditions is quite small. Typically, radial movement of less than .100 inches (2.54 mm) is sufficient, and in the subject embodiment, a movement of only .060 inches (1.53 mm) was required. It will be understood by those skilled in the art that the amount of radial movement required is in each case a function of the geometry of the particular gerotor displacement mechanism.
- the device shown in FIG. 4 includes a housing 101 which receives the plurality of bolts 111. Disposed within the housing 101 is the internally-toothed ring 123 including the internal teeth (cylindrical members 125). Eccentrically disposed within the ring 123 is an externally-toothed star 127, and the relative orbital and rotational motion between the ring 123 and star 127 are the same as in the FIG. 2 embodiment. However, in the FIG. 4 embodiment, the star 127 only rotates, while the ring 123 only orbits.
- the housing 101 defines a plurality of semicircular cutouts, each of which receives a roller 103.
- the ring 123 defines, about its outer periphery, a plurality of arcuate cutouts 105, each of which corresponds to one of the rollers 103.
- communication of fluid to and from the expanding and contracting volume chambers 129 will cause the ring 123 to orbit, while the engagement of the rollers 103 in the cutouts 105 prevents the ring 123 from rotating, thus permitting solely rotational motion of the star 127.
- the housing 101 includes a boss portion 171 which defines an opening 173 including a bore portion 175 and threaded portion 177. Disposed within the opening 173 is an actuation mechanism 183, including a back-up member 185 defining a surface 187. The mechanism 183 further includes an actuator 189 having a threaded portion 191, a serrated portion 193, and another threaded portion 195. All of the elements just described may be of the same structure as the corresponding elements in the FIG. 2 embodiment.
- the adjacent roller Upon actuation of the mechanism 183, which is accomplished in the same way as in the FIG. 2 embodiment, the adjacent roller is moved radially inwardly, and thus, that particular roller may also be considered a lock member 181. With the lock member 181 in the actuated position, normal orbital movement of the ring 123 is prevented, and therefore, normal rotational movement of the star 127 is also prevented.
- the present invention provides a simple, inexpensive and efficient way of locking the gerotor displacement mechanism in the manner of a parking brake or a load holding device.
- the present invention makes it possible to accomplish this without the need to add any additional sections to the motor, and as shown in the FIG. 2 embodiment, only the gerotor ring 23 is modified, all other parts are the same as in the standard motor.
- the present invention makes it possible to provide a motor lock with no substantial increase in the size or weight of the motor, or the space required by the motor.
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- Rotary Pumps (AREA)
Description
- The present invention relates to hydraulic motors of the gerotor type, and more particularly, to a parking brake for use in such motors.
- Although the present invention may be utilized in hydraulic devices functioning as pumps, it is especially advantageous when used with a device operating as a motor, and will be described in connection therewith.
- Hydraulic motors utilizing gerotor displacement mechanisms have been popular for many years for low speed high torque applications. Such motors typically include a housing defining a fluid inlet and a fluid outlet and a gerotor gear set associated with the housing. The gerotor gear set normally includes an internally-toothed ring fixed to the housing, and an externally-toothed star eccentrically disposed within the ring for orbital and rotational movement relative to the ring. The teeth of the ring and star interengage to define expanding and contracting volume chambers during the relative movement. A valve means within the housing operates in response to the relative movement to communicate fluid from the fluid inlet to the expanding fluid chambers, and from the contracting fluid chambers to the fluid outlet. An output shaft extends from the housing and is rotatably supported thereby, and a shaft member has a first end connected to the star and a second end connected to the output shaft, to transmit the orbital and rotational movements of the star into a low speed high torque rotational movement of the output shaft.
- As is well known to those skilled in the art, various arrangements of gerotor motors are known other than that described above wherein the ring is fixed to the housing and the star orbits and rotates, and although the invention may be applied advantageously to such other gerotor motor arrangements, as will be described subsequently, the above-described arrangement is the most common and constitutes the preferred embodiment of the invention.
- Low speed high torque gerotor motors are frequently used to propel the drive wheels of vehicles, thus making it desirable for the motor to include some form of parking brake. Another major use of such motors is to drive vehicle accessories, such as hoists and winches, and in this type of application it is desirable for the motor to have a "load holding" capability.
- One attempt by those working in the prior art to provide a motor equipped with a parking brake is shown in U.S. Pat. 3,616,882 in which a thin, flexible friction member can be selectively pressure biased into engagement with an end face of the gerotor star. However, it appears that such an arrangement would result in excessive friction and generated heat, with the possibility of galling the end surface of the star. In addition, the parking brake shown in the cited reference is not positive acting but instead, depends upon the presence of hydraulic pressure.
