JPS6151670B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a fluid pressure rotating device known as a hydraulic motor, and more particularly to a transmission mechanism for a fluid pressure rotating device that can change the rotational speed under a constant supply of hydraulic pressure.

Conventionally, hydraulic motors have been utilized in various industrial fields because they have the advantage of generating high torque at low speed rotation, and various hydraulic motors such as piston-type hydraulic motors and gerotor-type hydraulic motors have been put into practical use.

By the way, the rotation of the output shaft in this type of hydraulic motor is uniquely determined by the fluid flow rate flowing into and out of the fluid pressure converter that converts fluid pressure into rotational force, and usually the fluid pressure supply source is Since a constant capacity supply is being carried out, the rotational speed cannot be changed by the hydraulic motor itself, and the speed is changed by a separately installed transmission device, which increases the size of the device and increases the torque loss of the transmission device. Efficiency will decrease.

For this reason, it may be possible to change the speed using the hydraulic motor itself.For example, in piston-type or gerotor-type hydraulic motors, the supply and discharge of fluid to some of the multiple working chambers provided around the rotating shaft may be stopped. There is a known method of adding an external device that disables the
(No. 165636), the mechanism itself is complicated, leading to a significant increase in manufacturing costs.

The present invention has been made in view of the above, and by incorporating a simple switching mechanism into the hydraulic motor itself, fluid pressure can be converted to multiple rotational speeds without impairing the performance of the hydraulic motor. An object of the present invention is to provide a speed change mechanism for a fluid pressure rotating device.

In order to achieve this object, the present invention provides a fluid pressure conversion unit that converts fluid pressure into rotational force by expanding by supplying fluid to a plurality of working chambers arranged around the axis of a rotating shaft and contracting by discharging fluid. and a distribution valve that sequentially switches between supplying and discharging fluid to each of the working chambers of the fluid pressure conversion unit through a number of communication passages corresponding to the working chambers by eccentric movement of a valve body in synchronization with the rotating shaft. In the fluid pressure rotation device, the fluid pressure converting unit and the distribution valve are sandwiched between a pair of fixed members having the communication passage, and are slidably rotatable between a first rotational position and a second rotational position. A rotary switching valve body is provided, and the rotary switching valve body has a first valve hole provided so as to communicate between the opposing communication passages of the fixed member at the first and second rotational positions, and a first rotational switching valve body. a second valve hole provided to communicate between the opposing communication passages of the fixed member at the position and to close the communication passage of the fixed member on the distribution valve side at the second rotational position; Accordingly, the communication passage of the fixing member on the side of the fluid pressure converting unit that faces the communication passage closed at the second rotational position is provided with a communication groove that communicates with the communication passage.

Hereinafter, the present invention will be explained based on the drawings.

FIG. 1 is a partial sectional view showing a case where an embodiment of the present invention is applied to a gerotor type hydraulic motor.

First, to explain the configuration, reference numeral 1 is a gerotor-type fluid pressure converter, and a stator member 2 is provided with a plurality of internal teeth inside, and a rotor member has external teeth one less than the internal teeth. 3 are eccentrically engaged with each other, and the rotor member 3 is connected to the output shaft via a spline shaft 4. In this embodiment, the number of internal teeth of the stator member 2 is nine, and the number of external teeth of the rotor member 3 is one less than eight. Therefore, nine interdental gaps serving as working chambers are formed between the stator member 2 and the rotor member 3.

The conversion action of the gerotor type fluid pressure converter 1 is as follows:
As shown in Japanese Patent Publication No. 43-21325, among the plurality of interdental gaps formed by the stator member 2 and the rotor member 3, high-pressure fluid is supplied to the part that expands due to the rotation of the rotor member 3, and contracts. The rotor member 3 is rotated by discharging the fluid from the portion where the rotor member 3 rotates, and this rotation is extracted to the outside.

The fluid is supplied to and discharged from the fluid pressure converter 1 by means of a distribution valve provided in the casing section 5.

This distribution valve consists of a casing member 6 and a swinging valve body 7 accommodated in a valve chamber A inside the casing member 6. A valve drive shaft 9 is connected to the spline shaft 4 by a drive pin 8 for dynamic movement.
The eccentric shaft portion 9a is loosely fitted into the eccentric shaft portion 9a, and the eccentric shaft portion 9a has an eccentric direction with a predetermined phase difference with respect to the eccentric direction of the rotor member 3.

Further, when the swinging valve body 7 is eccentrically rotated by the valve drive shaft 9, the swinging valve body 7 rotates in a direction opposite to the rotation direction of the eccentric shaft.
The valve body 7 tries to rotate, but the swinging valve body 7 has a gear shape with a plurality of externally toothed protrusions 7a on the outer circumference, and the inner surface of the casing member 6 corresponds to the protrusions 7a. is provided with a half-moon-shaped guide receiving portion 6a, and sliding contact between the protrusion 7a and the guide receiving portion 6a in the eccentric direction of the swinging valve body 7 prevents rotational movement of the swinging valve body 7. There is. That is, the swinging valve body 7 performs only an eccentric swinging motion in synchronization with the eccentric rotation of the rotor member 3.

In this way, since the swinging valve body 7 does not rotate, the valve hole B for discharging the fluid from the shrinking interdental gap of the fluid pressure converter 1 is adjusted by the number of interdental gaps. (9 locations in this embodiment) are provided independently corresponding to each other.

The distribution valve used in the present invention has a structure that prevents the above-mentioned valve body from rotating, and also has a structure that prevents the valve body from rotating.
As shown in No. 21325, an annular valve body is used in which annular grooves that communicate with each other are provided as valve holes on both sides of the valve body, and the positional deviation of the valve hole due to rotation of the valve body is offset by the annular groove. It may also be a distribution valve.

A lid member 10 defining one side of the distribution valve is provided with a fluid inlet 11 and a fluid outlet 12. The fluid inlet 11 communicates with an outer annular groove 13 provided on the sliding surface with the distribution valve. , the fluid outlet 12 communicates with the inner annular groove 14 .

Switching of the fluid to the fluid pressure converting unit 1 by the distribution valve is performed by switching the fluid to the expanding portion of the fluid pressure converting unit 1 through the fluid inlet 11, the outer annular groove 13, and the valve chamber A of the distribution valve (swinging valve body 7). The high pressure fluid is supplied through the gap between the casing member 6 and the casing member 6,
The fluid in the contracting portion of the fluid pressure converting section 1 flows through the valve hole B of the swinging valve body 7 of the distribution valve and the inner annular groove 1.
4, and is discharged to the outside via the fluid outlet 12.

The expanding portion and the contracting portion of the fluid pressure conversion unit 1 are sequentially shifted in a predetermined rotational direction by eccentric rotation of the rotor member 3, and the distribution valve is configured to move the supply passage so as to follow the movement of the expanding portion and the contracting portion. and the discharge passages are sequentially switched.

In the present invention, for the gerotor type hydraulic motor having the above-mentioned configuration, the fluid pressure converter 1 and the distribution valve (casing section 5) are connected by switching the fluid passage connecting the two. A speed change mechanism is provided to change the rotation speed.

As shown in FIG. 1, the communication passage 15 connecting the distribution valve 5 and the fluid pressure converting section 1 is composed of three members stacked on top of each other in the axial direction.
6 and 17 are the numbers of interdental gaps in the fluid pressure converter 1;
In this embodiment, the number of communication passages is nine, so the switching valve plate 18 is a pair of fixed plates in which nine communicating passages corresponding to this number are independently provided in an annular shape. is installed so that it can rotate freely. The switching valve plate 18 has a drive lever 19 planted on its circumferential surface, and the drive lever 19 is connected to a switching handle 21 via a link member 20 with a shaft 22.
By operating the handle 21, the switching valve plate 18 is driven to rotate around the axis.

