JPH0225034B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an impeller type torque motor, and in particular, an impeller-type torque motor having an inner hole surrounded by a cam inner circumferential surface defining a plurality of pressure medium reservoirs spaced apart from each other in the circumferential direction on a concentric circle. a cam member having; a rotary piston that is rotatably arranged in the inner hole of the cam member and slidably supports a plurality of blade members in sliding contact with the inner circumferential surface of the cam in the radial direction; a pair of side closing flanges that close openings on both sides; a cam of a cam member having both side surfaces defined by the pair of side closing flanges and an inner circumferential surface in the radial direction defined by the outer circumferential surface of the rotating piston; a first opening communicating with one end in the circumferential direction of each of the plurality of pressure operation chambers constituted by the plurality of pressure medium reservoirs on the inner peripheral surface;
a second opening communicating with the other end in the circumferential direction of each pressure operating chamber, and a first opening and a first opening of each pressure operating chamber selected from among the plurality of pressure operating chambers in various predetermined combinations. pressure medium control means for selectively introducing and deriving the pressure medium or deriving and introducing the pressure medium into the openings of 2, and the pressure medium is selectively introduced into the plurality of pressure operation chambers selected by various predetermined combinations. A pressure medium is introduced through either the first opening or the second opening corresponding to each of the plurality of pressure operation chambers, and the pressure medium is introduced through the other of the first opening or the second opening. is introduced from the selected plurality of pressure operating chambers, and the pressure of the pressure medium is applied to the blade member in the selected plurality of pressure operating chambers to move the rotary piston in a desired direction in a desired stepwise manner. a rotary piston rotation control means for rotating the rotary piston at a rotational speed and rotational torque; a rotary piston rotation control means disposed between one side closing flange and the rotary piston, and located on the side remote from the rotary piston; an intermediate disk with a compensating pressure adapting surface area on its side facing the inner side; compensating pressure adapting means for loading the compensating pressure adapting surface area with a pressure medium during rotation of the rotary piston; and an impeller-type torque. Regarding motors.

The conventional impeller type torque motor of the kind described above is specifically constructed as follows.

That is, the rotating piston has a plurality of narrow grooves extending in a direction along the rotation center line on its outer peripheral surface at predetermined intervals, and each of these narrow grooves has a groove that slides in the radial direction of the rotating piston. A plate-shaped blade member is arranged so as to be freely movable. The plurality of blade members have their outer ends abutted in the radial direction against the cam inner peripheral surface of the cam member surrounding the rotary piston from the outside in the radial direction. A sealed state is created between the inner circumferential surface and the outer end of the vane member, and a space is defined between each of the vane members, the height of which changes in the radial direction as the inner circumferential surface of the cam changes in the radial direction. A pair of side closing flanges are connected to both side surfaces of the cam member in the direction along the rotation center line, and these create a sealed state of the space in the direction along the rotation center line. The radially inward boundary of said space is defined by the outer peripheral surface of the rotary piston, and the rotary piston has a boundary between said space between a pair of side closing flanges and a pair of side closing flanges. It is possible to rotate freely with only a very small gap in order to reduce leakage.

The inner circumferential surface of the cam is curved so as to gently protrude outward in the radial direction, and has a plurality of substantially concentric pressure fluid reservoirs for accommodating pressure fluid, such as pressurized oil. The fluid reservoir is communicated with a pressure fluid inflow passage and a pressure fluid outflow passage at both ends in the circumferential direction.

The pressure fluid introduced into said space in a plurality of pressure fluid reservoirs to rotate the rotary piston and acting on the vane members of the rotary piston is also applied to the inner ends of the plurality of slots for the vane members of the rotary piston. A vane member is urged radially outward during rotation of a rotary piston to cause the outer end of the vane member to slide on the inner circumferential surface of the cam. However, in certain situations, the pressure fluid introduced into the inner end of the plurality of narrow grooves of the rotary piston and the centrifugal force generated during the rotation of the rotary piston alone cannot move the blade member onto the inner peripheral surface of the cam. Since it will not be enough to make it slide,
A spring is disposed at the inner end of each of the plurality of grooves for biasing the vane member radially outwardly to ensure that the outer end thereof always slides on the inner circumferential surface.