- Another approach to the need for a positive acting brake has been the use of a disc pack, with some of the discs being splined to the fixed housing, and alternating discs being splined to the rotating output shaft. Typically, the discs are spring biased into engagement (braking) and hydraulic pressure is required to disengage the discs. In one commercial embodiment, the disc pack is disposed within the housing of the gerotor motor and is operable to lock the motor output shaft to the motor housing. This approach requires almost total redesign of the motor housing and output shaft, thus making it economically impractical to offer a parking brake as a motor option. In another commercial design, a separate parking brake package engages the motor output shaft and has its own housing and separate output shaft which can be locked together by engagement of a disc pack. This separate parking brake has the advantage that it can be added as an option, because no-major modification of the motor is required, but the cost of the commercially available parking brake may be as much or more than the gerotor motor itself.
- Accordingly, it is an object of the present invention to provide a rotary fluid pressure device having an integral parking brake (lock) which does not involve any change in, or addition to the hydraulic circuit of the motor.
- It is another object of the present invention to provide such a parking brake which is failsafe in operation, i.e., provides a positive mechanical lock to prevent rotation of the motor output shaft.
- It is another object of the present invention to provide such a parking brake which is integral with the motor, but which may be added to the motor as an option at reasonable expense, without requiring substantial redesign of the motor.
- The above and other objects of the present invention are accomplished by the provision of an improved rotary fluid pressure device of the type described. The device is characterized by a lock member operably associated with the internally-toothed member and disposed at least partially within one of the volume chambers. The device includes actuation means operably associated with the lock member and operable to move the lock member between first and second positions. In the first position the lock member is disposed to permit normal orbital and rotational movement of the tooth members. In the second position, the lock member extends a sufficient distance into the volume chamber to engage one of the external teeth of the externally-toothed member as the volume chamber approaches a minimum chamber volume, to prevent further orbital movement of the member having orbital movement, thereby preventing rotation of the member having rotational movement.
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- FIG. 1 is-an axial cross section showing a low speed high torque gerotor motor of the type to which the present invention may be applied.
- FIG. 2 is a transverse cross section taken on line 2-2 of FIG. 1, and on the same scale as FIG. 1, illustrating the motor lock of the present invention.
- FIG. 3 is an enlarged, fragmentary view, similar to FIG. 2, but taken as a plan view of the gerotor displacement mechanism.
- FIG. 4 is a transverse cross section, similar to FIG. 2, illustrating the use of the present invention in an alternative type of rotary fluid pressure device, the general arrangement of which type being disclosed in GB-A-2033479.
- Referring now to the drawings, which are not intended to limit the invention, FIG. 1 illustrates a low speed high torque gerotor motor of the type to which the present invention may be applied and which is illustrated and described in greater detail in U.S. Pat. Nos. 3,572,983 and 4,343,600, both of which are assigned to the assignee of the present invention, and are incorporated herein by reference.
- The hydraulic motor shown in FIG. 1 comprises a plurality of sections secured together, such as by a plurality of bolts 11 (shown in only in FIG. 2). The motor includes a
shaft support casing 13, awear plate 15, agerotor displacement mechanism 17, aport plate 19, and avalve housing portion 21. - The
gerotor displacement mechanism 17 is well known in the art, is shown and described in great detail in the incorporated patents, and will be described only briefly herein. More specifically, thedisplacement mechanism 17 is a Geroler@ mechanism comprising an internally-toothed ring 23 defining a plurality of generally semi-cylindrical openings, with acylindrical member 25 disposed in each of the openings. Eccentrically disposed within thering 23 is an externally-toothed star 27, typically having one less external tooth than the number ofcylindrical members 25, thus permitting thestar 27 to orbit and rotate relative to thering 23. The relative orbital and rotational movement between thering 23 andstar 27 defines a plurality of expanding and contractingvolume chambers 29. - Referring still to FIG. 1, the motor includes an
output shaft 31 positioned within theshaft support casing 13 and rotatably supported therein bysuitable bearing sets shaft 31 includes a set of internal,straight splines 37, and in engagement therewith is a set of external, crowned splines 39 formed on one end of amain drive shaft 41. Disposed at the opposite end of themain drive shaft 41 is another set of external, crownedsplines 43, in engagement with a set of internal,straight splines 45, formed on the inside diameter of thestar 27. Therefore, in the subject embodiment, because thering 23 includes seveninternal teeth 25, and thestar 27 includes six external teeth, six orbits of thestar 27 result in one complete rotation thereof, and one complete rotation of themain drive shaft 41 and theoutput shaft 31. - As is well known to those skilled in the art, the
