TW201919825A - Impact torque generator for hydraulic powerwrench - Google Patents

Abstract

To provide an impact torque generator for hydraulic torque wrench not requiring the blade always pushed toward the outer periphery direction of the main shaft by spring, which is small, simple in structure, and durable, featuring small sliding resistance, good energy efficiency, less temperature rise of the hydraulic fluid and stable output. Two sealing surfaces 31a and 31b of the liner 31 are formed at the position of 180 degree rotational symmetry, and when the sealing surfaces 31a and 31b of the liner 31 and one sealing surface of each driving blade 34a and 34b coincide, the other sealing surface slides in contact with the inner peripheral surface of the cavity to seal, thereby the inside of the liner 31 is divided into high-pressure room and low-pressure room by the driving blades 34a and 34b so as to generate impact torque on the main shaft 9.

Description

Impact torque generating device for hydraulic torque wrench

The present invention relates to an impact torque generating device for a hydraulic torque wrench.

As the impact torque generating device of the torque wrench, a hydraulic torque wrench using a hydraulic impact torque generating device having less noise and vibration has been developed and put into practical use.
Fig. 21 is a view showing an example of the hydraulic torque wrench, in which the main body 1 of the hydraulic torque wrench has a main valve 2 for supplying and stopping high-pressure air, and a shock torque for selectively inverting the forward and reverse directions. The forward/reverse switching valve 3 drives the rotor 4 that generates the rotational torque by the high-pressure air sent from the valves 2, 3. Further, the hydraulic type impact torque generating device 5 that converts the rotational torque of the rotor 4 into the impact torque is provided in the distal end case 6 which is provided to protrude from the distal end portion of the body 1 of the hydraulic torque wrench. The hydraulic impact torque generating device 5 is provided with a sleeve 8 in the sleeve shell 7, and the hydraulic oil is filled and sealed in the sleeve 8, and one or a plurality of blades are inserted into the groove and disposed coaxially in the sleeve. The main shaft 9 in the cylinder 8 is fitted with the vane B in the vane insertion groove, and the vane B is always biased toward the inner peripheral surface of the sleeve 8 by the spring S in the outer peripheral direction of the main shaft, and one or more The sealing surface is formed on the outer peripheral surface of the main shaft 9. Further, the sleeve 8 is provided with an output adjustment mechanism 10 that adjusts the magnitude of the impact torque. Further, when the sleeve 8 is rotated via the rotor 4, a plurality of sealing faces formed on the inner circumferential surface of the sleeve 8 and the sealing faces formed on the outer circumferential surface of the main shaft 9 and the blades B are superposed, the impact torque is generated. Spindle 9.

However, in the case of the impact torque generating device of the conventional hydraulic torque wrench, since one or a plurality of blade insertion grooves are provided in the main shaft 9, the blade B is fitted in the blade insertion groove, and the blade B is used. Since the spring S is always biased toward the outer circumferential direction of the main shaft to abut against the inner circumferential surface of the sleeve 8, the energy loss caused by the sliding friction between the tip end of the blade B and the inner circumferential surface of the sleeve 8 is large, and The frictional heat generated by the sliding causes the temperature of the hydraulic oil to rise, and the output of the torque wrench changes due to the change in the viscosity of the hydraulic oil. Further, from the viewpoint of providing the blade insertion groove and the hole into which the spring S is inserted in the main shaft 9, in order to maintain the strength of the main shaft 9, it is necessary to increase the diameter of the main shaft 9, and accordingly, the device itself is enlarged. Moreover, not only the structure of the device is complicated, but also the damage of the spring S or the like, and the durability of the device.

In order to cope with this problem, the applicant of the present invention proposed that the blade B which is always biased toward the outer circumference of the main shaft by the spring S is removed by the impact torque generating device of the hydraulic torque wrench, and the sliding friction is small and the energy efficiency is good. In addition, the impact torque generating device of the hydraulic torque wrench having a small temperature and a simple structure, and having a small temperature and a stable output of the hydraulic oil (see Patent Document 1).

[Previous Technical Literature]
[Patent Literature]

Patent Document 1 Japanese Patent Laid-Open No. Hei 7-328944

[The problem that the invention wants to solve]

The basic structure of the hydraulic torque wrench itself is the same as that of the conventional hydraulic torque wrench shown in Fig. 21. The hydraulic torque wrench has a main valve 2 for supplying and stopping high-pressure air, and is used for positive and negative. The forward/reverse switching valve 3 selectively generated by the pulsating torque is driven by the high-pressure air sent from the valves 2, 3 to drive the rotor 4 that generates the rotational torque. Further, the hydraulic type impact torque generating device 5 that can convert the rotational torque of the rotor 4 into the impact torque is provided in the distal end case 6 which is provided to protrude from the distal end portion of the body 1 of the hydraulic torque wrench.

The hydraulic impact torque generating device 5 is provided with the sleeve 11 in the sleeve shell 7 as shown in Figs. 1 to 6, and the hydraulic oil is filled and sealed in the sleeve 11, and coaxially The main shaft 9 is fitted in the sleeve 11.

In the sleeve 11 to which the main shaft 9 is assembled, a substantially elliptical hollow portion is formed inside, and four sealing faces 11a and 11b are formed in two groups in a mountain shape on the inner circumferential surface thereof, and the two sets are sealed. In other words, in other words, the sealing surface 11a and the sealing surface 11b are formed at a rotationally symmetrical position of 180°. The cylindrical sleeve 11 is supported by the sleeve shell 7 on its outer circumference, and the sleeve upper cover 12 and the sleeve lower cover 13 are disposed at both ends of the sleeve 11, the sleeve 11 and the sleeve upper cover 12 and the sleeve The canister lower cover 13 is integrally rotated by inserting the ejector pin 17 into the pin hole provided in the sleeve 11 and the pin holes 12a and 13a provided in the sleeve upper cover 12 and the sleeve lower cover 13, respectively. Further, the sleeve upper cover 12 is further fixed in the axial direction by the sleeve cover 7a to seal the hydraulic oil filled in the inside of the sleeve 11.