Normally, the number of pressure fluid reservoirs on the inner circumferential surface of the cam is
2 to 6 in order to balance the pressure of the pressure fluid on the outer peripheral surface of the rotating piston.

The aforementioned pressure fluid inflow passage and pressure fluid outflow passage for each pressure fluid reservoir extend in a direction along the rotation center line at one of the pair of side closing flanges.

In a known impeller-type torque motor, one of a pair of side closing flanges functions as a holding flange for rotatably supporting a rotary piston, and the other functions as a holding flange for rotatably supporting a rotating piston, and the other functions as a holding flange for introducing pressure fluid into a plurality of pressure fluid reservoirs. The flange functions as a control flange provided with a pressure fluid control means for controlling the flow and the derivation. The holding flange holds a roller bearing that rotatably supports the rotating piston, and between the holding flange and the rotating piston there is a support flange for supporting the rotating piston in the direction along the rotation center line. An intermediate disk is arranged to perform the operation.

In order for the rotary piston to rotate in the inner hole surrounded by the cam inner peripheral surface of the cam member, the rotary piston and 1
The gap set between the pair of side closing flanges is such that the dimension (width) of the rotating piston in the direction along the rotation center line is smaller than the dimension (width) of the cam inner peripheral surface in the above direction. The smaller the above-mentioned gap is, the more the leakage of pressure fluid from the pressure fluid reservoir through the above-mentioned gap can be prevented, and the operating efficiency of the impeller type torque motor can be improved. The aforementioned intermediate disk has an annularly formed compensating surface area on its side facing away from the rotary piston and facing the inner side of the retaining flange. A portion of the pressure fluid introduced into the pressure fluid reservoir is guided into this compensating surface area, which actuates the intermediate disk to reduce the above-mentioned gap and to prevent the rotating piston from seizing against the intermediate disk. . A portion of this pressure fluid is further introduced into the inner ends of the plurality of narrow grooves for the plurality of blade members of the rotary piston, as described above.

Even so, any lubricating oil or pressure fluid that leaks from the tiny gaps that must exist on both sides of the rotating piston is discharged through separate pipes.

The rotary piston has a central hole machined with involute internal teeth, to which the input shaft of a machine driven by an impeller-type torque motor can be easily connected. The rotating piston then transmits rotational torque to the input shaft.

An impeller-type torque motor is a constant-speed motor that rotates only at a substantially constant rotational speed due to a constant flow of pressure fluid such as oil, and a motor that rotates at a substantially constant rotational speed by a control valve that changes the rotational speed in stages by switching the suction capacity in stages. They can be basically classified into two types: variable speed motors that can be changed to different speeds.

A known impeller type constant speed torque motor can also be used as a pump by connecting the output shaft of an external torque generating means such as an electric motor to the center hole of the rotary piston. In this case, a known impeller type constant speed torque motor can be used for the brake.

JP-A-50-4467, which claims priority to West German Patent Publication No. 2228506, discloses an impeller type variable speed torque motor. Six pressure fluid reservoirs are formed on the cam inner peripheral surface of the cam member of this impeller type variable speed torque motor, and the six pressure fluid reservoirs have two types of suction amounts V ₁ and V ₂ in the circumferential direction. have alternately. As a result, in the variable speed torque motor as a whole, the following three levels of suction amount can be selected by using the three positions of the control valve.

The first position of the control valve...suction amount V ₁ ×3 The second position of the control valve...the suction amount V ₂ ×3 The third position of the control valve…the suction amount (V ₁ +V ₂ )×3 Here, the pressure fluid The unsuctioned pressurized fluid reservoir is communicated with the pressurized fluid outlet of the variable speed torque motor, thereby only causing circulation of substantially unpressurized pressure fluid. The energy loss that occurs in the impeller type variable speed torque motor at this time is only approximately as small as the energy loss that is lost from the gear pair rotating without load in the gear mechanism.

In the impeller type variable speed torque motor, the control valves for selecting the suction amount at each stage as described above can be operated not only manually but also by using liquid pressure or gas pressure.

Conventional impeller-type torque motors have been able to rotate a rotary piston in only one predetermined direction, but for example, in ground bore devices, a torque motor that can equally rotate in both directions is desired.