This transmission mechanism is shown in FIG.
It has a shaft hole 23 for the valve drive shaft 9 in the center, and nine communication passages 15 facing the interdental gap of the fluid pressure converting part 1 are arranged in an annular manner at equal intervals on the fixed plates 16 and 17 on both sides. The central switching valve plate 18 is provided with a plurality of valve holes as shown in left and right end views in FIGS. 3 and 4.

In other words, the third
Referring to the figure, valve holes 24 having a shape matching the communication passages 15 of the fixed plate 16 shown by dotted lines are provided at positions where nine valve passages 15 are equally divided into three, and the communication passages 15 located between the valve holes 24 The valve hole 25 facing the connecting passage 15 is an oblong valve hole that is elongated in the circumferential direction and exceeds the diameter of the communication passage 15.

The switching rotation angle Θ of the switching valve plate 18 is regulated to be, for example, Θ = 2π/2n, where n is the number of communication passages, and since n = 9 in this embodiment, the rotation angle Θ should be Θ=20°.

As a result, in the illustrated switching position a, the switching valve plate 18
The valve holes 24 and 25 of the fixed plate 1 facing each other are
All communication passages 15 of 6 and 17 are communicated with each other.
In the switching position b, the valve hole 24 is removed from the communication passage 15 of the opposing fixed plates 16 and 17 and closes the communication passage 15, but since the valve hole 25 is oval, the communication passage 15 maintains the communication state similar to the switching position a.

Furthermore, the left end surface of the switching valve plate 18 has a switching position b.
Branch grooves 26 and each branch groove 26 are arranged radially at three locations in order to communicate with each other the communicating passages 15 of the fixed plate 16 that were opposite to the valve hole 24 that is closed when the switch is switched to
An annular groove 27 is provided to connect the two.

An annular groove 28 is provided on the right end surface in FIG. 4, and the annular grooves 27 and 28 are communicated through a through hole 29.
7 (including the branch grooves 26) are provided in order to balance the fluid pressure applied to the switching valve plate 18 and smoothly rotate the switching valve plate 18.

FIG. 5 shows the transmission mechanism according to the above embodiment using a fluid circuit, in which the fixed plates 1 located on both sides
6 and 17, only the communication passages 15 thereof are shown arranged in an annular shape, and the communication passages 15 are shown in the shaded area.
A indicates a communication passage that is always in communication regardless of the switching position of the switching valve body, and the communication passage 15b is communicated with the switching valve plate at one switching position (the position shown in the figure) and is connected at the other switching position. It shows a communication path where communication with each other is cut off at a certain point. As is clear from the arrangement of the illustrated communication passages 15a and 15b,
In this embodiment, among the nine communication passages, the communication passages 15a are grouped by two, and this group is equally divided into three and arranged at equal intervals, with the remaining communication passages 15b being switched intermittently.

Further, the switching valve plate 18 surrounded by dotted lines constitutes a three-circuit switching valve, and is switched up and down by the switching handle 21, and is at the position shown in the drawing, connecting the connecting passage 15b where the fixed plates 16 and 17 face each other. At the other switching position pulled upward, the communication passages 15b of the fixed plates 16 and 17 are separated, and the communication passages 15b of the fixed plates 16 are communicated with each other. Of course, in an actual transmission mechanism, the switching by moving the switching handle 21 up and down in FIG. 5 is realized by rotating the switching valve plate 18.

Next, the speed change operation of the gerotor type hydraulic motor by the speed change mechanism shown in FIGS. 2 to 5 will be explained.

First, in the illustrated switching position a, all the communication passages between the distribution valve and the fluid pressure converter are in communication, so that low-speed rotation with high torque commensurate with the fluid supply amount Q (equal to the discharge amount) is possible. It is transmitted to the output shaft. The rotation speed at this time is Na.

Next, if the switching valve plate 18 is switched to the switching position b, three of the nine communication passages are closed, as is clear from the circuit of FIG. The interdental spaces of the parts are communicated with each other, and no fluid is supplied to or discharged from the distribution valve.

As a result, the number of interdental gaps in the fluid pressure converter used to convert fluid pressure into rotational force is reduced from nine to six. On the other hand, since the supply flow rate Q is constant, the rotation of the rotor member increases, and the rotational speed Nb at that time theoretically increases to a rotational speed such that Nb=1.5Na, and the rotation is switched to low torque and high speed rotation.

