KR100334211B1 - Stroke Torque Generator of Hydraulic Torque Wrench - Google Patents

Abstract

According to the present invention, in addition to providing a strike torque generating device of a hydraulic torque wrench, which has a small sliding resistance, good energy efficiency, a low temperature rise of the working oil, a stable output, small size, simple structure, and durability. The hydraulic torque wrench has a blow torque generating device (5) having a hollow portion and two or more even (2n) seal surfaces (11a) and (11b) in a pair, and a liner rotated by a rotor ( 11) and two or more n-protrusions 15a and 15b, the main shaft 9 being coaxially installed inside the liner 11, and the seal of the liner 11 described above near both ends. The seal surfaces corresponding to the surfaces 11a and 11b are retained, are fitted into the hollow portions of the liner 11, and abut the protrusions 15a and 15b of the main shaft 9. 2 or more n-driven blades 14a, (1) to generate the strike torque to the spindle 9 by 4b) and the like.

Description

Strike Torque Generator of Hydraulic Torque Wrench

The present invention relates to a striking torque generating device of a hydraulic torque wrench.

As a torque torque generating device of a torque wrench, a hydraulic torque wrench using a hydraulic blow torque generating device with low noise and vibration has been developed and put into practical use.

FIG. 21 shows an example of the hydraulic torque wrench, and the hydraulic torque wrench 1 is used for selectively generating the main valve 2 for supplying and stopping the high pressure air and the strike torque for forward and reverse rotation. It holds a forward and reverse rotation switching valve (3), and drives the rotor which generates the rotation torque by the high pressure air transmitted from these valves (2) and (3). Then, the hydraulic strike torque generating device 5 for converting the rotational torque of the rotor 4 into the strike torque is provided in the front case 6 protruding to the distal end of the hydraulic torque wrench 1. The hydraulic strike torque generating device 5 is provided with a liner 8 in the liner case 7, and seals the hydraulic oil in the liner 8 and fits the same axis in the liner 8. 9) One or more wing insertion grooves are installed, and the blades are inserted into the wing insertion grooves, and the wings are always applied with a spring in the main circumferential direction to contact the inner circumferential surface of the liner 8 One or more seal surfaces are formed in the outer peripheral surface of the main shaft 9. In addition, the liner 8 is provided with an output adjusting mechanism 10 for adjusting the magnitude of the striking torque.

Then, when the liner 8 is rotated by the rotor 4, a plurality of seal surfaces formed on the inner circumferential surface of the liner 8 and seal surfaces formed on the circumferential surface of the main shaft 9 coincide with each other. (9) to generate a strike torque.

By the way, in the case of the conventional torque torque generating device of the hydraulic torque wrench, one or more wing insertion grooves are provided in the main shaft 9, the blades are inserted into the wing insertion grooves, and the blades are always circumferentially circumferentially with springs. Since the structure adopts a configuration in which the force is applied to the inner circumferential surface of the liner 8, the energy loss due to the sliding resistance between the tip of the blade and the inner circumferential surface of the liner 8 is large, and the frictional heat generated by the sliding. By the temperature of the hydraulic fluid rises, there was a problem that the output of the torque wrench fluctuated by the viscosity change of the hydraulic fluid.

In addition, since it is necessary to provide a hole for inserting a wing insertion groove or a spring in the main shaft 9, since the strength of the main shaft 9 is maintained, the diameter of the main shaft 9 must be increased. In addition to the increase in size, the structure of the device is complicated, and there is a problem in the durability of the device such as a spring breakage.

The present invention, in view of the above problems of the conventional hydraulic torque wrench hitting torque generating device, while sliding the spring to always apply a force in the circumferential direction of the main shaft from the hydraulic torque wrench hitting torque generating device, sliding, It is an object of the present invention to provide a striking torque generating device for a hydraulic torque wrench, which has a small resistance, excellent energy efficiency, low temperature rise of the hydraulic oil, stable output, small size, simple structure, and durability.

In order to achieve the above object, the strike torque generating device of the hydraulic torque wrench of the present invention has a hollow portion and four or more even (2n) seal surfaces in a pair of two, and by the rotor A liner to be rotated, having at least two n-protrusions, a main shaft coaxially installed inside the liner, and a seal surface corresponding to the seal surface of the liner near both ends thereof, the cavity of the liner The gist of the present invention is composed of two or more n drive blades which are inserted into the negative parts and generate hitting torques on the main shafts by contacting the projections of the main shafts.

In addition, the hitting torque generating device of the hydraulic torque wrench of the third invention of the present invention has a hitting torque generating device of the hydraulic torque wrench of the first invention, wherein each seal face of the liner is 360 / n degrees with each seal face. The gist is formed so as to generate n strike torques on the main shaft with respect to one rotation of the liner by forming at positions that are rotationally symmetrical.

In the strike torque generating device of the hydraulic torque wrench of the third aspect of the present invention, in the strike torque generating device of the hydraulic torque wrench of the first invention, the seal surfaces of two sets of liners are each 360 / n degrees. It is formed in the position where the rotation is symmetrical, and a groove for releasing the hydraulic oil is formed on the inner surface of the liner cover and the side of the drive blade in sliding contact with the liner cover, thereby making one stroke torque per one rotation of the liner. It is made into the summary that it is made to generate | occur | produce in the

In the strike torque generating device of the hydraulic torque wrench of the fourth aspect of the present invention, in the strike torque generating device of the hydraulic torque wrench of the first invention, the seal surfaces of two sets of liners are 360 / n degrees each other. The gist is formed so as to generate one strike torque on the main shaft with respect to one rotation of the liner by being formed at a position where rotation asymmetry is achieved.

In the hit torque generating device of the hydraulic torque wrench of the fifth aspect of the present invention, the hit torque generating device of the hydraulic torque wrench of the first aspect of the present invention is characterized in that two seal sets of liners each have a seal surface of 36 / n degrees. Formed at the position to be rotationally symmetrical, in addition to the inner surface of the liner cover to form a guide groove by eccentric with the axis of rotation of the liner, by forming a pin to be inserted into the guide groove on the side of the drive blade in sliding contact with the liner cover, The gist of the present invention is to generate one strike torque on the main shaft with respect to one revolution of.