However, in a conventional impeller-type torque motor, the compensating surface of the intermediate disk is provided in the same number as the pressure fluid reservoirs, so that it is difficult to modify the conventional impeller-type torque motor so that it can rotate equally in both directions. is an impeller-type torque motor in which the roles of the pressure fluid inlet passage and the pressure fluid return passage are reversed every time the direction of rotation is changed.
It is necessary to form two communication holes for each pressure fluid reservoir to communicate each pressure fluid reservoir with both of the two pressure fluid passages, and each pressure fluid reservoir has two communication holes corresponding to the two communication holes of each pressure fluid reservoir. A check valve must be provided to prevent the pressure fluid return passage from communicating with the pressure fluid reservoir when the pressure fluid passage functions as a pressure fluid return passage. For example, in order to modify the impeller type variable speed torque motor described in the above-mentioned publication so that it can rotate equally in both directions, since this impeller type variable speed torque motor has six pressure fluid reservoirs, a total of 12 reverse rotations are necessary. A communication hole with a stop valve shall be provided.

This invention was made based on the above circumstances, and an object of the invention is to reduce the number of check valves that must be used when the rotational speed and rotational torque can be changed and the rotation can be reversed. Another object of the present invention is to provide an impeller type torque motor that has a simple configuration and can reduce manufacturing costs.

In order to achieve the purpose of this invention as mentioned above,
An impeller-type torque motor according to the present invention includes: a cam member having an inner hole surrounded by a cam inner circumferential surface defining a plurality of pressure medium reservoirs spaced apart from each other in the circumferential direction on a concentric circle; a rotary piston that is rotatably arranged in the hole and slidably supports a plurality of blade members in sliding contact with the inner circumferential surface of the cam in the radial direction; a pair of sides that close openings on both sides of the inner hole of the cam member; a plurality of pressure medium reservoirs on the inner circumferential surface of the cam of the cam member whose both sides are defined by the pair of side closing flanges and whose inner circumferential surface in the radial direction is defined by the outer circumferential surface of the rotating piston; a first opening that communicates with one circumferential end of each of the plurality of pressure operating chambers; a second opening that communicates with the other circumferential end of each of the pressure operating chambers;
Pressure medium control means for selectively introducing and leading out or introducing a pressure medium into the first opening and the second opening of each pressure operation chamber selected from among the plurality of pressure operation chambers in various predetermined combinations; , and one of a first opening and a second opening corresponding to each of the selected plurality of pressure operating chambers in the plurality of pressure operating chambers selected by various predetermined combinations. The pressure medium is introduced through the selected plurality of pressure operation chambers through the first opening and the second opening, and the pressure medium is led out of the selected plurality of pressure operation chambers through the other of the first opening and the second opening. a rotary piston rotation control means for applying the pressure of a pressure medium to a vane member in a pressure operation chamber to rotate the rotary piston in a desired direction at a desired stepwise rotational speed and rotational torque; one side closing flange; The rotary piston is disposed between the rotary piston and the rotary piston, and is provided concentrically with respect to the rotational center line of the rotary piston on a side surface facing the inner surface of the one side closing flange and located far from the rotary piston. an intermediate disc with at least two annular compensating pressure adapting surface areas;
at least two pressure-operating chambers belonging to a group of two smallest units and at least two annular shapes of the intermediate disc are provided between the compensating pressure-accommodating surface area, one circumferential end of the at least two pressure-operating chambers; communicates with one of the at least two compensation pressure adaptable surface regions via respective check valves, and both ends of the other of the at least two pressure operating chambers in the circumferential direction are connected to one of the at least two compensation pressure adaptable surface regions. Compensation pressure adaptation means communicated with the other via check valves, respectively.

In the impeller-type torque motor according to the present invention configured as described above, the two check valves facing both ends in the circumferential direction of each of the at least two pressure operation chambers are arranged so as to correspond to the ends thereof. one compensating pressure adaptation surface area, in which the check valve on the side of one of the first openings and the second opening used for the introduction of the pressure medium receives the pressure medium from the pressure operating chamber into which the pressure medium is introduced; to be introduced. Further, the pressure medium is introduced from one compensating pressure adapting surface region corresponding to the check valve on the other opening side of the first opening and the second opening corresponding to the two ends, which is used for leading out the pressure medium. This prevents the pressure medium from flowing out into the corresponding pressure operating chamber.