FIG. 6 is a circuit diagram of a transmission mechanism showing another embodiment of the present invention, in which three of the nine communication passages 15a are always connected, and the remaining six communication passages 15b are connected to the switching valve plate. 18, and the rotation speed Na when all the communication passages are connected is changed to the rotation speed Nb when six of them are closed, which is three times the rotation speed Nb = 3Na. I can do it.

The structure of the switching valve plate 18 for realizing the transmission mechanism shown in FIG. 6 is shown in left and right end views in FIGS. 7 and 8.

That is, the valve holes facing the communication passage 15a in FIG. The valve holes 24 having the same diameter are grouped into groups of two, and the groups are provided at three locations at equal intervals.

Further, on the left end surface of FIG. 7, which is the side of the fluid pressure converter, when the switching valve plate 18 is rotated from the illustrated position a to another switching position b, there is a communication passage on the fluid pressure converter side. A communication groove consisting of radially arranged branch grooves 26 and an annular groove 27 is provided to communicate the communication passages 15a of the fixed plate 16 shown in FIG. 6 with each other.

Furthermore, on the right end surface of FIG. 8 facing the distribution valve side,
An annular groove 28 is provided for pressure balancing, and this annular groove 28 communicates with an annular groove 27 on the left end surface through a through hole 29 to balance the hydraulic pressure applied to both sides of the switching valve plate 18. ing.

FIG. 9 shows another embodiment of the present invention in which the transmission ratio is 2:1, using a fluid circuit, and the number of communication passages is an even number of six. Therefore, in the fluid pressure converter of the gerotor type hydraulic motor shown in FIG.
By making the stator member 2 have 6 internal teeth and the rotor member 3 having 5 outer teeth, which is one less, the number of interdental gaps formed is 6, which is the same as the number of communication passages. There is.

According to the embodiment shown in FIG. 9, if the rotational speed when all the communication passages 15a and 15b are in communication at the illustrated switching position is Na, the communication passage 15b is separated and the interdental space of the fluid pressure converting section is The rotational speed Nb when the supply and discharge of fluid to half of the working chamber is stopped is Nb=2Na, and a gear ratio of 2:1 is obtained by the hydraulic motor itself.

FIG. 10 similarly shows another embodiment of the present invention using a fluid circuit, in which four communication passages 15a are always in communication and four communication passages 15b are disconnectable.
In this way, a gear ratio of 2:1 is similarly obtained, and the stability of the output torque is improved compared to the embodiment shown in FIG.

For this reason, the fluid pressure converter 1 of the gerotor type hydraulic motor shown in FIG. Eight matching interdental spaces are formed.

In this way, the valve hole of the switching valve body constituting the transmission mechanism is connected to a constantly communicating passage through communication passages corresponding to the number of interdental gaps (working chambers) that expand or contract in the fluid pressure converter. By determining the ratio with the passage, any gear ratio can be achieved.

FIG. 11 shows a switching mechanism for the switching valve plate 18 used in the transmission mechanism of the present invention, and the embodiment shown in FIG. 1 shows a switching mechanism operated manually.
This embodiment shows an example of a switching mechanism using hydraulic control.

That is, the drive rod 19 installed on the switching valve plate 18
The piston 31 accommodated in the cylinder tube 30
The advance of the piston 30 is performed by supplying pressure oil from the control pressure port 32, and the return of the piston 31 is caused by the repulsive force of the spring 33 to make the control pressure port 32 exhaust pressure. I'm trying to make sure that things are done accordingly. Note that 34 is an escape port when the piston 31 advances, and 35 is a blind cover that closes one side of the cylinder tube 30.

By providing such a hydraulically controlled switching mechanism for the switching valve body 18, the speed change control of the hydraulic motor can be performed remotely.

FIG. 12 shows an embodiment in which the transmission mechanism of the present invention is applied to a piston motor.

The piston motor is provided with a plurality of pistons 37 in a cylinder block 36 disposed around an output shaft 41, and a reciprocating movement of the pistons 37 is obliquely provided by sequentially switching the supply and discharge of fluid to and from the cylinder chamber 36a using a distribution valve 38. The distribution valve 38 is converted into the rotational force of the output shaft 41 via the swathshier plate 39 and the yoke 40, and the distribution valve 38 is eccentrically rotated in synchronization with the output shaft 41 by the eccentric shaft 42, similar to a gerotor type motor. It is an annular valve body,
The flow paths are sequentially switched so that fluid is supplied to the expanding cylinder chamber 36a and fluid is discharged from the contracting cylinder chamber 36a. Therefore, the number of communication passages 15 corresponding to the number of pistons 37 is provided between the distribution valve 38 and the cylinder block 36.

Therefore, similar to the gerotor type motor, the fluid passage 1 between the cylinder block 36 and the distribution valve 38 is
A transmission mechanism having a rotatable switching valve plate 18 sandwiched between fixed plates 16 and 17 is provided in the section 5, and the position of the switching valve plate 18 is changed by a switching handle 21, so that an arbitrary transmission ratio can be set. It is possible to realize a piston motor with

The structure and operation of this transmission mechanism are as shown in each of the above embodiments described for the gerotor type motor.

As explained above, according to the present invention, the configuration is provided with a switching valve body that selectively connects and disconnects the communication passage between the fluid pressure conversion part of the gerotor type motor or piston motor and the distribution valve. The conversion function can be changed by increasing or decreasing the number of working chambers in the fluid pressure converter by separating a part of the fluid pressure converter, so the transmission mechanism can be changed to It can be easily incorporated into the motor itself, and the transmission mechanism itself can be configured to any desired transmission ratio with a simple configuration, and can be switched between high-torque, low-speed rotation and low-torque, high-speed rotation by manual or remote control. This provides the advantage that a so-called two-speed hydraulic motor that can perform the following functions can be realized at a relatively low manufacturing cost.

Furthermore, in the present invention, by integrally providing the rotation switching valve body inside the motor, the following unique effects can be obtained compared to a case where a switching device is provided externally.

First, since the rotary switching valve body is installed inside the motor, there is no need for piping connections like when it is installed externally, and there is no loss due to piping connections. Since the motor is installed externally and connected to piping, the motor and its surroundings become complicated, but the present invention requires only the motor unit, and the overall device configuration can be made compact.

Second, when a high-pressure type hydraulic motor that uses a rotary type distribution valve is equipped with an external directional control valve, the number of piping connections increases significantly, and because of the high pressure, oil leaks occur at the connections. However, since it is installed internally in the present invention, it is exactly the same as a hydraulic motor without a speed change mechanism, and even under high pressure, the piping system The reliability of reliability can be guaranteed.

Furthermore, compared to a hydraulic motor that does not have a speed change mechanism, a rotary switching valve body is provided inside, and the passages for the distribution valve and fluid pressure conversion section are minimized to minimize the distance between the distribution valve and the fluid pressure conversion section. A rotary switching valve body is provided between the rotary switching valve body and the rotary switching valve body, and even if the rotary switching valve body is installed, the flow path is only longer by the width of the rotary switching valve and the fixed plates on both sides compared to a hydraulic motor that does not have a speed change mechanism. This allows the efficiency of fluid pressure utilization to be maximized.

Furthermore, first and second portions provided on the rotary switching valve body
The valve holes are arranged in an annular manner so that every other valve hole is equally spaced, or the first valve holes of one or more groups are equally spaced from the second valve holes of one or more groups. By alternately arranging them in an annular manner, the speed ratio can be set to an arbitrary value depending on the relationship with the number of working chambers of the fluid pressure converting section.

In addition, as a unique effect of the embodiments of the present invention, the switching valve body is of a balanced type in which the same force acts on both sides, so even when switching high pressure, the switching movement is smooth, and the switching valve body is smooth when switching high pressure. Since the valve body does not tilt, leakage from the rotary switching valve body can be minimized and conversion efficiency can be maintained at its maximum.

[Brief explanation of the drawing]

Fig. 1 is a sectional view showing an embodiment of the transmission mechanism of the present invention incorporated in a gerotor type hydraulic motor, Fig. 2 is a sectional view showing the transmission mechanism of Fig. 1 taken out, and Fig. 3 is the transmission mechanism. Figure 4 is a right end view of the switching valve body used in
Figure 6 is a fluid circuit diagram of a transmission mechanism with a gear ratio of 1:1.5. Figure 6 is a fluid circuit diagram of a high-speed mechanism with a gear ratio of 1:3. Figures 7 and 8 are fluid circuit diagrams of a transmission mechanism with a gear ratio of 1:3. Fig. 9 is a fluid circuit diagram showing another embodiment of the present invention in which a gear ratio of 1:2 is obtained.
The figure is a fluid circuit diagram showing another embodiment of the present invention in which a gear ratio of 1:2 is obtained by increasing the efficiency of output torque, and Figure 11 is a switching mechanism used in the gear shift mechanism of the present invention using hydraulic control. Partial sectional view showing 1st
FIG. 2 is a sectional view of a piston motor incorporating the transmission mechanism of the present invention. 1...Fluid pressure converter, 2...Stator member,
3...Rotor member, 4...Spline shaft, 5...
Casing section (distribution valve), 6... Casing member, 6a... Guide receiving part, 7... Rocking valve body, 7a...
...Protrusion, 8...Drive pin, 9...Valve drive shaft, 9a
... Eccentric shaft portion, 10 ... Lid member, 11 ... Fluid inlet, 12 ... Fluid outlet, 13, 14 ... Annular groove, 15, 15a, 15b ... Communication passage, 16,
17... Fixed plate, 18... Switching valve plate, 19... Drive lever, 20... Link member, 21... Switching handle, 22... Shaft, 23... Shaft hole, 24... Valve hole, 25... ... Valve hole (oval), 26 ... Branch groove, 2
7, 28... annular groove, 29... through hole, 30...
Cylinder tube, 31... Piston, 32... Control pressure port, 33... Spring, 34... Relief port,
35...Blind lid, 36...Cylinder block, 36
a... Cylinder chamber, 37... Piston, 38...
Distribution valve, 39...Swatshire plate, 40...
Yoke, 41...output shaft, 42...eccentric shaft.

Claims (1)

[Claims] 1. A fluid pressure converter that converts fluid pressure into rotational force by expanding by supplying fluid to a plurality of working chambers disposed around the axis of the rotating shaft and contracting by discharging fluid; A fluid pressure rotation device comprising: a distribution valve that sequentially switches the supply and discharge of fluid to each of the working chambers of the fluid pressure conversion unit through a number of communication passages corresponding to the working chambers by synchronized eccentric movement of the valve body; In the apparatus, a rotating member is provided between the fluid pressure converter and the distributing valve and is sandwiched between a pair of fixed members having the communication passage so as to be slidably rotatable between a first rotational position and a second rotational position. A switching valve body is provided, and the rotary switching valve body is provided with a first rotary switching valve body.
and a first valve hole provided to communicate between opposing communication passages of the fixed member at a second rotational position;
a second valve hole provided so as to communicate between the opposing communication passages of the fixed member in the first rotational position and close the communication passage of the fixed member on the distribution valve side in the second rotational position; A fluid pressure rotation device comprising: a communication groove that communicates with the communication passage of the fixed member on the side of the fluid pressure converting unit facing the communication passage closed at the second rotation position by the second valve hole; Transmission mechanism. 2. The fluid pressure rotation according to item 1, wherein the rotary switching valve body is arranged in an annular manner such that the first valve hole and the second valve hole are arranged at equal intervals every other valve hole. The transmission mechanism of the device. 3. The rotary switching valve body is characterized in that first valve holes formed in one or more groups and second valve holes formed in one or more groups are arranged in an annular shape alternately at equal intervals. A transmission mechanism for a fluid pressure rotating device.