drive shaft 41 always has its axis disposed at an angle relative to the main axis of the motor, i.e., the axis of thering 23 and of theoutput shaft 31. The primary function of thedrive shaft 41 is to transmit torque from thegerotor star 27 to theoutput shaft 31. This is accomplished by translating the orbital and rotational movement of thestar 27 into pure rotational motion of theoutput shaft 31. - Also in engagement with the
internal splines 45 is a set ofexternal splines 47 formed about one end of avalve drive shaft 49 which has, at its opposite end, another set ofexternal splines 51 in engagement with a set ofinternal splines 53 formed about the inner periphery of avalve member 55. Thevalve member 55 is rotatably disposed within thevalve housing 2. Thevalve drive shaft 49 is splined to both thestar 27 and thevalve member 55 in order to maintain proper valve timing therebetween, as is generally well known in the art. - The
valve housing 21 includes afluid port 57 in communication with anannular chamber 59 which surrounds thevalve member 55. Thevalve housing 21 also includes an outlet port 61 which is in fluid communication with achamber 63 disposed between thevalve housing 21 andvalve member 55. Thevalve member 55 defines a plurality of alternating valve passages 65 and 67, the passages 65 being in continuous fluid communication with theannular chamber 59, and the passages 67 being in continuous fluid communication with thechamber 63. In the subject embodiment, there are six of the passages 65, and six of the passages 67, corresponding to the six external teeth of thestar 27. Theport plate 19 defines a plurality of fluid passages 69 (only one of which is shown in FIG. 1), each of which is disposed to be in continuous fluid communication with theadjacent volume chamber 29. Motors of the type shown in FIG. 1 are commercially available, and are well known to those skilled in the art, and for any further details regarding the construction or operation of such a motor, reference should be made to the above incorporated patents. - Referring now to FIGS. 2 and 3, in conjunction with FIG. 1, the motor lock of the present invention will be described. As may best be seen in FIGS. 1 and 2, the internally-
toothed ring 23 includes a generally radially extendingboss portion 71. Theboss portion 71 defines a radially-extendingopening 73, which extends radially inward and opens into one of thevolume chambers 29. Theopening 73 includes an inner, smooth bore portion 75, and an outer larger, threadedportion 77. - The bore portion 75 is intersected by an axially oriented, upside down U-shaped recess 79 (see FIG. 3). The
recess 79 preferably extends the entire axial length of thering 23. Disposed within therecess 79 is an elongated, generallycylindrical lock member 81. Thelock member 81 is retained within therecess 79 because the opening defined by the intersection of therecess 79 andvolume chamber 29 has a circumferential width w which is less than the diameter of the lock member 81 (see FIG. 3). As may best be seen in FIGS. 2 and 3, therecess 79 is disposed circumferentially between a pair of adjacentinternal teeth 25. Also, it should be noted in FIG. 3 that the configuration of therecess 79 permits some radial movement of thelock member 81, the purpose of which will be described subsequently. - Associated with the
radial opening 73 is an actuation mechanism, generally designated 83. The actuation mechanism 83 includes a generally cylindrical back-up member 85 disposed within the bore portion 75. The back-up member 85 includes an 0-ring member disposed between it and the bore portion 75 to prevent fluid leakage past the member 85 when theadjacent volume chamber 29 contains pressurized fluid. The back-up member 85 includes a surface 87 which defines a portion of a cylinder and engages thecylindrical lock member 81. - The actuation mechanism 83 further includes an
actuator 89 disposed in theopening 73, adjacent the end of the back-up member 85. Theactuator 89 includes an externally-threadedportion 91 which is in threaded engagement with the threadedportion 77 of theopening 73. Theactuator 89 also includes a serrated portion 93 which is adapted to receive a handle member (not shown), whereby movement of the handle member results in rotation of theactuator 89, and movement either radially inwardly, or radially outwardly, depending upon the direction of movement of the handle. Theactuator 89 also includes another externally threaded portion 95, adapted to be in threaded engagement with a nut (not shown) for retention of the handle. - Referring now primarily to FIG. 2, the operation of the motor lock of the present invention will be described. When it is desired to permit the motor to operate in its normal fashion, i.e., with the
star 27 engaging in its normal orbital and rotational movement with respect to thering 23, the lock mechanism is placed in an unactuated condition. This is accomplished by moving the handle (not shown) to rotate theactuator 89 in a direction which results in movement upward in FIG. 2, radially away from thestar 27. Such movement of theactuator 89 will permit orbital movement of thestar 27 to force thelock member 81 and back-up member 85 radially upward toward theactuator 89. Normally, because of the 0-ring surrounding the back-up member 85, the member 85 will then remain in this upward position, as described above. However, thelock member 81 will remain free to move radially within therecess 79, first moving radially upwardly whenever one of the teeth of thestar 27 enters the volume chamber adjacent thelock member 81, causing that volume chamber to approach the minimum chamber volume (see FIG. 3). Then, as thestar 27 continues to orbit, and the adjacent volume chamber increases in volume, thelock member 81 will be free to move radially inwardly, merely under the force of gravity, back to the position shown in FIG. 2. - When it is desired to actuate the lock mechanism, in the manner of a vehicle parking brake, or as a load holding device on a winch, the handle is moved the opposite direction to rotate the