In the impeller type torque motor of the invention, the number of compensating pressure adapting surface areas can be much smaller compared to the number of pressure working chambers, so that two are required for each compensating pressure adapting surface area. The total number of check valves can be made much smaller than in the conventional method described above.

An annular compensating pressure concentric to the rotation center line of the rotary piston is provided on both sides of the intermediate disk, located on the side facing away from the rotary piston and facing the inner surface of the one lateral closing flange. It is easy to form multiple (at least two) adaptive surface areas.

The reduction in the number of check valves that must be used and the ease of forming the compensating pressure accommodating surface area simplify the construction of the impeller torque motor and thus reduce manufacturing costs.

In the impeller type torque motor of the present invention, the at least two compensating pressure adapting surface areas are such that in the above-described predetermined combination of the plurality of pressure operating chambers, the pressure operating chambers belonging to mutually different minimum unit groups have mutually different suction capacities. If so, it is preferable that the pressure operating chambers belonging to different minimum unit groups have effective surfaces of different dimensions corresponding to the difference in suction capacity.

Hereinafter, one embodiment of the present invention will be described in detail with reference to the accompanying drawings.

The housing 2 of the impeller type torque motor 1 according to one embodiment includes a cam member 8 having an inner hole defined by the inner peripheral surface of the cam, and an inner hole of the cam member 8 fixed on both sides of the cam member 8. It is provided with a holding flange 9 and a control flange 1 that cover the openings on both sides.

A rotary piston 6 is disposed in the inner hole of the cam member 8, and the rotary piston 6 is attached to a retaining flange 9.
It is rotatably supported in the inner hole by a bearing held in the inner hole. A center hole with internal spline teeth is formed at the center of rotation of the rotary piston 6, and an input shaft 5 of a device driven by the rotational force generated by the impeller-type torque motor 1 transmits the rotational force to the center hole. connected to receive.

On the outer peripheral surface of the rotary piston 6, a large number of radial grooves extending in a direction along the rotation center line of the rotary piston 6 are formed at a large number of positions spaced apart at predetermined intervals in the circumferential direction. A large number of blade members 7, 7', 7'', . , 7'', . 7', 7'', . . . slide their respective outer ends on the cam inner peripheral surface of the cam member 8.

A plurality of pressure medium suction spaces that are gently curved and protrude outward in the radial direction at positions equidistantly spaced from each other in the circumferential direction on the cam inner surface of the cam member 8 are formed by the outer circumferential surface of the rotary piston 6. By defining the inner surface in the radial direction and defining both side surfaces in the direction along the rotation center line of the rotary piston 6 by the control flange 1 and the holding flange 9,
A pressure operating chamber is created.

The control flange 1 is provided with a pressure medium inlet 3 and a pressure medium outlet 4, and is connected to one end in the circumferential direction of each of the plurality of pressure operation chambers from a direction along the rotation center of the rotary piston 6. First openings 11, 13, 1 having broad bean-shaped cross sections
5, 17, 19, 21, and second openings 12, 14, 16 having a bean-shaped cross section and communicating with the other ends in the circumferential direction of each of the plurality of pressure operation chambers from the direction along the rotational center line. , 18, 20, and 22 are provided.

The control flange 1 is provided with first openings 11, 13, 15, 17, in order to rotate the rotary piston 6 at different rotational speeds or different rotational torques.
19, 21 and second openings 12, 14, 16, 1
8, 20, 22 selectively to the pressure medium inlet 3 or the pressure medium outlet 4. In this embodiment, the control valve 23 connects the first
to a third position manually or pneumatically or hydraulically.

When the control slider 24 is placed in the first position, in this embodiment, six control sliders are defined at equal intervals from each other in the circumferential direction between the cam inner surface of the cam member 8 and the outer peripheral surface of the rotary piston 6. 1 in a pressure operating chamber
three second openings 14 opening at one end in the circumferential direction of the three pressure operation chambers arranged every other day;
18 and 22 communicate with the pressure medium inlet 3, and three first openings 13, 17, and 21 open at the other end in the circumferential direction of the three pressure operation chambers communicate with the pressure medium outlet 4. Ru. During this time, three second openings 12, 16, 20 and three first openings 11 open at both ends of the remaining three pressure operation chambers,
15 and 19 are communicated with the pressure medium outlet 4 so that the pressure medium in the remaining three pressure operation chambers does not affect the rotation of the rotary piston 6. The rotary piston 6 rotates counterclockwise in FIG. 1 at a predetermined speed and with a predetermined torque.