In the main shaft 9 coaxially disposed inside the sleeve 11, the two convex portions 15a and 15b formed in a smooth shape on the surface are formed at a rotationally symmetrical position of 180°.
The two bosses 15a and 15b of the main shaft 9 are formed such that the lengths in the axial direction and the circumferential direction are shorter than either of the hollow portions inside the sleeve 11, so that the passage of the flow of the hydraulic oil is formed. Both ends in the axial direction and the apex in the circumferential direction.

Two transmission blades 14a, 14b having a substantially triangular cross-section and the same size formed in a smooth shape on the surface are fitted to the inside of the sleeve 11, and are separated by the convex portions 15a, 15b of the main shaft 9. Inside the hollow. The two transmission blades 14a, 14b are configured to form the length in the axial direction with the sleeve 11 in such a manner that the sides of the transmission blades 14a, 14b are slidably coupled to the inner surface of the sleeve upper cover 12 and the sleeve lower cover 13. The inner hollow portions are substantially the same length, and a sealing surface corresponding to the sealing faces 11a, 11b of the sleeve 11 is formed near both end portions thereof, and each rotation of the sleeve 11 causes the sealing faces 11a, 11b of the sleeve 11 and The sealing faces of the drive blades 14a, 14b are doubled.

In the outer peripheral surface of the sleeve 11, a communication groove 16 which is a cavity portion of the low pressure chamber L in which the inside of the sleeve 11 which is divided by the transmission faces 14a and 14b of the sleeve 11 and the sleeve 11 is provided is communicated with each other. .

Further, the sleeve 11 is provided with an output adjustment mechanism 10 that adjusts the magnitude of the impact torque in parallel with the axial center of the sleeve 11. The output adjustment mechanism 10 is conventionally known, and is a hollow portion that becomes a high pressure chamber H inside the sleeve 11 that is divided by the seal faces 11a and 11b of the transmission blades 14a and 14b and the sleeve 11, and becomes a low pressure chamber L. The hollow portions 10a and 10b that communicate with each other are configured to be screwed to the output adjusting valve 10c provided in the screw hole 13b of the sleeve lower cover 13.

The operation of the impact torque generating device 5 of the hydraulic torque wrench 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 a high speed. The rotational force of this rotor is transmitted to the sleeve 11.

By the rotation of the sleeve 11, the inside of the sleeve shell 7 is changed in accordance with Fig. 6 (a) → (b) → (c) → (d) → (a). Fig. 6(a) is a view showing a state in which the impact torque is not generated in the main shaft 9, and the state in which the sleeve 11 is substantially rotated by 90° is shown in (b), (c), and (d).

The impact torque is generated when the main shaft 9 is shown in FIGS. 6(b) and (d), and the sealing faces 11a and 11b of the sleeve 11 and the sealing faces of the transmission blades 14a and 14b are overlapped, and the hollow portion inside the sleeve 11 is Divided into four chambers, from the shape of the hollow portion inside the sleeve 11, the impact torque is generated at the moment of the main shaft 9, the volume on the high pressure chamber H side is reduced, the volume on the low pressure chamber L side is increased, and each chamber becomes the high pressure chamber H and the low pressure chamber. L. In other words, when the sleeve 11 is rotated by the rotor 4, the sealing faces 11a, 11b of the sleeve 11 and the sealing faces of the drive blades 14a, 14b reach the coincident position, and the respective chambers become the high pressure chamber H and the low pressure chamber L, And the transmission blades 14a, 14b are pushed to the low pressure chamber L side, the sealing faces 11a, 11b of the sleeve 11 and the sealing faces of the transmission blades 14a, 14b coincide, and the hollow portion of the sleeve 11 is completely sealed, and the sleeve 11 The rotational force acts on the boss portions 15a, 15b of the main shaft 9 via the transmission blades 14a, 14b, so that an impact torque is generated in the main shaft 9. Further, the rotation of the main shaft 9 by the intermittently generated impact torque is performed twice for each rotation of the sleeve 11, and the required work of tightening and loosening the bolts and nuts is performed.

On the other hand, when the sealing faces 11a and 11b of the sleeve 11 and the sealing faces of the transmission blades 14a and 14b reach the overlapping position as shown in Fig. 6(a) and Fig. 6(c), the respective chambers become instantaneous. The high pressure chamber H and the low pressure chamber L are pushed to the low pressure chamber L side by the transmission blades 14a, 14b, so that the sealing faces 11a, 11b of the sleeve 11 and the sealing faces of the drive blades 14a, 14b do not coincide with each other due to the sleeve 11 The internal hollow portion does not become in a sealed state, and the hydraulic oil on the high pressure chamber H side flows to the low pressure chamber L side through the gap between the two sealing surfaces, so that the impact torque is not generated in the main shaft 9.

In addition, when the rotor 4 is rotated in the reverse direction, the inside of the sleeve shell 7 is changed in accordance with Fig. 6 (d) → (c) → (b) → (a) → (d). It is possible to generate an impact torque in the opposite direction from the front to the main shaft 9.

Here, although the basic structure is the same as that of the above-described example, the hydraulic impact torque generating device 5 may be configured as shown in Figs. 7 to 12 .

In the hydraulic impact torque generating device 5, the sleeve 21 is placed in the sleeve shell 7, and the hydraulic oil is filled and sealed in the sleeve 21, and the spindle 9 is coaxially fitted into the sleeve 21.