actuator 89 in the opposite direction, causing it to move radially inwardly. The inward movement of theactuator 89, by virtue of the threaded engagement between theportion 91 and threadedportion 77, forces the back-up member 85 radially inwardly. The inward movement of the member 85 moves thelock member 81 to its radially inner most position, as shown in FIG. 2. Now, however, in the actuated condition of the device, thelock member 81 is maintained fixed in the inward most position, and as thestar 27 orbits, one of the external teeth of the star enters the adjacent volume chamber. Instead of the external tooth of thestar 27 causing the volume chamber to reach the minimum chamber volume, as during normal operation, the external tooth engages thelock member 81, and is prevented from moving further into the volume chamber. Thus, further orbital movement of thestar 27 is prevented, as is further rotational movement of the star, relative to the ring. - It should be understood by those skilled in the art that the mode of operation described above would be the same in any device in which there is relative orbital and rotational movement between the
star 27 and thering 23, regardless of which member engages in which movement. For example, it is known to have thestar 27 only orbit, while thering 23 only rotates, and various other combinations are known. The lock mechanism of the present invention may be applied in a device using any of the possible combinations of relative orbital and rotational movement. - It should be noted that in accordance with the present invention, the amount of radial movement of the
lock member 81, actuation member 83 and back-up member 85, between the unactuated and actuated conditions, is quite small. Typically, radial movement of less than .100 inches (2.54 mm) is sufficient, and in the subject embodiment, a movement of only .060 inches (1.53 mm) was required. It will be understood by those skilled in the art that the amount of radial movement required is in each case a function of the geometry of the particular gerotor displacement mechanism. - Referring now to FIG. 4, there is illustrated the use of the present invention in an alternative type of rotary fluid pressure device. In the FIG. 4 embodiment, elements which are the same or similar to those shown in FIG. 2 bear the same reference numeral, plus 100, while totally new elements bear reference numerals beginning with 101. Accordingly, the device shown in FIG. 4 includes a
housing 101 which receives the plurality of bolts 111. Disposed within thehousing 101 is the internally-toothed ring 123 including the internal teeth (cylindrical members 125). Eccentrically disposed within thering 123 is an externally-toothed star 127, and the relative orbital and rotational motion between thering 123 and star 127 are the same as in the FIG. 2 embodiment. However, in the FIG. 4 embodiment, the star 127 only rotates, while thering 123 only orbits. - The
housing 101 defines a plurality of semicircular cutouts, each of which receives aroller 103. Thering 123 defines, about its outer periphery, a plurality ofarcuate cutouts 105, each of which corresponds to one of therollers 103. As is well known in the art, communication of fluid to and from the expanding and contracting volume chambers 129 will cause thering 123 to orbit, while the engagement of therollers 103 in thecutouts 105 prevents thering 123 from rotating, thus permitting solely rotational motion of the star 127. - The
housing 101 includes aboss portion 171 which defines anopening 173 including abore portion 175 and threaded portion 177. Disposed within theopening 173 is anactuation mechanism 183, including a back-up member 185 defining a surface 187. Themechanism 183 further includes anactuator 189 having a threadedportion 191, aserrated portion 193, and another threadedportion 195. All of the elements just described may be of the same structure as the corresponding elements in the FIG. 2 embodiment. - Upon actuation of the
mechanism 183, which is accomplished in the same way as in the FIG. 2 embodiment, the adjacent roller is moved radially inwardly, and thus, that particular roller may also be considered alock member 181. With thelock member 181 in the actuated position, normal orbital movement of thering 123 is prevented, and therefore, normal rotational movement of the star 127 is also prevented. - Although the preferred embodiment utilizes rotation of a threaded member to effect radial movement of the
lock member 81, it should be apparent that other forms of actuation could be used. For example, fluid pressure could be communicated to the upper end of the back-up member 85 to bias the member 85 and thelock member 81 inwardly to the actuated position. Also, various other mechanical arrangements could be utilized, such as some form of axial movement of a wedging member, to move the lock member inwardly. It would also be possible to have thelock member 81 enter the volume chamber axially, rather than radially. - It should be apparent to those skilled in the art that the present invention provides a simple, inexpensive and efficient way of locking the gerotor displacement mechanism in the manner of a parking brake or a load holding device. The present invention makes it possible to accomplish this without the need to add any additional sections to the motor, and as shown in the FIG. 2 embodiment, only the
gerotor ring 23 is modified, all other parts are the same as in the standard motor. Thus, the present invention makes it possible to provide a motor lock with no substantial increase in the size or weight of the motor, or the space required by the motor.
Claims (17)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US48197283A | 1983-04-04 | 1983-04-04 | |
US481972 | 1983-04-04 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0124299A2 EP0124299A2 (en) | 1984-11-07 |
EP0124299A3 EP0124299A3 (en) | 1986-12-17 |
EP0124299B1 true EP0124299B1 (en) | 1989-03-22 |
Family
ID=23914130
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19840302283 Expired EP0124299B1 (en) | 1983-04-04 | 1984-04-03 | Hydraulic gerotor motor and parking brake for use therein |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0124299B1 (en) |
JP (1) | JPS59194083A (en) |
DE (1) | DE3477415D1 (en) |
DK (1) | DK162791C (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP4276298A1 (en) * | 2022-05-10 | 2023-11-15 | Honeywell International Inc. | Actuator systems for thrust reverser |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4613292A (en) * | 1985-02-01 | 1986-09-23 | Eaton Corporation | Hydraulic motor having free-wheeling and locking modes of operation |
DE19727887C2 (en) * | 1997-07-01 | 1999-04-15 | Danfoss As | Hydraulic machine |
CN102168643B (en) * | 2011-03-25 | 2013-04-17 | 意宁液压股份有限公司 | Novel structure for cycloid hydraulic motor flow distributor |
KR101535266B1 (en) * | 2014-04-16 | 2015-07-08 | 해원산업주식회사 | Washing water spraing apparatus for washing for oil-tank |
US9850898B2 (en) | 2015-03-24 | 2017-12-26 | Ford Global Technologies, Llc | Gerotor pump for a vehicle |
IT201800008269A1 (en) * | 2018-08-31 | 2020-03-02 | Dana Motion Systems Italia Srl | Improved Hydraulic Orbital Machine and Adjustment Method of an Orbital Machine. |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3572983A (en) * | 1969-11-07 | 1971-03-30 | Germane Corp | Fluid-operated motor |
US3616882A (en) * | 1970-02-05 | 1971-11-02 | Trw Inc | Hydraulic motor-pump assembly with built-in brake |
DE2224484A1 (en) * | 1972-05-19 | 1973-12-06 | Ahmed Solhtschi | DEVICE FOR A DRIVEN VEHICLE, IN PARTICULAR MOTOR VEHICLE |
DE2844844A1 (en) * | 1978-10-14 | 1980-04-17 | Rexroth Gmbh G L | CIRCULAR PISTON MACHINE |
US4343600A (en) * | 1980-02-04 | 1982-08-10 | Eaton Corporation | Fluid pressure operated pump or motor with secondary valve means for minimum and maximum volume chambers |
-
1984
- 1984-02-28 DK DK122084A patent/DK162791C/en active
- 1984-04-03 DE DE8484302283T patent/DE3477415D1/en not_active Expired
- 1984-04-03 EP EP19840302283 patent/EP0124299B1/en not_active Expired
- 1984-04-04 JP JP6601984A patent/JPS59194083A/en active Granted
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP4276298A1 (en) * | 2022-05-10 | 2023-11-15 | Honeywell International Inc. | Actuator systems for thrust reverser |
Also Published As
Publication number | Publication date |
---|---|
DK122084A (en) | 1984-10-05 |
JPH033072B2 (en) | 1991-01-17 |
DE3477415D1 (en) | 1989-04-27 |
DK122084D0 (en) | 1984-02-28 |
DK162791C (en) | 1992-04-27 |
EP0124299A3 (en) | 1986-12-17 |
EP0124299A2 (en) | 1984-11-07 |
DK162791B (en) | 1991-12-09 |
JPS59194083A (en) | 1984-11-02 |
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