When the control slider 24 is placed in the second position, the three second openings 12,1 open at one end in the circumferential direction of the remaining three pressure operation chambers mentioned above.
6 and 20 communicate with the pressure medium inlet 3, and three first openings 11, 15, and 19 that open at the other end in the circumferential direction of the remaining three pressure operation chambers communicate with the pressure medium outlet 4. be done. During this time, the three second openings 14, 18, 22 and the three first openings 13, 17, 21, which are open at both ends of the three pressure operation chambers mentioned above, are connected to the pressure medium outlet 4. By communicating with each other, the pressure medium in the above-mentioned three pressure operation chambers is prevented from affecting the rotation of the rotary piston 6.

Here, the remaining three pressure working chambers described above have a different pressure medium suction amount from the previous three pressure working chambers, so that the rotary piston 6 is controlled so that the control slider 24 Compared to the case where the rotor is placed at the same position, it rotates at a predetermined different rotational speed and rotational torque even in the same rotational direction.

When the control slider 24 is disposed at the third position between the first position and the second position, all six pressure operation chambers are open at one end in the circumferential direction. two second openings 12,
14, 16, 18, 20, 22 are pressure medium inlets 3
The six first openings 11, 13, 15, 17, 19, and 21, which are open at the other end in the circumferential direction in all six pressure operation chambers, are communicated with the pressure medium outlet 4. Ru. As a result, the rotary piston 6 rotates at a predetermined different rotational speed and rotational torque even in the same rotational direction compared to when the control slider 24 is disposed at the first and second positions described above. .

An intermediate disk 25 is arranged between the rotating piston 6 and the holding flange 9. intermediate disk 2
5 is movable only a small distance in the direction along the rotational center line of the rotary piston 6 between the above-mentioned positions.

On one side (outer side) of the intermediate disk 25 located far from the rotary piston 6 and facing the holding flange 9, there are two concentric first and second concentric rings extending in an annular shape in the circumferential direction. Compensating surface areas 26, 27 are provided. In this embodiment, the first and second compensating surface areas 26, 27 are constituted by grooves on one side (outer side) of the intermediate disk 25,
The openings of these grooves are sealed against the inner surface of the holding flange 9 by sealing means provided on the inner surface of the holding flange 9 or on the outer surface of the intermediate disk 25.

In the intermediate disk 25 are two check valves which communicate the radially inwardly located first compensating surface area 26 with the circumferential ends of one of the three previously mentioned pressure chambers. 30, 31 and a radially outwardly located second compensating surface area 27 as described above.
Two check valves 28, 29 are also provided which communicate with both circumferential ends of one pressure working chamber. These two pairs of check valves 30, 31 and 28, 29 in the intermediate disk 25 are connected to the control flange 1.
0, two pairs of second and first pairs each opening at both circumferential ends of the corresponding pressure operation chamber.
The openings 13, 14 and 15, 16 are opposed to each other in the direction along the rotation center line of the rotary piston 6.

Each of the two pairs of check valves 30, 31 and 28, 29 has a second or first opening 13, which faces each other.
14, 15, 16 are connected to the pressure medium inlet 3, the second or first openings 13,
A pressure medium is introduced from 14, 15, 16 into the respective first or second compensation surface area 26 or 27. At this time, the other check valve that is paired with the check valve communicating with the pressure medium inlet 3 is connected to the pressure medium outlet 4.
Because it communicates with the first or second
Pressure medium is prevented from being led off from the compensating surface area 26 or 27 of the pressure medium outlet 4 .

