JPS59194083A - Rotary type fluid pressure device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary liquid pressure device of the Xeroke type.

Although the invention may also be used in rotary liquid pressure devices such as pumps, it is particularly useful when used in devices that act as motors, and this specification will be discussed in connection with this case.

Hydraulic motors using a zero displacement mechanism are capable of low speed,
It has been commonly used for many years for high torque applications. Such motors generally include a housing with a fluid inlet and a fluid outlet, and a zero gear mechanism associated with the housing. : Equipped with. Zero rotor gear mechanisms generally include an internally toothed ring fixed to a housing and an externally toothed star gear disposed religiously within the ring for orbital and rotational motion relative to the ring.

The teeth of the ring and star interlock during relative movement to form an expanding fluid chamber and a contracting fluid chamber. A valving system within the housing operates in response to this relative movement to communicate fluid from the fluid inlet to the expanding fluid chamber and from the contracting fluid chamber to the fluid outlet.

An output shaft is rotatably supported by and extends from the housing, and the drive shaft has a first end coupled to the star and a second end coupled to the output shaft to direct the orbital and rotational motion of the star to the output shaft. Converts speed to high torque rotational motion.

As those skilled in the art are well aware, the unique configuration of a zero motor
& is known in addition to the above-mentioned device in which the ring is fixed to the housing and the star makes orbital and rotational movements, and this invention can be effectively applied to such other zero-rotor motor devices as described below, but the above-mentioned The device is quite common and constitutes a preferred embodiment of the invention.

Low speed, high torque zero torque motors are often used to propel the drive wheels of vehicles, and therefore it is desirable to provide some type of parking brake for the motor. The other main purpose of use of such force motors is to drive 1x, i-equipment (1゛L) of vehicles such as hoists and winches, and for this type of use, the motor has a load holding capacity. It is desirable to have

One attempt made by those working with prior art sound to provide a motor with a complete parking brake is shown in U.S. Pat. No. 3,616,882, in which The friction member of the flexure member is biased to engage one end surface of the zero toaster. However, such devices generate excessive friction and heat generation, and have the potential to cause scratches on the 1 m edge of the star. Moreover, it was shown in the 1st edition of the quotation. O-king brakes are not actively applied, but are activated by the presence of hydraulic pressure.

Another attempt to address the need for positive brakes is the use of disc packs, in which several discs are splined to a stationary housing and alternating discs are splined to a rotating output shaft. It is something that Generally, these discs are spring biased toward a locking (braking) condition, and hydraulic pressure releases all of the discs. In the commercially available embodiment, a disc or socket is disposed within the housing of the zero rotor motor and serves to secure the output shaft of the motor to the entire motor housing. This arrangement is economically impractical since the motor housing and output shaft must be almost completely redesigned. Other commercially designed equipment have a separate parking brake that engages the motor output shaft and is secured by its own housing and disc engagement. This separate/e-king brake is useful because it does not require major modifications to the motor, but it is also possible to use an integrated parking brake that does not require the addition or addition of a non-king brake that can be used commercially. (Fixing means) To provide a rotary fluid pressure device.

Another object of the present invention is to provide a chisel brake that is fail-safe and provides a complete mechanical locking means to prevent rotation of the motor output shaft during use.

Still another object of the present invention is to provide a parking brake that is integrated with the motor and can be optionally attached to the motor at a reasonable cost without the need for substantial design of the motor.

The above and other objects of the invention are achieved by the provision of an improved rotary fluid pressure device of the type described above. The device is characterized in that it has a fixation member, which in combination with the internal tooth member, is at least partially located within one of the Mc body chambers. The device is combined with a fixing member to provide a first. An actuation mechanism is included for moving the stationary bridge at the second position 1dj. In the first position, the fixing member is arranged to cause the tooth member to undergo regular orbital and rotational movement.

In the second shift, the fixed member extends a sufficient distance into the fluid chamber and engages one of the extrusions of the external toothing as the fluid chamber approaches its minimum volume, thereby preventing further movement of the orbiting member. Orbital movement is prevented, thereby preventing rotation of the rotationally moving member.

The present invention will be described below with reference to the drawings, but the invention is not limited to the illustrated embodiments. Figure 1 shows
This invention applies to U.S. Patent No. 3,572,983, U.S. Pat.
600 shows a low speed, high torque upper rotor motor as disclosed in the '600 specification.