The striking torque generating device of the hydraulic torque wrench according to the first aspect of the present invention has a main shaft when a plurality of seal surfaces formed on the inner circumferential surface of the liner and seal surfaces formed near both ends of the driving blade coincide with each other by rotating the liner by the rotor. Generates a strike torque at

The striking torque generating device of the hydraulic torque wrench according to the second aspect of the present invention includes a plurality of seal faces and driving blades in the vicinity of both ends of a plurality of seal surfaces formed at positions where rotational symmetry is 360 / n degrees with respect to the inner circumferential surface of the liner by rotating the liner by the rotor. The seal face formed at the same position is matched n times with respect to one rotation of the liner, and at this time, n strike torques are generated with respect to one rotation of the liner on the main shaft.

The strike torque generating device of the hydraulic torque wrench according to the third aspect of the present invention is provided with a plurality of seal surfaces and driving blades near the ends of the plurality of seal surfaces formed at positions where rotational symmetry is 360 / n degrees with respect to the inner circumferential surface of the liner by rotating the liner by the rotor. The seal face formed at the inner side of the seal line is n-matched with respect to one rotation of the liner, and the hydraulic oil is moved from the groove formed in the inner surface of the liner cover and the side of the drive blade in sliding contact with the liner cover except one time, Generate one stroke torque per one revolution of the liner on the spindle.

The striking torque generating device of the hydraulic torque wrench according to the fourth aspect of the present invention is provided with a plurality of seal surfaces and driving blades in the vicinity of the rotational asymmetry of 360 / n degrees on the inner circumferential surface of the liner while rotating the liner by the rotor. The seal face formed at the same position is matched once with respect to one rotation of the liner, and at this time, one strike torque is generated with respect to one rotation of the liner on the main shaft.

The hitting torque generating device of the hydraulic torque wrench according to the fifth aspect of the present invention is provided with a plurality of seal surfaces and driving blades in a position where the rotational symmetry is 360 / n with respect to the inner circumferential surface of the liner while the liner is rotated by the rotor. The seal surface formed on the inner surface of the liner cover is eccentric with the rotation axis of the liner, and the movement of the drive blade is regulated by the pin of the drive blade inserted into the guide groove formed. One blow torque is generated for each revolution of the liner.

(Example)

The following will be described on the basis of the illustrated embodiment the striking torque generating device of the hydraulic torque wrench of the present invention.

1 to 6 show a first embodiment of the striking torque generating device of the hydraulic torque wrench of the present invention.

The basic structure of the hydraulic torque wrench itself of this embodiment is the same as the conventional hydraulic torque wrench shown in FIG. 15, and this hydraulic torque wrench 1 is provided with a main valve 2 for supplying and stopping high pressure air. It has a forward rotation switching valve (3) for selectively generating the forward torque of the forward and reverse rotation, and drives the rotor (4) generating the rotation torque by the high pressure air delivered from the valve (2), (3) do. A hydraulic strike torque generating device 5 for converting the rotational torque of the rotor 4 into the strike torque is provided in the front case 6 protruding from the tip of the hydraulic torque wrench 1.

The hydraulic striking torque generating device 5 of this embodiment installs the liner 11 into the liner case 7, seals and seals the hydraulic oil into the liner 11, and coaxially forms the main shaft 9 in the liner 11. ).

In the liner 11 to which the main shaft 9 is fitted, a hollow is formed in the shape of an ellipse inside, and four seal surfaces 11a and 11b are formed on the inner circumferential surface in a set of two in the form of a mountain. One set of seal surfaces, that is, the seal surface 11a and the seal surface 11b, are formed at positions that become rotationally symmetrical by 180 degrees.

The cylindrical liner 11 is supported on its outer circumference by a liner case 7, and the upper liner cover 12 and the lower liner cover 13 are provided at both ends of the liner 11, and the liner 11 is provided. With the upper liner top cover 12 and the lower liner bottom 13, the pin holes provided in the liner 11 and the pin holes 12a and 13a provided in the upper liner top cover 12 and the liner lower cover 13 By inserting the rust pin 17 into), it is configured to rotate integrally. Then, the liner upper cover 12 is further fixed in the liner case cover 7a in the axial direction to seal the hydraulic oil filled into the liner 11.

In the main shaft 9 provided coaxially inside the liner 11, two projections 15a and 15b formed in a smooth shape on the surface are formed at positions to be rotationally symmetrical by 180 degrees.

The two projections 15a and 15b of the main shaft 9 are formed to have a length in the axial direction and the circumferential direction shorter than the hollow inside the liner 11, so that the hydraulic oil is provided at both ends in the axial direction and the tip in the circumferential direction. It is configured to form a passage through which.

Two driving blades formed in the liner 11 and formed into a hollow defined by the protrusions 15a and 15b of the main shaft 9 having a smooth surface in the shape of a triangle having a substantially triangular cross section. Insert 14a and 14b.

The two driving blades 14a and 14b have an axial length such that the side surfaces of the driving blades 14a and 14b are in sliding contact with the inner surfaces of the upper liner cover 12 and the lower liner cover 13. It is formed to have substantially the same length as the hollow inside of the liner 11, and forms seal surfaces corresponding to the seal surfaces 11a and 11b of the liner 11 near both ends thereof, The sealing surfaces 11a and 11b of the liner 11 and the sealing surfaces of the driving blades 14a and 14b coincide twice in one rotation.

On the outer circumferential surface of the liner 11, it becomes the low pressure chamber L inside the liner 11 partitioned by the drive blades 14a and 14b and the seal surfaces 11a and 11b of the liner 11. Install a communication groove 16 communicating the hollow with each other.

In addition, the liner 11 is provided with an output adjusting mechanism 10 for adjusting the magnitude of the striking torque in parallel to the axis center of the liner 11. The output adjustment mechanism 10 is known in the prior art and is a high-pressure chamber inside the liner 11 partitioned by the drive blades 14a and 14b and the seal surfaces 11a and 11b of the liner 11 and the like. Outputs that are adjustable and screwed into ports 10a and 10b communicating hollows (H) and hollows (L) and screw holes (13b) provided in the liner bottom cover (13). The control valve 10c etc. are comprised.

In the first embodiment, two seals 11a and 11b provided in the liner 11 and two projections 15a and 15b provided in the main shaft 9 are provided. And the two driving blades 14a and 14b, the strike torque generating device 5 is constituted. However, the number of seal surfaces to be mounted on the liner is not limited thereto, and the strike torque generating device is provided to the liner. It can be composed of two or more even (2n) seal surfaces of six or more, three or more n protrusions provided on the main shaft, three or more n driving wings, and the like. n strike torques can be generated.