To explain in more detail, the control slider 24 of the control valve 23 is arranged in the first position to open the three second openings 14, 18, 22 corresponding to the three pressure operating chambers mentioned above and the three first opening 13,1
7 and 21, the pressure medium from the pressure medium inlet 3 is introduced into the above-mentioned three pressure operation chambers and is led out to the pressure medium outlet 4, whereby the above-mentioned three pressures are When the rotary piston 6 subjected to the action of pressure medium on the blade members 7, 7', 7'', etc. in the operating chamber rotates counterclockwise in FIG. 1 at a predetermined speed and a predetermined torque, the above-mentioned A first compensating surface area 26 in the radial direction, which is communicated via a pair of check valves 30, 31 with one pressure operating chamber included in the previous three pressure operating chambers, is provided with said one pressure. Pressure medium inlet 3 in the working chamber
Pressure medium from the pressure medium inlet 3 is introduced from one check valve 30 facing the second opening 14 communicating with the second opening 14 . During this time, the other check valve 31, which is opposite the first opening 13 communicating with the pressure medium outlet 4 in the one pressure working chamber, uses the pressure difference to divert the pressure medium in the first compensating surface area 26 to the first pressure medium outlet 4. Opening 13
There is no discharge to the pressure medium outlet 4 via the pressure medium outlet 4.

When the control slider 24 is placed in the first position, the radially outer second compensation surface areas 27 and 1
1 communicated via a pair of check valves 28 and 29.
three pairs of second and first openings 1 corresponding to the remaining three pressure-operating chambers, including the three pressure-operating chambers;
1, 12, 15, 16 and 19, 20 are in communication with the pressure medium outlet 4, so that the second compensating surface area 2
7, no pressure medium is introduced from the pressure medium inlet 3.

Therefore, the rotary piston 6 and the holding flanges 9 and control flanges 10 on both sides of the rotary piston 6 in the direction along the rotation center line of the rotary piston 6.
The compensation between .

Next, the control slider 24 of the control valve 23 is placed in the second position to open the three second openings 12, 16, 20 corresponding to the remaining three pressure operating chambers mentioned above.
and the three first openings 11, 15, 19, the pressure medium from the pressure medium inlet 3 is introduced into the remaining three pressure working chambers mentioned above and is led out to the pressure medium outlet 4. Accordingly, the blade members 7, 7',
Rotating piston 6 subjected to the action of pressure medium at 7″...
When rotates counterclockwise in FIG. 1 at a predetermined speed and a predetermined torque, the remaining three
A radially outward second compensating surface area 27, which is in communication with one of the pressure operating chambers contained in the two pressure operating chambers via a pair of check valves 28, 29, One check valve 2 facing the second opening 16 communicating with the pressure medium inlet 3 at
8, the pressure medium from the pressure medium inlet 3 is introduced. During this time, the other check valve 29, which is opposite the first opening 15 which communicates with the pressure medium outlet 4 in the one pressure working chamber, diverts the pressure medium in the second compensating surface area 27 due to the pressure difference to the first pressure medium outlet 4. There is no outlet to the pressure medium outlet 4 via the opening 15 .

When the control slider 24 is placed in the second position, the radially inward first compensating surface areas 26 and 1
1 communicated via a pair of check valves 30 and 31.
three pairs of second and first openings 1 corresponding to the aforementioned three pressure operating chambers including three pressure operating chambers;
3, 14, 17, 18 and 21, 22 are connected to the pressure medium outlet 4, so that the first compensating surface area 2
6, no pressure medium is introduced from the pressure medium inlet 3.

Therefore, in this case, the correction of the distance between the rotary piston 6 and the holding flanges 9 and control flanges 10 on both sides of the rotary piston 6 in the direction along the rotation center line of the rotary piston 6 is corrected by the holding flanges. This is done solely by the pressure of the pressure medium introduced into the second compensating surface area 27 of the intermediate disk 25 of 9.

Next, the control slider 24 of the control valve 23 is placed in the third position to open the six second openings 12, 14, 16, 18, corresponding to all six pressure operating chambers.
20, 22 and six first openings 11, 13, 1
Pressure medium inlet 3 via 5, 17, 19, 21
The pressure medium from is introduced into all six pressure working chambers and led to the pressure medium outlet 4, so that the vane members 7, 7', 7'', the rotary piston 6 under the action of the pressure medium exerts a torque which can be obtained by arranging the control slider 24 in the first and second positions in the counterclockwise direction in FIG. When rotated with a total value of torque and a predetermined speed, a pair of check valves 28 and 29 are installed in each of the two pressure operation chambers included in the six pressure operation chambers.
and a radially outer second compensating surface area 27 and a radially inner first compensating surface area 26 which communicate via 30, 31 with the pressure medium inlet 3 in the two pressure working chambers. Pressure medium from the pressure medium inlet 3 is introduced through one of the check valves 28 and 30 facing the second openings 16 and 14 that communicate with each other. During this time, the other check valves 29 and 31, which are opposite the first openings 15 and 13 communicating with the pressure medium outlet 4 in the two pressure working chambers, are opened due to the pressure difference between the second compensating surface area 27 and the first opening. The pressure medium in the compensation surface area 26 is not led out via the first openings 15 and 13 to the pressure medium outlet 4 .