In the sleeve 21 in which the main shaft 9 is assembled, a substantially elliptical cavity portion is formed inside, and four sealing faces 21a and 21b are formed in two groups in a mountain shape on the inner circumferential surface thereof, and the two sets of the sealing faces are formed. The surface, in other words, the sealing surface 21a and the sealing surface 21b, are formed at a 180-degree rotationally symmetrical position. The cylindrical sleeve 21 is supported by the sleeve shell 7 on its outer circumference, and the sleeve upper cover 22 and the sleeve lower cover 23 are disposed at both ends of the sleeve 21, the sleeve 21 and the sleeve upper cover 22 and the sleeve The cartridge lower cover 23 is formed by inserting a ejector pin (not shown) into a pin hole provided in the sleeve 21 and pin holes 22a and 23a provided in the sleeve upper cover 22 and the sleeve lower cover 23, respectively. Integration to rotate. Further, the sleeve upper cover 22 is further fixed in the axial direction by the sleeve cover 7a, and the hydraulic oil filled in the inside of the sleeve 21 is sealed. Further, the inner faces of the sleeve upper cover 22 and the sleeve lower cover 23 are eccentric with the rotation axis O of the sleeve 21 to form the guide grooves 22c and 23c so as to be eccentrically rotated by 180 degrees. Further, in the sleeve lower cover 23, a pin hole 23e and a hydraulic oil injection hole 23f are formed. Further, the locking of the sleeve shell 7 and the sleeve lower cover 23 is performed by inserting the pin 28 penetrating the sleeve shell 7 into the pin hole 23e.

In the main shaft 9 coaxially disposed inside the sleeve 21, the two convex portions 25a and 25b formed in a smooth shape on the surface are formed at a 180-degree rotational symmetry position. The two convex portions 25a and 25b of the main shaft 9 are formed such that the axial direction and the circumferential length are shorter than either of the hollow portions inside the sleeve 21 to form a passage for the flow of the hydraulic oil. Both ends in the axial direction and the apex in the circumferential direction.

Two transmission blades 24a, 24b having a substantially triangular cross-section and the same size formed in a smooth shape on the surface are fitted to the inside of the sleeve 21, and are separated by the convex portions 25a, 25b of the main shaft 9. Inside the hollow. The two transmission blades 24a, 24b are such that the side faces of the transmission blades 24a, 24b are slidably coupled to the inner surfaces of the sleeve upper cover 22 and the sleeve lower cover 23 to make the length in the axial direction into the inner portion of the sleeve 21. The cavity portions are substantially the same length, and the sealing faces corresponding to the sealing faces 21a, 21b of the sleeve 21 are formed near the both end portions thereof, and are fitted to the guide faces formed on the sleeve upper cover 22 and the sleeve lower cover 23 The pins 27a, 27b of the guide grooves 22c, 23c are formed on one side of one of the transmission blades 24a, 24b, and the pin 27b of the transmission blade 24b is fitted to the guide groove 22c of the sleeve upper cover 22 to drive the blade 24a. The pin 27a is fitted to the guiding groove 23c of the sleeve lower cover 23, and each rotation of the sleeve 21 causes the sealing faces 21a, 21b of the sleeve 21 to coincide with the sealing faces of the transmission blades 24a, 24b twice, among which Once, by the pins 27a, 27b of the drive blades 24a, 24b, the guide grooves 22c, 23c formed on the inner surface of the sleeve upper cover 22 and the sleeve lower cover 23 and the rotation axis O of the sleeve 21 are eccentric. To limit the movement of the drive blades 24a, 24b, to prevent overlap, thereby forming each of the sleeves 21 I.e., a rotation impact torque generated on the spindle 9.

The outer peripheral surface of the sleeve 21 is provided with a communication groove 26 which is a cavity portion of the low pressure chamber L in which the inside of the sleeve 21 which is divided by the transmission faces 24a and 24b of the sleeve 21 and the seal faces 21a and 21b of the sleeve 21 are communicated with each other. .

Further, the sleeve 21 is provided with an output adjustment mechanism 10 that adjusts the magnitude of the impact torque in parallel with the axial center of the sleeve 21. The output adjustment mechanism 10 is conventionally known, and is a hollow portion that becomes a high pressure chamber H inside the sleeve 21 that is divided by the seal faces 21a and 21b of the transmission blades 24a and 24b and the sleeve 21, and becomes a low pressure chamber L. The hollow portions 10a and 10b are connected to each other, and the output regulating valve 10c is adjusted from the operation hole 23b provided in the sleeve lower cover 23.

Further, an accumulator 29 for absorbing thermal expansion of the hydraulic oil in parallel with the axial center of the sleeve 21 is provided in the sleeve 21. The accumulator 29 is composed of a piston 29a and a ventilation member 29b, and is configured such that one end surface of the piston 29a communicates with the inside of the sleeve 21 via an accumulator small hole 23d that is pressed into the sleeve lower cover 23. The cavity portion communicates with the atmosphere via the venting member 29b, the accumulator small hole 22b punched into the sleeve upper cover 22, and the gap between the sleeve upper cover 22 and the sleeve cover 7a.

The operation of the impact torque generating device 5 of the hydraulic torque wrench 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 a high speed. The rotational force of this rotor is transmitted to the sleeve 21.

By the rotation of the sleeve 21, the inside of the sleeve shell 7 is changed in accordance with Fig. 12 (a) → (b) → (c) → (d) → (a). Fig. 12(a) is a view showing a state in which the impact torque is not generated in the main shaft 9, and the state in which the sleeve 21 is substantially rotated by 90 degrees is shown in (b), (c), and (d).