Next, the operation of the striking torque generating device 5 of the hydraulic torque wrench of the first embodiment will be described.

First, when the main valve 2 and the switching valve 3 are operated to introduce high pressure air into the rotor chamber in the main body 1, the rotor 4 rotates at high speed. The rotational force of this rotor is transmitted to the liner 11.

By the rotation of the liner 11, the inside of the liner case 7 changes as shown in Figs. 6 (a) → (b) → (c) → (d) → (a). FIG. 6 (a) shows a state in which no striking torque is generated on the main shaft 9, where the liner 11 is rotated by approximately 90 degrees (b), (c) and (d). Mark on.

Strike torque is generated in the main shaft 9 when it is shown in FIG. 6 (b) and (d), and the seal of the seal surface 11a, 11b and the drive blades 14a and 14b of the liner 11 is shown. The surface coincides, the hollow inside the liner 11 is divided into four chambers, and in the hollow shape inside the liner 11, at the moment when the torque is generated to the main shaft 9, the high pressure chamber H side The volume of is decreased, the volume of the low pressure chamber (L) side is increased, and each chamber becomes a high pressure chamber (H) and a low pressure chamber (L). That is, when the liner 11 is rotated by the rotor 4 to reach a position coinciding with the seal surfaces 11a and 11b of the liner 11 and the seal surfaces of the driving blades 14a and 14b. Each chamber becomes a high pressure chamber (H) and a low pressure chamber (L), and the driving blades (14a) and (14b) are pressed toward the low pressure chamber (L) side, so that the seal surface (11a) of the liner (11), The sealing surfaces of the 11b and the drive blades 14a and 14b coincide with each other, and the hollow inside the liner 11 is completely blocked, so that the rotational force of the liner 11 is driven by the drive blades 14a and 14b. ) Acts on the protruding portions 15a and 15b of the main shaft 9, and generates a striking torque on the main shaft 9; Then, the main shaft 9 is rotated by an intermittent impact torque generated twice per one rotation of the liner 11 to perform a desired operation such as tightening or loosening a bolt or nut.

On the other hand, when it is shown to FIG. 6 (a) and (c), it approaches to the position where the sealing surface 11a, 11b of the liner 11 and the sealing surface of the drive blades 14a, 14b match. When the respective chambers are brought into the high pressure chamber H and the low pressure chamber L at the moment, the seal surfaces 11a of the liner 11 are pressed while the driving blades 14a and 14b are pressed toward the low pressure chamber L side. ), (11b) and the sealing surfaces of the driving blades (14a), (14b) do not match, the hollow inside the liner 11 is not blocked, and the high pressure chamber (H) side and the hydraulic oil are Since it flows to the low pressure chamber L side through a clearance gap, the striking torque does not generate | occur | produce to the main shaft 9.

In addition, when the rotor 4 is rotated in the opposite direction, the interior of the liner case 7 changes as shown in FIG. 6 (d) → (c) → (b) → (a) → (d). , The main shaft (9) can generate a strike torque in the opposite direction to the first.

7 to 12 show a second embodiment of the hydraulic torque wrench striking torque generating device of the present invention.

The basic structure of this embodiment is the same as that of the first embodiment described above.

The hydraulic strike torque generating apparatus 5 of this embodiment installs the liner 21 into the liner case 7, fills and seals the hydraulic oil into the liner 21 and coaxially in the liner 21. Insert it.

In the liner 21 to which the main shaft 9 is fitted, a hollow which is substantially elliptical is formed inside, and four seal surfaces 21a and 21b are formed on the inner circumferential surface in a pair of two in a mountain shape. One set of seal surfaces, that is, the seal surface 21a and the seal surface 21b, is formed at a position that becomes rotationally symmetrical by 180 degrees.

The cylindrical liner 21 is supported by the liner case 7 and its outer circumference is provided with the liner upper cover 22 and the liner lower cover 23 at both ends of the liner 21, and the liner 21 and With the liner upper cover 22 and the liner lower cover 23, the pin holes provided in the liner 21 and the pin holes 22a and 23a respectively provided in the liner upper cover 22 and the liner lower cover 23, respectively. By inserting the rust pin 27 into), it is configured to rotate integrally. The liner upper cover 22 is further fixed in the liner case cover 7a in the axial direction to seal the hydraulic oil filled into the liner 21.

In addition, the inner surfaces of the liner upper cover 22 and the liner lower cover 23 are provided with grooves 28a and 28b for moving the hydraulic oil at predetermined positions.

In the main shaft 9 provided coaxially inside the liner 21, two projections 25a and 25b, each having a smooth surface, are formed at a position that becomes rotationally symmetrical by 180 degrees.

The two projections 25a, 25b of the main shaft 9 are formed to have a length in the axial direction and the circumferential direction shorter than the hollow inside the liner 21, so that the hydraulic oil is provided at both ends in the axial direction and the tip in the circumferential direction. It is configured to form a passage through which.

Two driving blades formed into the liner 21 and formed into a hollow defined by the protrusions 25a and 25b of the main shaft 9 having a smooth surface in the shape of a cross section having a substantially triangular shape and having the same size. Insert 24a and 24b.

The two driving blades 24a and 24b have an axial length such that the side surfaces of the driving blades 24a and 24b are in sliding contact with the inner surfaces of the upper liner cover 22 and the lower liner cover 23. It is formed to be substantially the same length as the hollow inside of the liner 21, and forms the seal surface corresponding to the seal surface 21a, 21b of the liner 21 near the both ends, and the drive blade 24a. , Grooves 29a and 29b for moving the hydraulic fluid to both end surfaces of the line 24b, and the seal surfaces 21a and 21b of the liner 21 and the driving blades for one rotation of the liner 21. The seal surfaces of 24a and 24b coincide twice, one of which is the grooves 28a and 28b formed on the inner surfaces of the upper liner cover 22 and the lower liner cover 23 and the driving blades. The hydraulic fluid is moved from the outflow grooves 29a and 29b formed at both end surfaces of the 24a and 24b, so that one stroke torque is generated per one rotation of the liner 21 on the main shaft 9. do.

In addition, in this embodiment, grooves 28a and 28b for moving the hydraulic oil are formed on both inner surfaces of the liner upper cover 22 and the liner lower cover 23, but the grooves are formed on the liner upper cover 22 or It may be provided only on either side of the liner lower cover 23, and in this case, a groove for moving the hydraulic oil to the corresponding one surface of the driving blades 24a and 24b is formed.

On the outer circumferential surface of the liner 21, the low-pressure chamber L inside the liner 21 partitioned by the drive blades 24a and 24b and the seal surfaces 21a and 21b of the liner 21 is used. A communication groove 26 communicating with the hollow is installed.

In addition, the liner 21 is provided with an output adjusting mechanism 10 for adjusting the magnitude of the striking torque in parallel with the axis of the liner 21. The output adjustment mechanism 10 is known in the art and has a high pressure inside the liner 21 partitioned by the drive blades 24a and 24b and the seal surfaces 21a and 21b of the liner 21 and the like. Adjustable screwing into the ports (10a), (10b) and the screw holes (23b) provided in the liner lower cover (23) to communicate the hollows of the chamber (H) and the hollows of the low pressure chamber (L) An output adjustment valve 10c or the like.

In addition, the second embodiment described above includes four seal surfaces 21a, 21b, two protrusions 25a, 25b, which are provided on the liner 21, and four seal surfaces 21a, 21b. Although the strike torque generating device 5 is constituted by the two driving blades 24a and 24b, the number of seal surfaces to be mounted on the liner is not limited thereto, and the strike torque generating device is provided on the liner. Two pairs of six or more even (2n) seal surfaces, three or more n protrusions provided on the main shaft, three or more n driving wings, and the like can be configured. A larger hit torque can be obtained while generating one hit torque.

In this case, by forming grooves for moving the proper shape and the appropriate number of hydraulic fluids at appropriate positions on the inner surface of the liner upper cover and the lower liner lower cover, it is possible to generate an appropriate number of strike torques for one revolution of the liner on the spindle. Can be.

Next, the operation of the striking torque generating device 5 of the hydraulic torque wrench of the second embodiment will be described.

First, when the main valve 2 and the switching valve 3 are operated to introduce high pressure air into the rotor chamber in the main body 1, the rotor 4 rotates at high speed. The rotational force of this rotor is transmitted to the liner 21.

By the rotation of the liner 21, the inside of the liner case 7 changes as shown in Fig. 12 (a)-(b)-(c)-(d)-(a). FIG. 12 (a) shows a state in which the striking torque is not generated in the main shaft 9, where the liner 21 is rotated by approximately 90 degrees (b), (c) and (d). To be displayed.

Strike torque is generated in the main shaft 9 when shown in FIG. 12 (b), and the seal surfaces 21a, 21b of the liner 21, and the seal surfaces of the driving blades 24a, 24b are The hollow inside the liner 21 is divided into four chambers, and in the shape of the inner hollow of the liner 11, at the moment when the torque is generated to the main shaft 9, the volume of the high pressure chamber H side is It decreases, the volume of the low pressure chamber L side increases, and each chamber becomes the high pressure chamber H and the low pressure chamber L. As shown in FIG. That is, the liner 21 is rotated by the rotor 4 to reach a position where the seal surfaces 21a and 21b of the liner 21 coincide with the seal surfaces of the driving blades 24a and 24b. In other words, each seal becomes a high pressure chamber H and a low pressure chamber L, and the driving blades 24a and 24b are pressed toward the low pressure chamber L side, so that the seal surface 21a of the liner 21 is closed. , 21b and the sealing surfaces of the driving blades 24a and 24b coincide, and the hollow inside the liner 21 is completely blocked, so that the rotational force of the liner 21 is driven by the driving blades 24a and ( It acts on the projection part 25a, 25b of the main shaft 9 via 24b), and generate | occur | produces a strike torque to the main shaft 9.

The main shaft 9 is rotated by an intermittent impact torque once per rotation of the liner 21 to perform a desired work such as tightening or loosening a bolt or nut.

On the other hand, when it shows in FIG. 12 (d), although the sealing surface 21a, 21b of the liner 21 and the sealing surface of the drive blades 24a, 24b match, it is the high pressure chamber H side. Of the hydraulic oil to move the hydraulic oil formed on both sides of the driving blades 24a and 24b from the grooves 28a and 28b for moving the hydraulic oil formed by the upper liner cover 22 and the lower liner cover 23. Since the hollow inside the liner 21 is not blocked by passing through the grooves 29a and 29b to the low pressure chamber L side, no impact torque is generated in the main shaft 9.

In addition, when it shows in FIG. 12 (a) and (c), when the seal surface 21a, 21b of the liner 21 and the sealing surface of the drive blades 24a, 24b come to the position which coincides. Each chamber becomes the high pressure chamber (H) and the low pressure chamber (L) at the moment, but as the driving blades (24a) and (24b) are pressed toward the low pressure chamber (L) side, the seal surfaces (21a) and (21b) and Without matching the seal surfaces of the drive blades 24a and 24b, the hollow inside the liner 21 is not blocked, and the working oil on the high pressure chamber H side passes through the gap between both seal surfaces and the low pressure chamber ( Since it flows to L) side, a hitting torque does not generate | occur | produce to the main shaft 9.

In this case, a part of the hydraulic oil on the high-pressure chamber H side is liner upper cover 22 from the outflow grooves 29a and 29b for moving the hydraulic oil formed on both side surfaces of the driving blades 24a and 24b. And flow through the grooves 28a and 28b for moving the working oil formed by the liner lower cover 23 to the low pressure chamber L side.

In the case where the rotor 4 is rotated in the opposite direction, the inside of the liner case 7 changes as shown in FIG. 12 (d) → (c) → (b) → (a) → (d). As a result, the main shaft 9 can generate the strike torque in the opposite direction.

13 to 14 show a third embodiment of the striking torque generating device of the hydraulic torque wrench of the present invention.

The basic structure of this embodiment is the same as that of the first embodiment described above.

The hydraulic striking torque generating device 5 of the present embodiment installs a liner 31 into the liner case 7, fills and seals hydraulic fluid into the liner 31, and coaxially runs the main shaft 9 in the liner 31. ).

In the liner 31 to which the main shaft 9 is fitted, a hollow is formed in a substantially oval shape, and four seal surfaces 31a and 31b are formed on the inner circumferential surface thereof in a set of two in a mountain shape. One set of seal surfaces, that is, the seal surface 31a and the seal surface 31b are rotated by 180 degrees to form asymmetrical positions.

The cylindrical liner 31 supports the outer periphery by the liner case 7, and installs the upper liner cover 32 and the lower liner cover 33 at both ends of the liner 31, and the liner 31 and the liner 31. The upper liner cover 32 and the lower liner cover 33 are the pinholes provided in the liner 31 and the pinholes 32a and 33a respectively provided in the liner upper cover 32 and the liner lower cover 33, respectively. By inserting the rust pin 37 into the), it is configured to rotate integrally. Then, the liner upper cover 32 is further fixed in the liner case cover 7a in the axial direction to seal the hydraulic oil filled into the liner 31.

In the main shaft 9 provided coaxially inside the liner 31, the two projections 35a and 35b, each of which has a smooth surface, are rotated by 180 degrees to be formed in asymmetrical positions. The two projections 35a and 35b of the main shaft 9 are formed to have both axial and circumferential lengths shorter than hollows inside the liner 31, so that both ends in the axial direction and the tip in the circumferential direction are formed. It is configured to form a passage through which the working oil flows.

Two drives of different sizes, formed into the liner 31 and partitioned by hollows partitioned by the projections 35a and 35b of the main shaft 9, having a smooth surface in the shape of a cross section. The wings 34a and 34b are inserted.

In this embodiment, one drive blade 34a is formed in a shape larger than the other drive blade 34b.

The two driving blades 34a and 34b have an axial length such that the side surfaces of the driving blades 34a and 34b are in sliding contact with the inner surfaces of the upper liner cover 32 and the lower liner cover 33. It is formed to have substantially the same length as the hollow inside the liner 31, and the seal surfaces corresponding to the seal surfaces 31a and 31b of the liner 31 are formed in the vicinity of both ends thereof, and 1 of the liner 31 is formed. Rotation The seal surfaces 31a and 31b of the liner 31 coincide with the seal surfaces of the drive blades 34a and 34b once, and with respect to one rotation of the liner 31 with the main shaft 9. It is configured to generate one strike torque.

In the present embodiment, four seal surfaces 31a and 31b are formed on the inner circumferential surface of the liner 31 at a position where the rotational asymmetry is 180 degrees, and one driving blade 34a is formed. Of the seal surfaces 31a, 31b and the drive wings 34a, 34b of the liner 31 with respect to one rotation of the liner 31 by forming a larger shape than the other drive blade 34b. The seal face coincides once, and the main shaft 9 is configured to generate one strike torque for one rotation of the liner 31. Instead, the seal face is replaced with a surface-symmetric crank or tilted. By forming a linear shape or a shape in which the seal surface of the liner and the seal surface of the driving blade coincide once with respect to one rotation of the liner, such as a V-shape, so that one stroke torque is produced in one rotation of the liner on the main shaft. can do.

On the outer circumferential surface of the liner 31, the low pressure chamber L inside the liner 31 partitioned by the drive blades 34a and 34b and the seal surfaces 31a and 31b of the liner 31 is used. Install a communication groove 36 communicating the hollow with each other.

In addition, the liner 31 is provided with an output adjusting mechanism 10 for adjusting the magnitude of the striking torque in parallel to the axis center of the liner 31. The output adjustment mechanism 10 is known in the prior art, and the high pressure inside the liner 31 partitioned by the drive blades 34a and 34b and the seal surfaces 31a and 31b of the liner 31 and the like. The screws 10 are adjustable in the port 10a, 10b for communicating the hollow which becomes the chamber H, and the hollow which becomes the low pressure chamber L, and the screw hole 33b provided in the lower cover 33 of the liner. An output adjustment valve 10c or the like.

In the third embodiment, the two seals 31a and 31b provided in the liner 31 and the two projections 35a and 35b provided in the main shaft 9 are provided. And the two driving blades 34a and 34b constitute the striking torque generating device 5, but the number of seal surfaces provided on the liner is not limited to this, and the striking torque generating device is provided on the liner. Two pairs of six or more even (2n) seal surfaces, three or more n protrusions provided on the main shaft, three or more n driving wings, and the like can be configured. A larger hit torque can be obtained while generating one hit torque.

In this case, by forming the seal face of the liner and the driving blade in a suitable shape, the appropriate number of times of the torque and the seal surface of the liner and the seal surface of the drive blade is matched with one rotation of the liner on the main shaft, the appropriate number of strike torque Can be generated.

Next, the operation of the striking torque generating device 5 of the hydraulic torque wrench of the third embodiment will be described.

First, when the main valve 2 and the switching valve 3 are operated to introduce high pressure air into the rotor chamber in the main body 1, the rotor 4 rotates at high speed. The rotational force of this rotor is transmitted to the liner 31.

By the rotation of the liner 31, the inside of the liner case 7 changes as shown in Fig. 14 (a) → (b) → (c) → (d) → (a). FIG. 14 (a) shows a state in which the impact torque is not generated in the main shaft 9, in which the liner 31 is rotated by approximately 90 degrees (b), (c) and (d). To be displayed.

Strike torque is generated in the main shaft 9 when it is shown in FIG. 14 (b), and the seal surfaces 31a, 31b and the driving surfaces 34a, 34b of the liner 31 Coinciding, the hollow inside the liner 31 is divided into four chambers, and the volume on the high pressure chamber H side decreases at the moment of the impact torque from the shape of the inner hollow of the liner 31 to the main shaft 9; The volume of the low pressure chamber L side increases, and each chamber becomes a high pressure chamber H and a low pressure chamber L. As shown in FIG. That is, the liner 31 is rotated by the rotor 4 to reach a position where the seal surfaces 31a and 31b of the liner 31 coincide with the seal surfaces of the driving wings 34a and 34b. In other words, each seal becomes a high pressure chamber (H) and a low pressure chamber (L), and the drive blades (34a) and (34b) are pressed toward the low pressure chamber (L) side, so that the seal surface (31a) of the liner (31). , 31b and the sealing surfaces of the driving blades 34a and 34b coincide with each other, and the hollow inside the liner 31 is completely blocked, so that the rotational force of the liner 31 is driven by the driving blades 34a and ( It acts on the projection part 35a, 35b of the main shaft 9 via 34b), and generate | occur | produces a hitting torque to the main shaft 9.

Then, the main shaft 9 is rotated by the intermittent impact torque generated once per one rotation of the liner 31 to perform a desired operation such as tightening or loosening the bolts and nuts.

On the other hand, in the case shown in FIG. 12A, when the seal surfaces 31a and 31b of the liner 31 and the seal surfaces of the driving blades 34a and 34b come to the same position, the respective seals At the moment, the high pressure chamber H and the low pressure chamber L are formed, but the sealing surfaces of the driving blades 34a and 34b do not coincide, and the hollow inside the liner 31 is not blocked and the high pressure chamber H is not blocked. The hydraulic oil on the side flows through the gap between the seal faces on both sides and flows to the low pressure chamber L side, so that no striking torque is generated on the main shaft 9.

In addition, when it is shown by (c) and (d) of FIG. 14, since the seal surface 31a, 31b of the liner 31 and the seal surface of the drive blades 34a, 34b do not correspond, (9) No striking torque occurs.

In the case where the rotor 4 is rotated in the opposite direction, the inside of the liner case 7 changes as shown in Fig. 14 (d) → (c) → (b) → (a) → (d). As a result, the main shaft 9 can generate the strike torque in the opposite direction.

15 to 20 show a fourth embodiment of the striking torque generating device of the hydraulic torque wrench of the present invention.

The basic structure of this embodiment is the same as that of the first embodiment described above.

The hydraulic strike torque generating apparatus 5 of the present embodiment installs the liner 41 into the liner case 7, fills and seals the hydraulic oil into the liner 41, and coaxially runs the main shaft 9 in the liner 41. ).

In the liner 41 into which the main shaft 9 is fitted, a hollow is formed in a substantially elliptical shape, and four seal surfaces 41a and 41b are formed on the inner circumferential surface thereof in a set of two in a mountain shape. One set of seal surfaces, that is, the seal surface 41a and the seal surface 41b are formed at a position that becomes rotationally symmetrical by 180 degrees.

The cylindrical liner 41 supports the outer periphery by the liner case 7 and installs the upper liner cover 42 and the lower liner cover 43 at both ends of the liner 41 to form the liner 41 and the liner 41. The liner upper cover 42 and the liner lower cover 43 are different from the pin holes provided in the liner 41 and the pin holes 42a and the liner upper cover 42 and the liner lower cover 43 respectively. 43a), the rust pin (not shown) is inserted into the unit, so that it is integrated and rotated. Then, the liner upper cover 42 is further fixed in the liner case cover 7a in the axial direction to seal the hydraulic oil filled into the liner 41.

On the inner surfaces of the liner upper cover 42 and the liner lower cover 43, the direction in which the guide grooves 42c and 43c are eccentric with the rotation shaft 0 of the liner 41 is rotated 180 degrees. It is formed to be.

In addition, the liner lower cover 43 is provided with a pin hole 43e and a hydraulic oil injection hole 43f. In addition, since the pin 48 penetrating the liner case 7 is inserted into the pin hole 43e, the rotation stop of the liner case 7 and the liner lower lid 43 is performed. The same applies to other examples.

In the main shaft 9 provided coaxially inside the liner 41, two projections 45a and 45b formed in a smooth shape on the surface thereof are formed at a position which becomes rotationally symmetrical by 180 degrees. The two projections 45a and 45b of the main shaft 9 are formed in both the axial direction and the circumferential length to be shorter than the hollow inside the liner 41, so as to be at both ends in the axial direction and the tip in the circumferential direction. It is configured to form a passage through which the working oil flows.

Two driving wings formed in the liner 41 and formed into a hollow defined by the projections 45a and 45b of the main shaft 9 having a smooth surface in the shape of a cross section having a substantially triangular shape and having the same size. Insert 44a and 44b.

The two driving blades 44a and 44b have an axial length such that the side surfaces of the driving blades 44a and 44b are in sliding contact with the inner surfaces of the upper liner cover 42 and the lower liner cover 43. It is formed to have substantially the same length as the hollow inside the liner 41, and the seal surfaces corresponding to the seal surfaces 41a and 41b of the liner 41 are formed near both ends thereof, and the drive wings 44a, On one side of the 44b, the pins 47a and 47b for fitting into the guide grooves 42c and 43c formed on the inner surfaces of the liner upper cover 42 and the liner lower cover 43 are formed, The pin 47b of the drive blade 44b is guided by the guide groove 42c of the upper liner top cover 42, and the pin 47a of the drive blade 44a is guided by the guide groove 43c of the lower liner bottom 43, respectively. When the seal surface 41a, 41b of the liner 41 and the seal surface of the drive blades 44a, 44b try to match twice with respect to one rotation of the liner 41, one of them Ash liner top cover (42) and liner bottom cover ( By the pins 47a and 47b of the drive blades 44a and 44b inserted into the guide grooves 42c and 43c formed by eccentricity with the rotation shaft 0 of the liner 41 on the inner surface of the line 43. By regulating the movements of the drive blades 44a and 44b, the coincidence is prevented, whereby a single strike torque is generated for each rotation of the liner 41 by the main shaft 9.

On the outer circumferential surface of the liner 41, the low pressure chamber L inside the liner 41 partitioned by the drive blades 44a and 44b and the seal surfaces 41a and 41b of the liner 41 is used. Install a communication groove 46 communicating the hollow with each other.

In addition, the liner 41 is provided with an output adjusting mechanism 10 for adjusting the magnitude of the striking torque in parallel to the axis center of the liner 41. The output adjustment mechanism 10 is known in the prior art and has a high pressure inside the liner 41 partitioned by the drive blades 44a and 44b and the seal surfaces 41a and 41b of the liner 41. An output adjustment valve adjusted from the ports 10a and 10b communicating the hollows formed by the chamber H and the hollows formed by the low pressure chamber L, and the operation holes 43b provided by the liner lower lid 23 ( 10c).

In addition, the liner 41 is provided with an accumulator 49 for absorbing thermal expansion of the hydraulic oil in parallel to the axis center of the liner 41. The accumulator 49 is composed of a piston 49a and a ventilation member 49b, and the accumulator small hole 43d whose one end surface of the piston 49a is bored by the liner lower lid 43 is formed. It communicates with the hollow inside the liner 41 and intersects the other end surface with the vent member 49b, the accumulator small hole 42b and the liner upper cover ( It is comprised so that it may communicate with air | atmosphere through the clearance gap between 42) and the liner case cover 7a.

In the fourth embodiment, two seals 41a and 41b provided in the liner 41 and two projections 45a and 45b provided in the main shaft 9 are provided. And the two strike blades 44a and 44b constitute the striking torque device 5, but the number of seal surfaces to be mounted on the liner is not limited to this, and the striking torque generating device 2 is provided to the liner. It can be composed of six or more even (2n) seal surfaces, three or more n protrusions provided on the main shaft, and three or more n driving wings, thereby making one turn per rotation of the liner on the main shaft. While generating a hitting torque, a larger hitting torque can be obtained.

In this case, an appropriate number of guide grooves are formed at an appropriate position on the inner surfaces of the liner upper cover and the lower liner lower cover with the rotation axis of the liner, so that a proper number of strike torques are applied to the main shaft with respect to one rotation of the liner. Can be generated.

Next, the operation of the striking torque generating device 5 of the hydraulic torque wrench of the fourth embodiment will be described.

First, when the main valve 2 and the switching valve 3 are operated to introduce high pressure air into the rotor chamber in the main body 1, the rotor 4 rotates at high speed. The rotational force of this rotor is transmitted to the liner 21.

By the rotation of the liner 41, the inside of the liner case 7 changes as shown in FIG. 20 (a)-(b)-(c)-(d)-(a). FIG. 20 (a) shows a state in which the impact torque is not generated in the main shaft 9, in which the liner 41 is rotated approximately 90 degrees (b), (c) and (d). To be displayed.

Strike torque is generated in the main shaft 9 when it is shown in FIG. 20 (b), and the seal surfaces 41a, 41b of the liner 41 and the seal surfaces of the driving blades 44a, 44b are In accordance with this, the hollow inside the liner 41 is divided into four chambers, and from the shape of the inner hollow of the liner 41, the volume on the high pressure chamber H side decreases at the moment of the impact torque to the main shaft 9. The volume on the low pressure chamber L side increases, and each chamber becomes a high pressure chamber H and a low pressure chamber L. As shown in FIG. That is, the liner 41 is rotated by the rotor 4 to reach a position where the seal surfaces 41a and 41b of the liner 41 and the seal surfaces of the driving blades 44a and 44b coincide. In other words, each seal becomes the high pressure chamber H and the low pressure chamber L, and the driving blades 44a and 44b are pressed toward the low pressure chamber L side, so that the seal surface 41a of the liner 41 is pressed. , 41b and the sealing surfaces of the driving blades 44a and 44b coincide with each other, and the hollow inside the liner 41 is completely blocked, so that the rotational force of the liner 41 is driven by the driving blades 44a and ( It acts as the projection part 45a, 45b of the main shaft 9 via 44b), and strikes a torque to the main shaft 9. As shown in FIG.

Then, the main shaft 9 is rotated by an intermittent impact torque generated once per one rotation of the liner 41 to perform a desired operation such as tightening or loosening a bolt or nut.

On the other hand, in the case shown in FIG. 20 (d), the seal surfaces 41a and 41b of the liner 41 try to coincide with the seal surfaces of the driving blades 24a and 24b. ) And pins 47a of the drive blades 44a and 44b inserted into the guide grooves 42c and 43c formed by eccentricity with the rotation shaft 0 of the liner 41 on the inner surface of the liner bottom cover 43. The movement of the drive blades 44a and 44b is regulated by means of 47b, which does not cause the hollow inside the liner 41 to be clogged, so that no striking torque is generated on the main shaft 9.

In addition, when it shows in FIG. 20 (a) and (c), it approaches to the position where the sealing surface 41a, 41b of the liner 41 and the sealing surface of the drive blade 44a, 44b match. When it comes, each chamber is going to be the high pressure chamber H and the low pressure chamber L at the moment, but the driving surfaces 44a and 44b are pressed toward the low pressure chamber L side, so that the seal surface of the liner 41 ( 41a), 41b, and drive surfaces 44a, 44b do not coincide, the inside of the liner 41 does not become clogged, and the hydraulic fluid of the high pressure chamber H side is both seal surfaces. As it passes through the gap between and flows to the low pressure chamber L side, no striking torque is generated to the main shaft 9.

In addition, when the rotor 4 is rotated in the opposite direction, the inside of the liner case 7 changes as shown in FIG. 20 (d) → (c) → (b) → (a) → (d). In this case, the main shaft 9 can generate the strike torque in the opposite direction to the previous one.

According to the strike torque generating device of the hydraulic torque wrench of the present invention, when the liner is rotated by the rotor, a plurality of seal surfaces formed on the inner circumferential surface of the liner and seal surfaces formed near both ends of the driving blades are matched. , It can generate hitting torque on the main shaft, and it is a spring that was essential for the conventional blow torque generating device of the hydraulic torque wrench. It doesn't always need the blade to apply the force to the outer circumferential direction, and it has small sliding resistance and good energy efficiency. It is possible to obtain the striking torque generating device of the hydraulic torque wrench, which has a small temperature rise of the hydraulic oil, a stable output is obtained, is compact, the structure is simple, and the durability is ensured.

Further, according to the hit torque generating device of the hydraulic torque wrench of the second aspect of the present invention, a plurality of seal surfaces and drive blades are formed at positions where the rotational symmetry is 360 / n on the inner circumferential surface of the liner while the liner is rotated by the rotor. The seal surface formed near both ends of N is matched n times with respect to one rotation of the liner, and at this time, n strike torques can be generated with respect to one rotation of the liner on the main axis.

Further, according to the hit torque generating device of the hydraulic torque wrench of the third aspect of the present invention, a plurality of seal surfaces and drive blades formed at positions of 360 / n degree rotational symmetry on the inner circumferential surface of the liner by rotating the liner by the rotor Matching the seal surface formed near the both ends of the liner n times with respect to one rotation of the liner, except for the one time in the double, the hydraulic oil from the groove formed in the inner surface of the liner cover and the side of the drive blade in sliding contact with the liner cover. By moving, it is possible to generate one large striking torque for one revolution of the liner on the main shaft.

In addition, according to the blow torque invention device of the hydraulic torque wrench of the fourth aspect of the present invention, a plurality of seal surfaces and drive blades formed at positions where rotational asymmetry is 360 / n degrees on the inner circumferential surface of the liner while the liner is rotated by the rotor The seal surface formed near both ends of the coincidence is matched once with respect to one rotation of the liner, and at this time, one large striking torque can be generated with respect to one rotation of the liner on the main shaft.

In addition, according to the hitting torque generating device of the hydraulic torque wrench of the fifth aspect of the present invention, a plurality of seal surfaces and drive blades formed at positions where rotational symmetry is 360 / n degrees on the inner circumferential surface of the liner by rotating the liner by the rotor The seal surface formed at both ends of the liner is controlled on the inner surface of the liner cover by regulating the movement of the drive blade by the pin of the drive blade inserted into the guide groove formed by eccentric with the rotation axis of the liner. At this time, one large striking torque can be generated per one revolution of the liner on the main shaft.

1 shows the striking torque generating device of the first embodiment of the present invention,

(a) is a front sectional view,

(b) is an I-I section.

2 is a view showing the drive blade of the striking torque generating device of the first embodiment of the present invention.

3 is a diagram showing a main axis of the striking torque generating device of the first embodiment of the present invention.

4 is a view showing a cover on the liner of the striking torque generating device according to the first embodiment of the present invention.

5 is a view showing a liner bottom cover of the striking torque generating device of the first embodiment of the present invention.

6 is a view showing the operation of the striking torque generating device of the first embodiment of the present invention.

7 shows the striking torque generating device of the second embodiment of the present invention,

(a) is a front sectional view,

(b) Section II-II.

8 is a view showing the drive blades of the striking torque generating device according to the second embodiment of the present invention.

9 is a view showing the main axis of the striking torque generating device of the second embodiment of the present invention.

10 is a view showing a cover on the liner of the striking torque generating device of the second embodiment of the present invention.

FIG. 11 is a view showing a cover under the liner of the striking torque generating device of the second embodiment of the present invention. FIG.

12 is a view showing the operation of the striking torque generating device of the second embodiment of the present invention.

13 shows a striking torque generating device according to the third embodiment of the present invention,

(a) is a front sectional view,

(b) is III-III cross section.

14 is a view showing the operation of the striking torque generating device of the third embodiment of the present invention.

15 shows a striking torque generating device of a fourth embodiment of the present invention,

(a) is a front sectional view,

(b) is IV-IV sectional drawing.

FIG. 16 is a view showing drive blades of the strike torque generating device of the fourth embodiment of the present invention;

17 is a view showing the main axis of the striking torque generating device of the fourth embodiment of the present invention.

18 is a view showing a cover on the liner of the striking torque generating device according to the fourth embodiment of the present invention.

FIG. 19 is a view showing a lower liner cover of the striking torque generating device of the fourth embodiment of the present invention. FIG.

20 is a view showing the operation of the striking torque generating device of the fourth embodiment of the present invention.

21 is a view showing the entire hydraulic impact wrench in which a conventional strike torque generating device is assembled.

-Explanation of symbols for the main parts of the drawing-

(1) ------------------------ main body,

(2) -------------------- main valve,

(3) ------------ reverse rotation switching valve,

(4) ---------------------- rotor,

(5) ------------ Strike Torque Generator,

(6) ---------------- front case,

(7) ---------------- liner case,

(8) ---------------------- liner,

(9) ------------------------ spindle,

(10) --------------- output adjusting mechanism,

(11) --------------------- liner,

(11a), (11b) ---- seal surface of liner,

(12) --------------- liner top cover,

(13) ------------- liner bottom cover,

(14a), (14b) ----------- drive wing,

(15a), (15b) ------ the projection of the spindle,

(16) --------------------- Communication Home,

(17) ----------------------- Nolphin,

21 --------------------- liner,

21a, 21b ---- seal surface of liner,

(22) --------------- liner top cover,

(23) ------------- Liner bottom cover,

(24a), (24b) ----------- Driven wing,

(25a), (25b) ------ the projection of the spindle,

(26) --------------------- Communication Home,

(27) ----------------------- Nolphin,

(28a), (28b) ----------------- home,

(29a), (29b) ------------- outflow grooves,

31 --------------------- liner,

31a, 31b ---- seal surface of liner,

(32) --------------- liner top cover,

(33) ------------- Liner bottom cover,

(34a), (34b) ----------- Driven wing,

(3Sa), (35b) ------ the projection of the spindle,

(36) --------------------- Communication Home,

(37) ----------------------- Rustpin,

41 --------------------- liner,

41a, 41b ---- seal surface of liner,

(42) --------------- liner top cover,

(42c) ------------------ Guide groove,

(43) ------------- Liner bottom cover,

(43c) ------------------ Guide groove,

(44a), (44b) ----------- Driven wing,

(45a), (45b) ------ the projection of the spindle,

(47a), (47b) ----------------- pin,

(49) --------------- Accumulator,

(H) ---------------------- high pressure room,

(L) ---------------------- Low pressure chamber,

Claims (5)

It has a hollow part and two sets of two or more even (2n) seal surfaces, has a liner rotated by a rotor, and two or more n protrusions, and is installed coaxially inside the liner. And a seal surface corresponding to the seal surface of the liner near both ends thereof, and being fitted into the hollow portion of the liner, and hitting the protrusion of the spindle to generate a strike torque on the spindle. Strike torque generating device of a hydraulic torque wrench, characterized in that consisting of two or more drive blades. The liner according to claim 1, wherein two sets of seal surfaces of the liner are formed at positions where the seal surfaces are rotationally symmetrical to each other by 360 / n degrees, thereby generating n strike torques on the main shaft with respect to one rotation of the liner. Strike torque generating device of a hydraulic torque wrench, characterized in that configured to. 2. The drive according to claim 1, wherein the two sets of seal surfaces of the liner are formed at positions where the seal surfaces are rotated by 360 / n degrees, and are in sliding contact with the inner surface of the liner cover and the liner cover. A hydraulic torque wrench hitting torque generating device, characterized in that configured to generate a one-time hitting torque on the main shaft for each rotation of the liner by forming an outflow groove for moving the hydraulic oil on the side of the wing. The method according to claim 1, wherein the two sets of seal surfaces of the liner are formed at positions where the seal surfaces are asymmetrically rotated 360 / n degrees from each other, thereby generating one strike torque on the main shaft with respect to one rotation of the liner. Strike torque generating device of the hydraulic torque wrench, characterized in that configured to. The guide groove according to claim 1, wherein the two sets of seal surfaces of the liner are formed at positions where the seal surfaces are rotated to be symmetrical with each other by 360 / n degrees, and the guide grooves are eccentric with the rotation axis of the liner on the inner surface of the liner cover. And by forming a pin to be inserted into the guide groove on the side of the drive blade in sliding contact with the liner cover, the hydraulic torque characterized in that it is configured to generate one stroke torque to the main shaft for each rotation of the liner Wrench torque generating device.