In the impeller type torque motor 1 of this embodiment, regardless of whether the control slider 24 of the control valve 23 is placed in any of the first to third positions, the rotary piston 6 is moved to the opposite position as described above. It can be rotated clockwise in Figure 1. In this case, the functions of the pressure medium inlet 3 and pressure medium outlet 4 of the control flange 10 are reversed.
Therefore, six first openings 11 or 13 or 15
or six second openings 1 into which pressure medium is introduced from either 17 or 19 or 21 into their corresponding pressure working chambers and which communicate with pressure medium inlets 3 which are to serve as pressure medium outlets.
2 or 14 or 16 or 18 or 20 or 22 from these corresponding pressure working chambers. In addition, the first
and a second opening communicates with a pressure medium inlet 3 which is to function as a pressure medium outlet.

The rotary piston 6 obtained by arranging the control slider 24 at each of the first to third positions when the rotary piston 6 is rotated in the clockwise direction in FIG. The rotational speed and rotational torque can be obtained by arranging the control slider 24 at each of the first to third positions when the rotary piston 6 is rotated in the counterclockwise direction in FIG. 1 as described above. The rotational speed and rotational torque of the rotating piston 6 are the same.

Furthermore, even when the rotary piston 6 is rotated in the clockwise direction in FIG.
1, the first and second compensating surface areas 2
The pressure of a pressure medium can be applied to 6 and 27. In this case, two pairs of check valves 3 corresponding to the first and second compensation surface areas 26 and 27 are provided.
The roles played by the check valves 30, 31 and 28, 29 in each of the pairs 0, 31 and 28, 29 are reversed from those in the case where the rotary piston 6 is rotated counterclockwise in FIG. 1 as described above. It goes without saying that you should.

That is, when the control slide 24 is placed in the first position in the case of rotating the rotating piston 6 in the clockwise direction in FIG. Valve 3
1 from the pressure medium outlet 4 which is to function as a pressure medium inlet, and another non-return valve 30 in which the pressure medium in the first compensating surface area 26 is to function as a pressure medium outlet. This prevents the pressure medium from being led out to the actual pressure medium inlet 3.

Also, when the rotary piston 6 is rotated in the clockwise direction in FIG. valve 2
9, pressure medium is introduced from the pressure medium outlet 4, which is to act as a pressure medium inlet, and another check valve 28 allows the pressure medium in the first compensating surface area 26 to function as a pressure medium outlet. This prevents the pressure medium from being led out to the actual pressure medium inlet 3.

When the control slide 24 is placed in the third position in the case of rotating the rotary piston 6 in the clockwise direction in FIG. The pressure medium from the pressure medium outlet 4, which is to function as a pressure medium inlet, is introduced from the check valves 31 and 29 corresponding to both of them, respectively.
Further check valves 30 and 31 respectively corresponding to both compensating surface areas 26 and 27 serve as pressure medium outlets for the pressure medium in the first and second compensating surface areas 26 and 27. This prevents the pressure medium from being led out to the pressure medium inlet 3.

The first and second compensating surface areas 26, 27 are formed in the intermediate disk 25, as shown in FIG.
7'', . , 33, the outer ends of the plurality of blade members 7, 7', 7'', . , 7', 7'', . . . effectively prevents pressure medium from leaking between the outer end and the inner circumferential surface of the cam.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of an impeller-type torque motor according to an embodiment of the present invention, excluding the intermediate disk and retaining flange; FIG. 2 is a cross-sectional view taken along the line - in FIG. FIG. 1... Impeller type torque motor, 2... Housing, 3... Pressure medium inlet, 4... Pressure medium outlet,
5... shaft, 6... rotary piston, 7, 7', 7'',
...Blade member, 8...Cam member, 9...Holding flange, 10...Control flange, 11, 13, 1
5, 17, 19, 21...first opening, 12, 1
4, 16, 18, 20, 22...second opening, 2
3... Control valve, 24... Control slider, 25...
Intermediate disc, 26...first compensation surface area, 27...
...Second compensation surface area, 28, 29, 30, 31
...Check valve, 32, 33...hole.