The impact torque is generated when the main shaft 9 is shown in Fig. 12(b), the sealing faces 21a, 21b of the sleeve 21 and the sealing faces of the transmission blades 24a, 24b are overlapped, and the hollow portion inside the sleeve 21 is divided into four chambers. From the shape of the hollow portion inside the sleeve 21, the moment when the impact torque is generated at the main shaft 9, the volume on the high pressure chamber H side is reduced, and the volume on the low pressure chamber L side is increased, and each chamber becomes the high pressure chamber H and the low pressure chamber L. In other words, the sleeve 21 is rotated by the rotor 4, and when the sealing faces 21a, 21b of the sleeve 21 and the sealing faces of the drive blades 24a, 24b reach the coincident position, the respective chambers become the high pressure chamber H and the low pressure chamber L, And the transmission blades 24a, 24b are pushed to the low pressure chamber L side, the sealing faces 21a, 21b of the sleeve 21 and the sealing faces of the transmission blades 24a, 24b are coincident, and the hollow portion inside the sleeve 21 is completely sealed, and the sleeve 21 is The rotational force acts on the boss portions 25a, 25b of the main shaft 9 via the transmission blades 24a, 24b, so that the impact torque is generated in the main shaft 9. Further, each time the sleeve 21 is rotated, the spindle 9 is rotated by the intermittently generated impact torque, and the bolt, the nut are tightened, loosened, and the like.

On the other hand, when shown in Fig. 12(d), the sealing faces 21a, 21b of the sleeve 21 and the sealing faces of the drive vanes 24a, 24b are intended to coincide, but at this time, by the pins of the drive vanes 24a, 24b 27a, 27b are fitted to guide grooves 22c, 23c formed on the inner surface of the sleeve upper cover 22 and the sleeve lower cover 23 and eccentric with the rotation axis O of the sleeve 21 to restrict the movement of the transmission blades 24a, 24b. Since the hollow portion inside the sleeve 21 does not become in a sealed state, the impact torque is not generated in the main shaft 9.

Further, when the sealing faces 21a, 21b of the sleeve 21 and the sealing faces of the drive vanes 24a, 24b reach the coincident position as shown in Fig. 12(a) and Fig. 12(c), the respective chambers instantaneously become a high pressure. The chamber H and the low pressure chamber L are pushed to the low pressure chamber L side by the transmission blades 24a, 24b, so that the sealing faces 21a, 21b of the sleeve 21 and the sealing faces of the transmission blades 24a, 24b do not coincide with each other due to the sleeve 21 The internal hollow portion does not become in a sealed state, and the hydraulic oil on the high pressure chamber H side flows to the low pressure chamber L side through the gap between the two sealing surfaces, so that the impact torque is not generated in the main shaft 9.

Further, when the rotor 4 is rotated in the reverse direction, the inside of the sleeve shell 7 is changed in accordance with FIG. 12(d)→(c)→(b)→(a)→(d)・・・. It is possible to generate an impact torque in the opposite direction from the front to the main shaft 9.

According to the hydraulic type impact torque generating device 5 described in the first to sixth and seventh to twelfth drawings, there is an advantage that the conventional hydraulic torque wrench described in FIG. 21 is not required. In the impact torque generating device, the blade that is always biased toward the outer circumferential direction of the main shaft by the spring can obtain a small sliding friction and good energy efficiency, and obtain a stable and stable output of the hydraulic oil, which is not only small, but also small. An impact torque generating device of a hydraulic torque wrench having a simple structure and durability.

An object of the present invention is to provide a hydraulic type impact torque generating device 5 as described in Figs. 1 to 6 and Figs. 7 to 12, which is further improved in structure, durability, and sliding. An impact torque generating device of a hydraulic torque wrench having less friction and better energy efficiency.

[Technical means to solve the problem]

In order to achieve the above object, the impact torque generating device of the hydraulic torque wrench of the present invention includes a sleeve having a cavity portion filled with hydraulic oil therein, and a sealing surface is formed by projecting from the inner circumferential surface of the cavity portion. Rotating by the rotor; the main shaft has two convex portions coaxially disposed inside the sleeve; and the two transmission blades are sealed portions at both ends and are fitted to the hollow portion of the sleeve filled with the hydraulic oil, The driving blade is used to divide the inside of the sleeve into a high pressure chamber and a low pressure chamber, so that the impact torque is generated in the main shaft, and the sealing surface of the sleeve is formed at two 180° rotational symmetry positions of the cavity portion. When the sealing surface of the sleeve overlaps with the sealing surface of one of the transmission blades, the sealing surface of the sleeve is slidably connected to the inner circumferential surface of the hollow portion for sealing to drive the blade to divide the inside of the sleeve into a high pressure chamber. And a low pressure chamber to generate an impact torque on the main shaft.

In this case, the steel ball which is fitted to the inner surface of the sleeve upper cover and the inner surface of the sleeve lower cover and which restricts the movement of the drive blade is disposed on one side of each of the aforementioned transmission blades. It is possible to make the impact torque of the sleeve once per revolution of the spindle.

Further, the sealing surface of the aforementioned transmission blade may be configured by a steel bar disposed in a groove formed at both end portions of the transmission blade.

In addition, the cross-sectional shape of the aforementioned transmission blade can be formed to be asymmetrical.

In addition, the aforementioned transmission blade can be made to have a magnetic force.

[Effect of the invention]

An impact torque generating device for a hydraulic torque wrench according to the present invention, the impact torque generating device of the hydraulic torque wrench, comprising: a sleeve having a hollow portion filled with hydraulic oil therein, and an inner circumferential surface of the hollow portion The protrusion forms a sealing surface and is rotated by the rotor; the main shaft has two convex portions coaxially disposed inside the sleeve; and the two transmission blades have sealing surfaces at both ends and are assembled with hydraulic oil filled The hollow portion of the sleeve divides the inside of the sleeve into a high pressure chamber and a low pressure chamber by means of a transmission blade, so that an impact torque is generated on the main shaft, which is characterized in that the sealing surface of the sleeve is 180° rotationally symmetric in the cavity portion. Two positions are formed. When the sealing surface of the sleeve overlaps with the sealing surface of one of the transmission blades, the sealing surface of the other sealing surface is slidably sealed to the inner circumferential surface of the hollow portion to seal the blade to drive the blade. The inside of the cylinder is divided into a high pressure chamber and a low pressure chamber so that an impact torque is generated from the main shaft, from the above viewpoint, by the sealing surface of the sleeve which will correspond to the other sealing surface of each of the transmission blades The inner peripheral surface of the hole portion is constituted, the processing steps may be omitted formed substantially hollow portion of the sealing surface of the sleeve, the configuration becomes simple, the impact may be provided a hydraulic torque wrench having a torque generating apparatus durability.

Further, a steel ball that is fitted to the guide groove formed on the inner surface of the sleeve upper cover and the sleeve lower cover and that restricts the movement of the drive blade is disposed on one side of each of the aforementioned transmission blades so that Each rotation of the sleeve generates an impact torque of one time on the main shaft, whereby an impact torque generating device of a hydraulic torque wrench having a small sliding friction and an energy efficiency can be provided.

In addition, by forming the sealing surface of the aforementioned transmission blade with a steel bar disposed in a groove formed at both end portions of the transmission blade, it is possible to provide a hydraulic torque wrench having less sliding friction and better energy efficiency. Impact torque generating device.

Further, by making the cross-sectional shape of the transmission blade asymmetrical, it is possible to improve the stability of the operation of the transmission blade when the rotation shaft is used in the horizontal direction, and to obtain a stable and efficient output.

Further, by causing the transmission blade to have a magnetic force, it is possible to prevent the magnetic powder from being worn by the magnetic powder by adsorbing the magnetic powder generated by the wear of the components contained in the hydraulic oil to the transmission blade. In addition, the magnetic powder adsorbed to the drive blades can be easily removed by simply wiping the drive blades during maintenance.

Hereinafter, an embodiment of the impact torque generating device of the hydraulic torque wrench of the present invention will be described with reference to the drawings.

Fig. 13 to Fig. 16 show an embodiment of an impact torque generating device of the hydraulic torque wrench of the present invention.

This hydraulic type impact torque generating device 5 further improves the hydraulic type impact torque generating device 5 described in Figs. 1 to 6 and Figs. 7 to 12, and has a simpler structure and durability. A product that has less sliding friction and is more energy efficient.

Further, the basic structure is the same as that of the hydraulic impact torque generating device 5 described in FIGS. 1 to 6 and FIGS. 7 to 12, and the sleeve 31 is placed in the sleeve case 7, and The hydraulic oil is filled and sealed in the sleeve 31, and the main shaft 9 is coaxially fitted in the sleeve 31.

A substantially elliptical cavity portion is formed inside the sleeve 31 of the assembly main shaft 9, and the two sealing faces 31a, 31b are formed in a 180-degree rotationally symmetrical position on the inner peripheral surface thereof in a mountain shape. The cylindrical sleeve 31 is supported by the sleeve shell 7 on its outer circumference, and the sleeve upper cover 32 and the sleeve lower cover 33 are disposed at both ends of the sleeve 31, the sleeve 31 and the sleeve upper cover 32 and the sleeve. The cylinder lower cover 33 is integrally formed by inserting an ejector pin (not shown) into a pin hole provided in the sleeve 31 and pin holes provided in the sleeve upper cover 32 and the sleeve lower cover 33, respectively. Turn. Further, the sleeve upper cover 32 is further fixed in the axial direction by the sleeve cover 7a, and the hydraulic oil filled in the inside of the sleeve 31 is sealed. Further, the inner faces of the sleeve upper cover 32 and the sleeve lower cover 33 are eccentric with the rotation axis O of the sleeve 31 to form the guide grooves 32c and 33c so as to be eccentrically rotated by 180 degrees. Further, on the inner surface of the sleeve upper cover 32 and the sleeve lower cover 33, a groove for releasing hydraulic oil is formed at a predetermined position.

Here, the hydraulic impact torque generating device 5 of the present embodiment is different from the hydraulic impact torque generating device 5 described in FIGS. 1 to 6 and 7 to 12, The other sealing faces 31a' and 31b' of the pair of sealing faces 31a and 31b, in other words, the sealing faces of the sleeve 31 corresponding to the sealing faces of the respective transmission blades 34a and 34b to be described later, are the inner circumference of the cavity portion. Face to face.
The inner peripheral surface of the cavity portion of the sleeve 31 constituting the sealing faces 31a' and 31b' is formed into a substantially cylindrical shape, and the angle θ is formed by 30 to 70 degrees, preferably 40 to 60 degrees. This embodiment is 50°).
Thereby, by forming the two mountain-shaped sealing faces 31a, 31b, the processing steps of the hollow portion of the sleeve 31 which substantially forms the sealing faces 31a', 31b' can be omitted, and the structure becomes simple and can be provided with durability. Impulse torque generating device for hydraulic torque wrenches.

The main shaft 9 coaxially disposed inside the sleeve 31 is formed in a 180-degree rotationally symmetrical position by forming two convex portions 35a and 35b having a smooth shape on the surface. The two convex portions 35a and 35b of the main shaft 9 are formed such that the axial direction and the circumferential length are shorter than either of the hollow portions inside the sleeve 31 to form a passage for the flow of the hydraulic oil. Both ends in the axial direction and the apex in the circumferential direction.

Two transmission blades 34a, 34b having a substantially triangular cross section and a same size formed in a smooth shape on the surface are fitted to the inside of the sleeve 31, and are separated by the convex portions 35a, 35b of the main shaft 9. Inside the hollow. The two transmission blades 34a, 34b are such that the side faces of the transmission blades 34a, 34b are slidably coupled to the inner surfaces of the sleeve upper cover 32 and the sleeve lower cover 33 to make the length in the axial direction into the inner portion of the sleeve 31. The hollow portions are substantially the same length, and the sealing faces corresponding to the sealing faces 31a, 31a', 31b, 31b' of the sleeve 31 are formed near the both end portions thereof, and are fitted to the sleeve upper cover 32 and the sleeve lower cover. The steel balls 37a, 37b of the guide grooves 32c, 33c on the inner surface of the 33 are disposed on the side of one of the transmission blades 34a, 34b, and the steel ball 37b of the transmission blade 34b is fitted to the guide recess of the sleeve upper cover 32. The groove 32c fits the steel ball 37a of the transmission blade 34a to the guiding groove 33c of the sleeve lower cover 33, and each rotation of the sleeve 31 causes the sealing faces 31a, 31a', 31b, 31b' of the sleeve 31 to When the sealing faces of the drive blades 34a, 34b are overlapped twice, one of them is fitted to the inner surface of the sleeve upper cover 32 and the sleeve lower cover 33 by the steel balls 37a, 37b of the drive blades 34a, 34b. The guide grooves 32c, 33c formed by the eccentricity of the rotation axis O of 31 restrict the movement of the drive blades 34a, 34b to block Together, whereby each configured to produce rotation of the sleeve 31 i.e. of the first impact torque to the main shaft 9.

Here, it is also possible to apply the guide groove 22c for guiding and restricting the movement of the transmission blades 34a, 34b as described in FIGS. 7 to 12 and used in the hydraulic impact torque generating device 5. The pins 27a, 27b of the 23c replace the steel balls 37a, 37b fitted to the guide grooves 32c, 33c for guiding and restricting the movement of the transmission blades 34a, 34b used in the present embodiment.

Tables 1 and 16 show the output of the comparison test (measurement measured by the digital torque tester) and the waveform thereof when the pins 27a and 27b and the steel balls 37a and 37b are used.

As a result of the comparison test when the pins 27a and 27b and the steel balls 37a and 37b were used, it was found that the steel balls 37a and 37b were compared with the pins 27a and 27b, and it was confirmed that the sliding friction was small and the energy efficiency was improved.

The sealing faces of the drive blades 34a, 34b, as shown in Fig. 15, can be constructed as required by the steel bars 34d disposed in the grooves 34c formed at both end portions of the transmission blade.
Thereby, it is possible to provide an impact torque generating device of a hydraulic type torque wrench which has a small sliding friction and is more energy efficient.

On the outer circumferential surface of the sleeve 31, a hollow portion which becomes the low pressure chamber L inside the sleeve 31 which is divided by the sealing faces 31a, 31a', 31b, 31b' of the transmission blades 34a, 34b and the sleeve 31 is provided to each other. Connected communication grooves (not shown).

Further, the sleeve 31 is provided with an output adjustment mechanism 10 that adjusts the magnitude of the impact torque in parallel with the axial center of the sleeve 31. The output adjustment mechanism 10 is a well-known hollow hole which is a high pressure chamber H inside the sleeve 31 which is divided by the seal faces 31a, 31a', 31b, and 31b' of the drive vanes 24a and 24b and the sleeve 31. The portion is configured to communicate with a hollow portion that is a low pressure chamber L (not shown), and an output adjustment valve 10c that is adjustably screwed to a screw hole provided in the sleeve lower cover 33.

Further, an accumulator 39 for absorbing thermal expansion of the hydraulic oil in parallel with the axial center of the sleeve 31 is provided in the sleeve 31.

The operation of the impact torque generating device 5 of the hydraulic torque wrench 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 a high speed. The rotational force of this rotor is transmitted to the sleeve 31.

By the rotation of the sleeve 31, the inside of the sleeve shell 7 is changed in accordance with Fig. 14 (a) → (b) → (a). Fig. 14(a) is a view showing a state in which the impact torque is generated in the main shaft 9, and the state in which the sleeve 31 is substantially rotated by 180 is shown in Fig. 14(b).

The impact torque is generated when the main shaft 9 is shown in Fig. 14(a), and the sealing faces 31a, 31a', 31b, 31b' of the sleeve 31 and the sealing faces of the transmission blades 34a, 34b coincide, and the cavity inside the sleeve 31 is hollow. The portion is divided into four chambers. From the shape of the hollow portion inside the sleeve 31, the impact torque is generated at the moment of the main shaft 9, the volume on the side of the high pressure chamber H is reduced, and the volume on the side of the low pressure chamber L is increased, and each chamber becomes the high pressure chamber H and Low pressure chamber L. In other words, when the sleeve 31 is rotated by the rotor 4, and the sealing faces 31a, 31a', 31b, 31b' of the sleeve 31 and the sealing faces of the drive blades 34a, 34b reach the coincident position, the respective chambers become high pressure The chamber H and the low pressure chamber L, and the transmission blades 34a, 34b are pushed to the low pressure chamber L side, and the sealing faces 31a, 31a', 31b, 31b' of the sleeve 31 and the sealing faces of the transmission blades 34a, 34b coincide, the sleeve 31 The inner hollow portion is completely sealed, and the rotational force of the sleeve 31 acts on the boss portions 35a, 35b of the main shaft 9 via the transmission blades 34a, 34b, so that the impact torque is generated in the main shaft 9. Further, each time the sleeve 31 is rotated, the main shaft 9 is rotated by the intermittently generated impact torque, and the bolts and the nuts are tightened and loosened.

On the other hand, when shown in Fig. 14(b), the sealing faces 31a, 31a', 31b, 31b' of the sleeve 31 coincide with the sealing faces of the drive blades 34a, 34b, but at this time, by the drive blades The steel balls 37a, 37b of 34a, 34b are fitted to guide grooves 32c, 33c formed on the inner surface of the sleeve upper cover 32 and the sleeve lower cover 33 and eccentric with the rotation axis O of the sleeve 31 to restrict the transmission blades 34a, The operation of 34b is such that the cavity portion inside the sleeve 31 does not become in a sealed state, so that the impact torque is not generated in the main shaft 9.

As described above, the sealing faces 31a, 31a', 31b, and 31b' of the sleeve 31 and the sealing faces of the drive vanes 34a and 34b are not overlapped or sealed except when shown in Fig. 14(a).

Further, when the rotor 4 is rotated in the reverse direction, the impact torque in the reverse direction can be generated in the spindle 9.

Further, the other structure and action of the hydraulic impact torque generating device 5 are the same as those of the hydraulic impact torque generating device 5 described in FIGS. 1 to 6 and 7 to 12 .

Further, with each rotation of the sleeve 31, a single impact torque is generated in the mechanism of the main shaft 9, except for the steel fitted to the guide grooves 32c, 33c which guides and restricts the action of the transmission blades 34a, 34b. The balls 37a, 37b; and the guides for guiding and restricting the movement of the transmission blades 34a, 34b as described in Figs. 7 to 12, and being used in the hydraulic impact torque generating device 5 are fitted to the guide grooves 22c, In addition to the pins 27a and 27b of 23c, the mechanism disclosed in Patent Document 1 can also be employed.

Further, since the hydraulic impact type torque generating device 5 has a small sliding friction and good energy efficiency, it can be the same as the hydraulic type impact torque generating device 5 described in Figs. 1 to 6 . Each rotation of 31 causes two impact torques to be generated at the main shaft 9.

However, although the hydraulic impact torque generating device 5 exerts the above-described effects, the following problems remain.
(1) The stability of the operation of the drive blade when the rotary shaft is used in the horizontal direction is low.
(2) The magnetic powder generated by the wear of the parts contained in the hydraulic oil causes the parts to wear and the durability of the apparatus is lowered.

A modified embodiment of the impact torque generating device of the hydraulic torque wrench of the present invention which can cope with this problem is shown in Figs. 17 to 20 .

In order to cope with the problem of the above (1), the cross-sectional shape of the transmission blades 34a, 34b is formed to be asymmetrical in this modified embodiment.
Specifically, as shown in Fig. 17(c), in the cross-sectional shape of the transmission blades 34a, 34b, the bulging portion 34e is formed on the left side by sandwiching the center line Lo, and the volume of the left half is formed to be larger than the right side. Half of the volume is so large that the center of gravity does not land on the center line Lo.
Therefore, as shown in FIG. 20, in particular, when the rotation axis of the transmission blades 34a and 34b is not stabilized, the rotation axis is used in a horizontal direction as compared with the case where the rotation axis is used in a vertical direction with respect to the horizontal plane. The stability of the operation of the drive blades 34a, 34b is improved, and a stable and efficient output can be obtained.

Next, in order to cope with the problem of the above (2), in the modified embodiment, the transmission blades 34a, 34b have magnetic forces.
Specifically, the magnet 38 is embedded in a portion that does not come into contact with other members of the drive blades 34a, 34b, as shown in Figs. 18(a) and 18(b), or as in item 18(c). As shown in the figure, the magnets 38 may be attached, and the drive blades 34a and 34b themselves may be magnetized.
Further, the size (surface area and thickness) and magnetic strength of the magnet 38 can be appropriately set by the amount of magnetic powder adsorbed to the transmission blades 34a and 34b.
Thereby, the magnetic powder generated by the abrasion of the components contained in the hydraulic oil is adsorbed to the transmission blades 34a and 34b without being affected by the resistance caused by the contact with the other members and the balance surface, thereby preventing the cause. Magnetic powder causes parts to wear out. Further, the magnetic powder adsorbed to the transmission blades 34a, 34b can be easily removed by simply wiping the drive blades 34a, 34b during maintenance.

Further, the other structure and action of the hydraulic impact torque generating device 5 are the same as those of the hydraulic impact torque generating device 5 described in FIGS. 13 to 16 .

Although the impact torque generating device of the hydraulic torque wrench according to the present invention has been described based on the embodiments, the present invention is not limited to the configuration described in the above embodiments, for example, a motor as a driving source, except for pneumatics. In addition to the motor, an electric motor or the like may be used, and the configuration may be appropriately changed without departing from the scope of the invention.

[Industry use possibility]

The impact torque generating device of the hydraulic torque wrench of the present invention has a small sliding friction and good energy efficiency because the blade is always urged toward the outer circumferential direction of the main shaft by the spring, and the temperature rise of the hydraulic oil is less and stable. The output is small, simple in structure, and durable, so it can be applied to hydraulic torque wrenches for electric motors that use air-cooling effects caused by high-pressure air that cannot expect power sources, and requires high fastening precision. In addition to the use of the hydraulic torque wrench, for example, it can also be applied to the use of a hydraulic torque wrench using a pneumatic motor.

1‧‧‧ Ontology

2‧‧‧Main valve

3‧‧‧ Forward and reverse switching valve

4‧‧‧Rotor

5‧‧‧ Impact Torque Generator

6‧‧‧ front end shell

7‧‧‧Sleeve shell

8‧‧‧ sleeve

9‧‧‧ Spindle

10‧‧‧Output adjustment mechanism

11‧‧‧Sleeve

11a‧‧‧ Sealing surface of the sleeve

11b‧‧‧ Sealing surface of the sleeve

12‧‧‧Sleeve cover

13‧‧‧Sleeve lower cover

14a‧‧‧Drive blades

14b‧‧‧Drive blades

15a‧‧‧The convex part of the main shaft

15b‧‧‧The convex part of the main shaft

16‧‧‧Connecting groove

17‧‧‧Top sales

21‧‧‧Sleeve

21a‧‧‧ Sealing surface of the sleeve

21b‧‧‧ Sealing surface of the sleeve

22‧‧‧Sleeve cover

22c‧‧‧ guiding groove

23‧‧‧Sleeve lower cover

23c‧‧‧ guiding groove

24a‧‧‧Drive blades

24b‧‧‧Drive blades

25a‧‧‧The convex part of the main shaft

25b‧‧‧The convex part of the main shaft

26‧‧‧Connecting groove

27a‧‧ sales

27b‧‧ sales

29‧‧‧ accumulator

31‧‧‧ sleeve

31a‧‧‧ Sealing surface of the sleeve

31a’‧‧‧ sealing surface of the sleeve

31b‧‧‧ Sealing surface of the sleeve

Sealing surface of 31b’‧‧‧ sleeve

32‧‧‧Sleeve cover

32c‧‧‧ guiding groove

33‧‧‧Sleeve lower cover

33c‧‧‧ guiding groove

34a‧‧‧Drive blades

34b‧‧‧Drive blades

34c‧‧‧ Groove

34d‧‧‧Steel rod

34e‧‧‧ Uplift

35a‧‧‧The convex part of the main shaft

35b‧‧‧The convex part of the main shaft

37a‧‧‧ steel ball

37b‧‧‧ steel ball

38‧‧‧ Magnet

39‧‧‧ accumulator

H‧‧‧High pressure room

L‧‧‧ low pressure room

Lo‧‧‧ center line

S‧‧ ‧ spring

Fig. 1 is a view showing an example of an impact torque generating device of a hydraulic torque wrench, wherein (a) is a front cross-sectional view and (b) is a cross-sectional view taken along line I-I.

Fig. 2 is a view showing a transmission blade of the impact torque generating device of this example.

Fig. 3 is a view showing the main shaft of the impact torque generating device of this example.

Fig. 4 is a view showing the sleeve upper cover of the impact torque generating device of this example.

Fig. 5 is a view showing a sleeve lower cover of the impact torque generating device of this example.

Fig. 6 is a view showing the operation of the impact torque generating device of this example.

Fig. 7 is a view showing another example of the impact torque generating device of the hydraulic torque wrench, wherein (a) is a front cross-sectional view and (b) is a cross-sectional view taken along line II-II.

Fig. 8 is a view showing a transmission blade of the impact torque generating device of this example.

Fig. 9 is a view showing the main shaft of the impact torque generating device of this example.

Fig. 10 is a view showing the sleeve upper cover of the impact torque generating device of this example.

Fig. 11 is a view showing a sleeve lower cover of the impact torque generating device of this example.

Fig. 12 is a view showing the operation of the impact torque generating device of this example.

Fig. 13 is a view showing an embodiment of an impact torque generating device for a hydraulic torque wrench according to the present invention, wherein (a) is a front sectional view and (b) is a sectional view taken along line III-III.

Fig. 14 is a view showing the operation of the impact torque generating device of the embodiment.

Fig. 15 is an exploded view of the transmission blade of the embodiment, (a) is a front view, and (b) is a side view.

Fig. 16 is a view showing an output of a comparative test and a waveform thereof by a pin and a steel ball which restrict the operation of the drive blade.

Figure 17 is a perspective view showing a modified embodiment of the impact torque generating device of the hydraulic torque wrench of the present invention, wherein (a) is a front sectional view, (b) is a sectional view taken along line IV-IV, and (c) is a transmission. Side view of the blade.

Fig. 18 is an exploded view of the transmission blade of the modified embodiment, (a) is a front view, (b) is a side view, and (c) is a side view showing a different embodiment.

Fig. 19 is a view showing the operation of the impact torque generating device of the modified embodiment.

Fig. 20 is a view showing an output waveform of a comparative test according to the modified embodiment.

Fig. 21 is a view showing the entirety of a hydraulic air impact wrench to which a conventional impact torque generating device is attached.

Claims (5)

An impact torque generating device for a hydraulic torque wrench, comprising: a sleeve having a hollow portion filled with hydraulic oil inside, protruding from the inner peripheral surface of the hollow portion to form a sealing surface and being rotated by the rotor; a main shaft having two bosses coaxially disposed inside the sleeve; The two transmission blades are sealing portions at both ends and are fitted to the hollow portion of the sleeve filled with hydraulic oil. By means of the drive blades, the inside of the sleeve is divided into a high pressure chamber and a low pressure chamber, so that the impact torque is generated in the main shaft, which is characterized by: Forming two sealing faces of the sleeve at 180° rotationally symmetric positions of the cavity portion, and when the sealing surface of the sleeve coincides with one of the sealing faces of each of the transmission blades, the sealing surface is slid by the other sealing surface The inner peripheral surface of the cavity is sealed to drive the blades, and the inside of the sleeve is divided into a high pressure chamber and a low pressure chamber so that an impact torque is generated in the main shaft. An impact torque generating device for a hydraulic torque wrench according to claim 1 of the patent scope, wherein By arranging a steel ball that is fitted to the guide groove formed on the inner surface of the sleeve upper cover and the lower cover of the sleeve and restricting the movement of the drive blade, the side surface of one of the aforementioned transmission blades is disposed so that the sleeve Each rotation produces one impact torque on the spindle. An impact torque generating device for a hydraulic torque wrench according to claim 1 or 2, wherein The sealing surface of the aforementioned transmission blade is configured by a steel bar disposed in a groove formed at both end portions of the transmission blade. An impact torque generating device for a hydraulic torque wrench according to claim 1, 2, or 3, wherein The cross-sectional shape of the aforementioned transmission blade is formed to be asymmetrical. An impact torque generating device for a hydraulic torque wrench according to the first, second, third or fourth aspect of the patent application, wherein The aforementioned transmission blade is made to have a magnetic force.