The hydraulic motor shown in FIG. 1 includes a plurality of parts connected by a plurality of bolts 11 (only shown in FIG. 2). This motor includes a shaft support casing 13, a wear plate 15, a zero rotor mechanism 17, a port plate 19, and a valve housing 21f:
It is equipped with

Zerota (geometry 17 is well known in the art,
Since it is explained in detail in the above-mentioned patent T3A, a brief description will be given here. More specifically, the zero-to-re mechanism 17 has a portion of a plurality of almost early 1:;) shapes,
It is a serola mechanism in which a cylindrical member 25 is self-centered in each opening. External tooth star 27 is ring 2
3, and one fewer than the number of cylindrical members 25 (J'J k), thus the number of stars 27
allows for orbital and rotational movement relative to ring 23.

The relative 4'++ movement and rotational movement between the ring 23 and the star 27 creates a plurality of enlarged viL body chambers and reduced fa
ii', forming body u29.

In Fig. 1, this mold is the Tsukuda 1 support casing 13.
It comprises an output shaft 31 located within and rotatably supported within the casing by bearings 33,35. 113
1 has all IQ linear splines 37, one set of external crown-shaped splines 39 formed at one end of the main drive shaft 41 engages with the splines 37, and another set of external crown-shaped splines. 43 is provided at the opposite end of the main drive shaft 410 and engages a set of internal linear splines 45 formed in the inner bore of the star 27.

In this embodiment, since the ring 23 has seven internal teeth 25 and the star 27 has six external teeth, the star 27 makes one revolution through six orbital movements, and the main drive shaft 41 And the output shaft 31 rotates once.

As those skilled in the art well know, the drive shaft 41 is always the main axis of the motor, i.e. the axis of the ring 23 and the output shaft 31 &! r(
It has an axis arranged at an angle to the The main function of the drive shaft 41 is to transmit torque from the star 27 to the output shaft 31. This is star 27
This is achieved by converting the orbital motion and rotational motion of the output shaft 31 into the rotational motion of the output shaft 31.

A pair of outer splines 47 formed at one end of the valve drive shaft 49 engages with the inner splines 45, and the other end of the valve drive shaft 49 engages with an inner spline 53 formed in the inner hole of the valve member 55. It has another outer spline 51.

Valve member 55 is rotatably disposed within valve housing 21 .

Valve drive shaft 49 is splined to both star 27 and valve member 550 to maintain proper valve timing therebetween, as is well known in the art.

Valve housing 21 has a fluid volume 57 in communication with a current chamber 59 surrounding valve member 55 .

The valve housing 21 also has a fluid outlet 61 that communicates with a chamber 63 located between the valve housing 21 and the valve body 55. The valve members 55 are plural.

With valve passages 65 and 67 arranged alternately, passage b'? s
65 is in constant communication with the current chamber 59, and the passage 67 is in constant communication with the chamber 63. In this example, star 27
Six passages h\f 65 and six passages 67 corresponding to the six external teeth are provided.

The port plate 19 has a plurality of fluid passages 69 ('jj!;1
), and each fluid passageway has 1!
It is arranged so as to be in constant communication with the fluid chamber 29 in contact with A.

A motor of the type shown in Figure 1 is available as an off-the-shelf item and is well known to those skilled in the art; for details of the structure and operation of such a motor, please refer to the above-cited patent specification '4. .

Motor Fixing Device The motor fixing device of the present invention will be described with reference to FIG. 1 as well as FIGS. 2 and 3. As can be seen in FIG. 1.2, the internal toothed ring 23 has a generally radially extending sheath portion 71.

The body part 71 has a radially extending open lower opening 3 which extends radially inwardly and opens into one of the fluid chambers 29 . The open lower part 3 has an inner smooth bore portion 75 and an outer large screw hole portion 77.

Bore portion 75 intersects an axially oriented inverted U-shaped recess 79 (see FIG. 3). Preferably, the recess 79 extends over the entire axial length of the ring 23. An elongated cylindrical fixing member 81 is disposed within the recess 79 . Fixed member 8
1, the opening formed by the intersection of the four parts 79 and the fluid chamber 29 has a circumferential width W smaller than the diameter of the fixing member 81.
(see FIG. 3), so that it is held in the recess 79.

As is clear from FIGS. 2 and 3, the four portions 79 are arranged circumferentially between a pair of internal teeth 25 that are in instant contact. It can also be seen from FIG. 3 that the shape of quadrilateral 79 allows some radial movement of fixation member 81, the purpose of which will be discussed below.

An actuation mechanism 83 is associated with the lower radial volume 3.

The working sag structure s3 has a cylindrical backup member 85 disposed within the bore portion 75. The back-up member 85 has an O-ring member disposed between it and the inner bore portion to completely prevent leakage of fluid through the knock-up member 85 when the fluid chamber 29 in contact with the back-up member 85 contains all the pressurized fluid. Backup section 85 has a surface 87 that engages cylindrical fixation member 81 .

The structure 83 further includes an actuator 8 which is adjacent to the floor 91 of the no.
I have 9. The actuator 89 has a threaded portion 9 that is threadedly engaged with the threaded hole portion 77 of the opening lower lower 3. The actuator 89 also has a serration portion 93 for receiving a nozzle member (not shown) so that movement of the nozzle member causes the actuator 89 to rotate in a radial direction according to the direction of movement of the nozzle. moved either towards or radially outward. Actuator 89 also has another threaded portion 95 that is threadedly engaged with a nut (not shown) for retaining the handle.

Regarding the operation, the operation of the present invention will be described mainly with reference to FIG. In the normal state of the motor, ie when it is desired to cause the star 27 to move in a normal orbit and rotation relative to the ring 23, the fixed part is placed in the inoperative state. This is accomplished by moving the nozzle (not shown) upwardly in FIG. 2 and radially away from star 27.

This movement of actuator 89 allows orbital movement of star 27 and forces fixed member 81 and backup member 85 radially upwardly toward actuator 89. Normally, there is an O-ring surrounding the pull-up member 85 so that the backup member 85 remains in the upper position. However, the fixed member 8
1 can move freely in the radial direction within the recess 79,
Whenever one of the teeth of the star 27 enters the fluid chamber adjacent to the fixing member 81, it first moves radially upwards, bringing this fluid chamber closer to the minimum volume position (see FIG. 3). As star 27 then continues its orbital motion and the adjacent fluid chamber increases in volume, fixing member 81 is free to return radially inwardly to the position shown in FIG. 2 solely by gravity.

Circumstances ξ - When it is desired to actuate a locking mechanism, such as a king brake or a load holding device on a hinge, move the handle completely in the opposite direction and press the actuator 89.
in the opposite direction to move the fixation member radially inward. The inward movement of the actuator 89 due to the threaded engagement between the threaded portion 91 and the threaded hole portion 77 is caused by:
move radially inward. Inward movement of member 85 moves locking member 81 to its radially innermost position as shown in FIG. In this operating state of this device 1,
The fixing member 81 is fixedly maintained in the innermost position, and as the star 27 orbits, one of the outer teeth of the star enters the adjacent fluid chamber. Instead of the external teeth of star 27 causing this fluid chamber to become the smallest fluid chamber as during normal operation, the external teeth engage locking member 81 and are prevented from moving further into the fluid chamber. Further orbital movements relative to the ring, as well as further rotational movements of the star 27, are thus prevented.

As will be understood by those skilled in the art, the above-described mode of operation is similar in other devices, and the star 27 and ring 23
There is relative orbital and rotational movement between the star 27 and the ring 23, regardless of which member moves which. For example, the star may only have an orbital motion and the ring only have a rotational motion, or various other combinations of motions are known. The fixing member of the invention is applicable to devices using any possible combination of relative orbital and rotational motion.

According to the invention, the amount of radial movement of the fixing member 81, actuating mechanism 83 and back-up member 85 between the inoperative state and the operating state is quite small. Generally less than 0.100 inches of radial movement is sufficient, and in this example, only 0.100 inches of radial movement is sufficient.
Only 0,060 inches of movement is required. As will be understood by those skilled in the art, the amount of radial movement required is
Each case is a function of the geometry of that particular zero rotor mechanism.

Embodiment of FIG. 4 Referring now to FIG. 4, which shows an example in which the invention is applied to a rotary fluid pressure device of another type. In the embodiment of this figure, elements the same as or similar to those shown in FIG. 2 are shown with the addition of ioo, and new elements begin with the numeral 101. Internal tooth (cylindrical member 125) fMore internal tooth ring 1
23 is disposed within the housing 101. External tooth star 1
27 is eccentrically disposed within ring 123, and ring 12
The relative orbital and rotational movements between star 127 and star 127 are similar to the embodiment of FIG. However, in the embodiment of FIG. 4, the star 127 only rotates, and the ring 127
3 performs only orbital motion.

Housing 101 has a plurality of semicircular cutouts, each of which receives a roller 103. The ring 123 has a plurality of arcuate cutouts 105 on its outer periphery, each cutout corresponding to one of the rollers 103. As is well known in the art, the flow to and from the expanding and contracting fluid chambers 129 causes the ring 123ff to orbit, while the engagement of the rollers 103 within the notches 105 , preventing the ring 123 from rotating and the star 127
Only rotational movement is allowed.

The housing 101 has an opening 173 that includes a bore portion 175 and a threaded portion 177.
have. An actuation mechanism 183 is disposed within the opening 173;
The mechanism has a backup member 185 with a surface 187.

The actuating mechanism 183 further includes an actuator 189 having a threaded portion 191, a serration portion 193 and another threaded portion 195. All of the above elements may be of the same construction as the corresponding elements in the embodiment shown in FIG.

Actuation mechanism 183 operated similarly to the embodiment of FIG.
Upon activation, the adjacent rollers are moved radially inward, so that this particular roller can also be considered as one identification member 181. When the identification member 181 is in the operating position, normal orbital interlocking of the ring 123 is prevented, and therefore normal rotational operation of the star 127 is also prevented.

Although this embodiment utilizes threaded members to effect radial movement of the fixation members 81, 181, other actuation schemes may also be used. For example, when fluid pressure is applied to the backup member 85
The backup member 85 and the fixing member 81 are moved inward toward the operating position. Various other mechanical means can be used to move the fixation members inwardly, such as wedge members that move in parallel axially. It is also possible to advance the fixing member 81 radially and axially into the fluid chamber.

As will be apparent to those skilled in the art, the present invention provides a simple, inexpensive, and efficient device for securing zero rotor mechanisms such as those used in parking brakes or load retention devices. According to this invention, the above method can be achieved without providing any additional parts to the motor, and as shown in the embodiment of FIG. Same as standard motor. Therefore, according to the present invention, the motor can be completely fixed without substantially increasing the size or weight of the motor or the space that the motor should occupy.

The invention has thus been described in sufficient detail to enable any person skilled in the art to make and use the same. It is believed that those skilled in the art will be able to make various changes and modifications to this invention by reading and understanding this specification, and such modifications are included in this invention as long as they fall within the scope of the claims of this invention. It is something that can be done.

[Brief explanation of the drawing]

1 is a longitudinal sectional front view of an embodiment of the invention, FIG. 2 is a sectional view taken along line 2-2 in FIG. 1, and FIG. 3 is an enlarged view of a portion of FIG. 2. , FIG. 4 is a sectional view similar to FIG. 2 of another embodiment of the invention. 13... Shaft support casing 17... Zero rotor mechanism 19... Port plate 21... Valve housing 23, 123... Inner ring 25, 125...
- Cylindrical members 27, 127...External toothed stars 29, 129...Fluid chamber 31 that expands and contracts...
Output l1Q (l37...141)
Straight K17 spline 39, 43...Outer crown type spline 41...Main drive II1+ 45...Inner linear spline 47, 51...Outer spline 49...Valve drive shaft 53...Inner spline 55. ...Valve member 57...
・Fluid population 61...Fluid outlet 65, 67・
...Valve passage 69...Fluid passage 71, 171.
... Zesu part 73, 173... Open lower 5, 17
5... Inner hole portion 77, 177... Screw hole portion 79... Inverted U-shaped recess 81, 181... Fixing member 83, 183... Operating mechanism

Claims (1)

[Scope of Claims] 1. A housing having a fluid inlet and a fluid outlet, an internal tooth member combined with the housing, and an external tooth member eccentrically disposed within the internal tooth member, one tooth member; performs rotational movement about its axis, the other tooth member performs orbital movement about the axis of one tooth member, and the teeth of both tooth members engage during the rotational and orbital movement to form an enlarged fluid chamber. and a gear mechanism forming a reduced fluid chamber, and one of rotational motion and orbital motion.
an input/output shaft, and an input/output shaft and one of the internal and external toothed members; a torque transmitting member for transmitting torque at a fluid pressure device comprising: (a) a fixing member disposed at least partially within one of the fluid chambers in combination with the internal gear member;
b) a first position in which the fixing member is arranged in combination with the fixing member such that the fixing member allows normal orbital and rotational movement of the tooth member, and the fixing member extends sufficiently into the fluid chamber so that the fluid chamber is when approaching the minimum volume, engaging one of the external teeth of the external toothed member to prevent further orbital movement of the orbiting member;
A rotary fluid pressure device characterized by having an actuation mechanism that moves a fixed part and a member between a second position and a second position that prevents rotation of a rotary member. 2. The internal tooth member has four sections disposed circumferentially between a pair of adjacent internal teeth, and the fixed member is partially disposed within the recess and is radially movable therein. A rotary fluid pressure device according to claim 1, characterized in that: 3. The rotary fluid pressure device according to claim 1, wherein the fixed member is an elongated cylindrical member having an axis parallel to the axis of the rotary member. 4. The actuating mechanism includes an internally toothed member having a generally radially extending aperture and an adjustment member fitting disposed within the aperture, and in response to input movement of the adjustment member. The rotary fluid pressure device according to claim 1, characterized in that the fixing member is moved between the second positions. 5. 1st. The radial interlocking of the fixing member between the second positions is 2
The rotary fluid pressure device according to claim 1, wherein the rotary fluid pressure device is less than 54 inches (0,100 inches).