Claims (1)

[Scope of Claims] 1. A cam member having an inner hole surrounded by a cam inner peripheral surface defining a plurality of pressure medium reservoirs spaced apart from each other in the circumferential direction on concentric circles; a rotary piston that slidably supports a plurality of vane members that are freely arranged and slidably contact the inner peripheral surface of the cam in the radial direction; a pair of side closing flanges that close openings on both sides of the inner hole of the cam member; ; A plurality of pressure medium reservoirs constituted by a plurality of pressure medium reservoirs on the cam inner circumferential surface of the cam member whose both side surfaces are defined by a pair of side closing flanges and whose inner circumferential surface in the radial direction is defined by the outer circumferential surface of the rotary piston; A first opening communicating with one circumferential end of each pressure operating chamber, a second opening communicating with the other circumferential end of each pressure operating chamber, and various pressure operating chambers selected from among the plurality of pressure operating chambers. pressure medium control means for selectively introducing and deriving the pressure medium or deriving and introducing the pressure medium into the respective first openings and second openings of the pressure operation chambers selected by a predetermined combination of; Introducing the pressure medium into the plurality of pressure operation chambers selected by various predetermined combinations through either the first opening or the second opening corresponding to each of the selected plurality of pressure operation chambers. At the same time, the pressure medium is led out of the selected plurality of pressure operation chambers through the other of the first opening and the second opening. a rotary piston rotation control means for applying pressure to the vane member to rotate the rotary piston in a desired direction at a desired stepwise rotational speed and rotational torque; disposed between one side closing flange and the rotary piston; at least two annular compensations arranged concentrically with respect to the center of rotation of the rotary piston on the side facing the inner surface of the one lateral closing flange and located on the side facing away from the rotary piston; an intermediate disc with a pressure-accommodating surface area; at least two pressure-working chambers belonging to at least two groups of minimal units different from each other in the above-mentioned predetermined combination of a plurality of pressure-working chambers; and at least two of the intermediate discs; and an annular compensating pressure adapting surface area, and communicating both circumferential ends of one of the at least two pressure operating chambers to one of the at least two compensating pressure adapting surface areas via check valves, respectively. and a compensating pressure adapting means for communicating the other ends of the at least two pressure operating chambers in the circumferential direction with the other of the at least two compensating pressure adapting surface regions via respective check valves; , two check valves corresponding to both ends in the circumferential direction of each of the at least two pressure operation chambers are used for introducing the pressure medium out of the first opening and the second opening corresponding to the both ends. A check valve on one opening side introduces the pressure medium from the pressure working chamber into which the pressure medium is introduced into a corresponding one compensating pressure adaptation surface area, and a first opening and a second The non-return valve on the other side of the opening, which is used for the discharge of the pressure medium, allows the pressure medium to be discharged from the corresponding compensation pressure adaptation surface area into the corresponding pressure working chamber into which the pressure medium has been introduced. An impeller-type torque motor characterized by preventing. 2. The impeller type torque motor according to claim 1, wherein the at least two compensation pressure adapting surface areas have mutually different pressure receiving areas. 3. The pressure-operating chambers according to claim 1 or 2, wherein the pressure-operating chambers belonging to each group of the minimum unit combination of a plurality of pressure-operating chambers have mutually different dimensions. Impeller type torque motor. 4 In the above-mentioned predetermined combination of a plurality of pressure operation chambers, there are two groups of mutually different minimum units.
4. The impeller type torque motor according to any one of claims 1 to 3, characterized in that the total number of compensation pressure adapting surface areas is two. 5. The impeller type according to claim 4, wherein the two groups of minimum units can be used independently of each other and can be used simultaneously with each other. torque motor. 6. The total number of the pressure operation chambers is 6, and the 2.
Each of the two smallest unit groups has three pressure operation chambers arranged every other place in the circumferential direction, and the two groups each having three pressure operation chambers are mutually connected to each other. can be used both independently and simultaneously with each other,
An impeller type torque motor according to claim 4, characterized in that: