TWI770255B - Impact torque generator for hydraulic power wrench - Google Patents

Abstract

The present invention provides a vane that is always elastically pressed toward the outer circumference of the main shaft without the use of a spring, obtains a stable output with less sliding friction, good energy efficiency, less temperature rise of hydraulic oil, and is not only small, simple in structure, but also durable The impact torque generator of the hydraulic torque wrench.

Two sealing surfaces (31a, 31b) of the sleeve (31) are formed at 180° rotationally symmetrical positions of the cavity, when the sealing surfaces (31a, 31b) of the sleeve (31) and the respective transmission blades (34a, 34b) When one of the sealing surfaces overlaps, the other sealing surface is slidably connected to the inner peripheral surface of the cavity for sealing, and the inside of the sleeve (31) is divided into a high-pressure chamber ( H) and low pressure chamber (L), so that the impact torque is generated on the main shaft (9).

Description

Impact torque generator for hydraulic torque wrenches

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

As an impact torque generator for a torque wrench, a hydraulic torque wrench using a hydraulic impact torque generator with less noise and vibration has been developed and put into practical use. Fig. 21 shows an example of the hydraulic torque wrench. The body 1 of the hydraulic torque wrench includes a main valve 2 for supplying and stopping high-pressure air, and a valve for selectively generating an impact torque for forward and reverse rotation. The forward/reverse switching valve 3 drives the rotor 4 that generates rotational torque by the high-pressure air sent from the valves 2 and 3 . In addition, a hydraulic impact torque generator 5 that converts the rotational torque of the rotor 4 into impact torque is provided in a front end housing 6 protruding from the front end of the main body 1 of the hydraulic torque wrench. In the hydraulic impact torque generating device 5, a sleeve 8 is installed in the sleeve shell 7, the sleeve 8 is filled and sealed with hydraulic oil, and one or more blade insertion grooves are arranged in the sleeve coaxially assembled to the sleeve 8. The main shaft 9 in the cylinder 8 is assembled with the blade B into the blade insertion groove, the blade B is always pressed by the spring S toward the outer peripheral direction of the main shaft to abut against the inner peripheral surface of the sleeve 8, and one or more The sealing surface is formed on the outer peripheral surface of the main shaft 9 . In addition, the sleeve 8 is provided with an output adjustment mechanism 10 that adjusts the magnitude of the impact torque. Then, when the sleeve 8 is rotated via the rotor 4 so that a plurality of sealing surfaces formed on the inner peripheral surface of the sleeve 8 overlap with the sealing surfaces formed on the outer peripheral surface of the main shaft 9 and the vanes B, impact torque is generated in the Spindle 9.

However, in the case of the impact torque generator of the conventional hydraulic torque wrench, one or a plurality of blade insertion grooves are provided in the main shaft 9, the blade B is assembled in the blade insertion groove, and the blade B is inserted into the blade insertion groove. Since the spring S is always pressed in the outer peripheral direction of the main shaft to abut against the inner peripheral surface of the sleeve 8, the energy loss caused by the sliding friction between the tip of the vane B and the inner peripheral surface of the sleeve 8 is large, and this The frictional heat generated by sliding increases the temperature of the hydraulic oil, and the output of the torque wrench fluctuates due to the change in the viscosity of the hydraulic oil. In addition, in order to maintain the strength of the main shaft 9, in order to maintain the strength of the main shaft 9, the diameter of the main shaft 9 has to be increased, and the size of the device itself is accordingly increased. , and not only the structure of the device becomes complicated, but also there is a problem of the durability of the device, such as breakage of the spring S.

In order to deal with this problem, the applicant of the present application proposes to first remove the blade B that is always pressed toward the outer circumference of the main shaft by the spring S from the impact torque generating device of the hydraulic torque wrench, so as to obtain low sliding friction and good energy efficiency. , The hydraulic oil temperature rise is small and stable output, not only small size, simple structure, but also durable impact torque generator of hydraulic torque wrench (refer to Patent Document 1). [Prior Art Literature] [Patent Literature]

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

[Problems to be Solved by Invention]

The basic structure of this 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 a The forward/reverse switching valve 3 that selectively generates rotational impact torque drives the rotor 4 that generates rotational torque by the high-pressure air sent from the valves 2 and 3 . Furthermore, the hydraulic impact torque generator 5 capable of converting the rotational torque of the rotor 4 into the impact torque can be installed in the front end housing 6 protruding from the front end of the main body 1 of the hydraulic torque wrench.

As shown in FIGS. 1 to 6, the hydraulic impact torque generator 5 has a sleeve 11 installed in the sleeve case 7, filled and sealed with hydraulic oil in the sleeve 11, and coaxially connected to the sleeve 11. The main shaft 9 is fitted in the sleeve 11 .

The sleeve 11 to which the main shaft 9 is attached is formed with a substantially elliptical hollow portion inside, and two sets of four sealing surfaces 11a and 11b are formed on the inner peripheral surface of the sleeve 11 in the shape of a mountain, and the two sets of seal faces 11a and 11b are sealed. The surfaces, in other words, the sealing surface 11a and the sealing surface 11b, are formed at 180° rotationally symmetrical positions. The outer circumference of the cylindrical sleeve 11 is supported by the sleeve shell 7, and the sleeve upper cover 12 and the sleeve lower cover 13 are arranged on both ends of the sleeve 11. The sleeve 11, the sleeve upper cover 12 and the sleeve The lower cylinder cover 13 is configured to rotate integrally by inserting the ejector pin 17 into the pin hole provided in the sleeve 11 and the pin holes 12a and 13a respectively provided in the upper sleeve cover 12 and the lower sleeve cover 13 . Furthermore, the sleeve upper cover 12 is further fixed in the axial direction with the sleeve case cover 7a, and the hydraulic oil filled in the inside of the sleeve 11 is sealed.

In the main shaft 9 coaxially arranged inside the sleeve 11 , two bosses 15 a and 15 b formed in a smooth shape on the surface are formed at positions that are rotationally symmetric by 180°. The two bosses 15a and 15b of the main shaft 9 are configured to have lengths in the axial direction and the circumferential direction shorter than any of the hollow parts inside the sleeve 11 so as to form a passage for the flow of hydraulic oil. Both ends in the axial direction and the tip in the circumferential direction.

Two propeller blades 14a, 14b having a substantially triangular cross-section and having the same size and having a smooth shape on the surface are assembled inside the sleeve 11 and divided by the bosses 15a, 15b of the main shaft 9. Inside the cavity. The two transmission vanes 14a, 14b are configured to have a length in the axial direction equal to that of the sleeve 11 so that the side surfaces of the transmission vanes 14a, 14b are slidably connected to the inner surfaces of the sleeve upper cover 12 and the sleeve lower cover 13 The hollow portion inside is approximately the same length, and sealing surfaces corresponding to the sealing surfaces 11a, 11b of the sleeve 11 are formed in the vicinity of both ends thereof, and the sealing surfaces 11a, 11b and 11b of the sleeve 11 and The sealing surfaces of the transmission blades 14a and 14b are overlapped twice.

On the outer peripheral surface of the sleeve 11, there is provided a communication groove 16 that communicates the hollow portions of the low-pressure chamber L in the interior of the sleeve 11, which are divided by the transmission vanes 14a, 14b and the sealing surfaces 11a, 11b of the sleeve 11. .

In addition, the sleeve 11 is provided with an output adjustment mechanism 10 that adjusts the magnitude of the impact torque in parallel with the axis of the sleeve 11 . The output adjustment mechanism 10 is conventionally known, and includes a hollow portion serving as a high pressure chamber H and a low pressure chamber L inside the sleeve 11 divided by the transmission vanes 14a, 14b and the sealing surfaces 11a, 11b of the sleeve 11. It is composed of ports 10a and 10b which communicate with the hollow part of the sleeve, and an output regulating valve 10c which is adjustably screwed to the screw hole 13b provided in the lower sleeve cover 13 .

The operation of the impact torque generator 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 the rotor is transmitted to the sleeve 11 .

By the rotation of the sleeve 11, the inside of the sleeve case 7 changes according to Fig. 6 (a)→(b)→(c)→(d)→(a)・・・. Fig. 6(a) shows a state in which impact torque is not generated in the main shaft 9, whereby the state in which the sleeve 11 is rotated approximately 90° is shown in (b), (c) and (d).

When the impact torque is generated by the main shaft 9 as shown in Figs. 6(b) and (d), the sealing surfaces 11a and 11b of the sleeve 11 and the sealing surfaces of the propeller blades 14a and 14b overlap, 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 moment the impact torque is generated on the main shaft 9, the volume of the high-pressure chamber H side decreases, and 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. In other words, when the sleeve 11 is rotated by the rotor 4 and the sealing surfaces 11a and 11b of the sleeve 11 and the sealing surfaces of the transmission vanes 14a and 14b are overlapped, the respective chambers become the high pressure chamber H and the low pressure chamber L, In addition, the drive vanes 14a and 14b are pushed to the low pressure chamber L side, the sealing surfaces 11a and 11b of the sleeve 11 and the seal surfaces of the drive vanes 14a and 14b overlap, and the hollow portion inside the sleeve 11 is completely sealed, and the sleeve 11 The rotational force of the shaft acts on the bosses 15 a and 15 b of the main shaft 9 via the transmission blades 14 a and 14 b, so that an impact torque is generated in the main shaft 9 . In addition, every rotation of the sleeve 11 is performed twice by the intermittently generated impact torque to rotate the main shaft 9, and to perform necessary operations such as tightening and loosening of bolts and nuts.

On the other hand, as shown in Figs. 6(a) and 6(c), when the sealing surfaces 11a and 11b of the sleeve 11 and the sealing surfaces of the propeller blades 14a and 14b reach the overlapping position, the respective chambers instantly become The high pressure chamber H and the low pressure chamber L are pushed to the low pressure chamber L side by the transmission vanes 14a and 14b so that the sealing surfaces 11a and 11b of the sleeve 11 and the sealing surfaces of the transmission vanes 14a and 14b do not overlap. The hollow portion inside of the duct is not sealed 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 impact torque is not generated on the main shaft 9 .

In addition, when the rotor 4 is rotated in the opposite direction, the inside of the sleeve case 7 changes according to Fig. 6 (d)→(c)→(b)→(a)→(d)... It is possible to generate the impact torque in the opposite direction to the main shaft 9 .

Here, although the basic structure is the same as that of the above-mentioned example, the hydraulic shock torque generator 5 may be configured as shown in FIGS. 7 to 12 .

In the hydraulic impact torque generator 5 , a sleeve 21 is installed in the sleeve shell 7 , the sleeve 21 is filled and sealed with hydraulic oil, and the main shaft 9 is assembled in the sleeve 21 coaxially.

The sleeve 21 to which the main shaft 9 is attached is formed with a substantially elliptical hollow portion inside, and two sets of four sealing surfaces 21a and 21b are formed on the inner peripheral surface of the sleeve 21 in the shape of a mountain, and the two sets of seal faces 21a and 21b are formed. The surfaces, in other words, the sealing surface 21a and the sealing surface 21b, are formed at positions that are rotationally symmetric by 180 degrees. The cylindrical sleeve 21 is supported by the sleeve shell 7 at its outer periphery, and the sleeve upper cover 22 and the sleeve lower cover 23 are arranged on both ends of the sleeve 21. The sleeve 21, the sleeve upper cover 22 and the sleeve The lower cylinder cover 23 is constructed by inserting an ejector pin (not shown) into the pin hole provided in the sleeve 21 and the pin holes 22a and 23a provided in the upper sleeve cover 22 and the lower sleeve cover 23, respectively. Integrate to rotate. Furthermore, the sleeve upper cover 22 is further fixed in the axial direction by the sleeve case cover 7a, so as to seal the hydraulic oil filled in the sleeve 21. As shown in FIG. In addition, the guide grooves 22c and 23c are eccentrically formed on the inner surfaces of the sleeve upper cover 22 and the sleeve lower cover 23 with respect to the rotation axis O of the sleeve 21 so that the eccentric direction is 180 degrees rotationally symmetrical. Further, in the sleeve lower cover 23, a pin hole 23e and a hydraulic oil injection hole 23f are formed. In addition, by inserting the pin 28 penetrating the sleeve case 7 into the pin hole 23e, the sleeve case 7 and the sleeve lower cover 23 are locked.

In the main shaft 9 coaxially arranged inside the sleeve 21 , two bosses 25 a and 25 b formed in a smooth shape on the surface are formed at positions that are rotationally symmetric by 180 degrees. The two bosses 25a and 25b of the main shaft 9 are formed to have lengths in the axial direction and the circumferential direction shorter than any of the hollow parts inside the sleeve 21 so as to form a passage for the flow of hydraulic oil. Both ends in the axial direction and the tip in the circumferential direction.

Two propeller blades 24a, 24b having a substantially triangular cross-section and having the same size and having a smooth shape on the surface are assembled inside the sleeve 21 and divided by the bosses 25a, 25b of the main shaft 9. Inside the cavity. The two transmission vanes 24a and 24b are such that the side surfaces of the transmission vanes 24a and 24b are slidably connected to the inner surfaces of the sleeve upper cover 22 and the sleeve lower cover 23 so that the length in the axial direction is equal to that of the inside of the sleeve 21 . The hollow portion has approximately the same length, and the sealing surfaces corresponding to the sealing surfaces 21a and 21b of the sleeve 21 are formed near both ends thereof, and are assembled to guides formed on the inner surfaces of the sleeve upper cover 22 and the sleeve lower cover 23. The pins 27a and 27b of the guide grooves 22c and 23c are formed on one of the side surfaces of the transmission blades 24a and 24b. The pins 27b of the transmission blade 24b are assembled to the guide grooves 22c of the sleeve upper cover 22, and the The pin 27a is assembled in the guide groove 23c of the sleeve lower cover 23, when the sealing surfaces 21a, 21b of the sleeve 21 and the sealing surfaces 24a, 24b of the drive blades 24a, 24b overlap each time the sleeve 21 rotates, the Once, by assembling the pins 27a, 27b of the transmission blades 24a, 24b to the guide grooves 22c, 23c formed by eccentricity between the inner surfaces of the sleeve upper cover 22 and the sleeve lower cover 23 and the rotation axis O of the sleeve 21 The movement of the transmission blades 24a and 24b is restricted to prevent overlapping, whereby an impact torque is generated to the main shaft 9 every time the sleeve 21 rotates.

On the outer peripheral surface of the sleeve 21, there is provided a communication groove 26 that communicates the hollow portions of the low-pressure chamber L in the interior of the sleeve 21, which are divided by the transmission vanes 24a, 24b and the sealing surfaces 21a, 21b of the sleeve 21. .

In addition, the output adjustment mechanism 10 that adjusts the magnitude of the impact torque in parallel with the axis of the sleeve 21 is provided in the sleeve 21 . This output adjustment mechanism 10 is conventionally known, and includes a hollow portion serving as a high-pressure chamber H and a low-pressure chamber L inside the sleeve 21 divided by the transmission vanes 24a, 24b and the sealing surfaces 21a, 21b of the sleeve 21. It consists of ports 10a and 10b which communicate with the hollow part of the sleeve, and an output adjustment valve 10c which is adjusted from an operation hole 23b provided in the lower sleeve cover 23 .

In addition, an accumulator 29 for absorbing thermal expansion of 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 vent member 29b, and is configured such that one end face of the piston 29a is communicated with the inside of the sleeve 21 through a small hole 23d for accumulator punched in the sleeve lower cover 23 The other end face communicates with the atmosphere via the vent member 29b, the small hole 22b for accumulator punched in 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 generator 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 the rotor is transmitted to the sleeve 21 .

By the rotation of the sleeve 21, the inside of the sleeve case 7 changes according to Fig. 12 (a)→(b)→(c)→(d)→(a)・・・. Fig. 12(a) shows the state in which the impact torque is not generated in the main shaft 9, whereby the state in which the sleeve 21 is rotated approximately 90 degrees at a time is shown in (b), (c) and (d).

When the impact torque is generated by the main shaft 9 as shown in Fig. 12(b), the sealing surfaces 21a and 21b of the sleeve 21 and the sealing surfaces of the transmission blades 24a and 24b overlap, 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 the impact torque is generated on the main shaft 9, the volume of the high pressure chamber H side decreases, and the volume of the low pressure chamber L side increases, and the respective chambers become the high pressure chamber H and the low pressure chamber L. In other words, when the sleeve 21 is rotated by the rotor 4, when the sealing surfaces 21a and 21b of the sleeve 21 and the sealing surfaces of the transmission vanes 24a and 24b are overlapped, the respective chambers become the high pressure chamber H and the low pressure chamber L, In addition, the drive vanes 24a and 24b are pushed to the low pressure chamber L side, the sealing surfaces 21a and 21b of the sleeve 21 and the seal surfaces of the drive vanes 24a and 24b overlap, and the hollow portion inside the sleeve 21 is completely sealed, and the sleeve 21 The rotational force of the shaft acts on the bosses 25 a and 25 b of the main shaft 9 via the transmission blades 24 a and 24 b, so that an impact torque is generated on the main shaft 9 . In addition, every time the sleeve 21 is rotated once, necessary operations such as rotation of the main shaft 9 by the impact torque generated intermittently, and tightening and loosening of bolts and nuts are performed.

On the other hand, as shown in Fig. 12(d), the sealing surfaces 21a and 21b of the sleeve 21 and the sealing surfaces of the propeller blades 24a and 24b are intended to overlap. 27a, 27b are assembled in the guide grooves 22c, 23c formed by the eccentricity between the inner surface of the sleeve upper cover 22 and the sleeve lower cover 23 and the rotation axis O of the sleeve 21 to restrict the movement of the transmission blades 24a, 24b, thereby , since the hollow portion inside the sleeve 21 is not in a sealed state, the impact torque is not generated in the main shaft 9 .

In addition, as shown in Fig. 12(a) and Fig. 12(c), when the sealing surfaces 21a and 21b of the sleeve 21 and the sealing surfaces of the propeller blades 24a and 24b reach the overlapping position, the respective chambers will instantaneously become high pressure The chamber H and the low pressure chamber L are pushed to the low pressure chamber L side by the transmission vanes 24a and 24b, so that the sealing surfaces 21a and 21b of the sleeve 21 and the sealing surfaces of the transmission vanes 24a and 24b do not overlap. The internal cavity is not sealed 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 impact torque is not generated on the main shaft 9 .

In addition, when the rotor 4 is rotated in the opposite direction, the inside of the sleeve case 7 changes according to Fig. 12 (d)→(c)→(b)→(a)→(d)... It is possible to generate the impact torque in the opposite direction to the main shaft 9 .

According to the hydraulic impact torque generator 5 described in FIGS. 1 to 6 and 7 to 12, there is an advantage that the conventional hydraulic torque wrench described in FIG. 21 is not required. The blade that is always pressed towards the outer circumference of the main shaft by the spring, which is necessary in the impact torque generating device of the 1000V, can obtain low sliding friction and good energy efficiency, and obtain a stable output with less temperature rise of the hydraulic oil, which is not only small, but also Simple and durable impact torque generator for hydraulic torque wrenches.

An object of the present invention is to provide a further improvement of the hydraulic impact torque generator 5 described in FIGS. 1 to 6 and 7 to 12, with a simpler structure, durability, and sliding Impact torque generator for hydraulic torque wrenches with less friction and better energy efficiency. [Technical means to solve problems]

In order to achieve the above-mentioned object, the impact torque generator for a hydraulic torque wrench of the present invention includes a sleeve having a cavity portion filled with hydraulic oil, and a sealing surface protruding from the inner peripheral surface of the cavity portion and using The main shaft is rotated by the rotor; the main shaft has two convex parts, which are coaxially arranged inside the sleeve; and the two transmission blades have sealing surfaces at both ends and are assembled in the hollow part of the sleeve filled with hydraulic oil. The inside of the sleeve is divided into a high-pressure chamber and a low-pressure chamber by the transmission blade, so that the impact torque is generated on the main shaft, and it is characterized in that: the sealing surface of the sleeve is formed into two at the 180° rotationally symmetrical position of the cavity, when the When the sealing surface of the sleeve overlaps with one of the sealing surfaces of the transmission blades, the other sealing surface is slidably connected to the inner peripheral surface of the cavity for sealing, so that the transmission blade divides the interior of the sleeve into a high-pressure chamber and low pressure chamber, so that the impact torque is generated on the main shaft.

In this case, the steel balls, which are fitted in the guide grooves formed on the inner surfaces of the sleeve upper cover and the sleeve lower cover, and restrict the movement of the transmission blades, are arranged on the side surface of one of the transmission blades. , which can generate an impact torque on the main shaft every time the sleeve rotates.

In addition, the sealing surfaces of the propeller blades may be formed of steel rods arranged in grooves formed in both end portions of the propeller blades.

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

In addition, the aforementioned propeller blades may be provided with magnetic force. [Inventive effect]

An impact torque generator for a hydraulic torque wrench according to the present invention, the impact torque generator for a hydraulic torque wrench has a sleeve having a cavity portion filled with hydraulic oil, and a cavity portion is provided from an inner peripheral surface of the cavity portion. The protruding seal surface is formed and rotated by the rotor; the main shaft has two protruding parts, which are coaxially arranged inside the sleeve; and the two transmission blades have sealing surfaces at both ends and are assembled in the hydraulic oil-filled The hollow part 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 the impact torque is generated on the main shaft. Two positions are formed. When the sealing surface of the sleeve coincides with one of the sealing surfaces of each transmission blade, the other sealing surface is slidably connected to the inner peripheral surface of the cavity for sealing, so that the transmission blade and the sleeve are sealed. The inside of the cylinder is divided into a high-pressure chamber and a low-pressure chamber so that the impact torque is generated on the main shaft. From the above point of view, the sealing surface of the sleeve corresponding to the other sealing surface of each transmission blade is divided into the inner part of the cavity. It is possible to omit the processing step of the hollow portion of the sleeve that substantially forms the sealing surface, and the structure is simplified, and a durable impact torque generator for a hydraulic torque wrench can be provided.

In addition, the steel balls, which are fitted into the guide grooves formed on the inner surfaces of the sleeve upper cover and the sleeve lower cover, and restrict the movement of the transmission blades, are arranged on one of the side surfaces of the transmission blades, so that the Each rotation of the sleeve generates an impact torque on the main shaft, thereby providing an impact torque generating device for a hydraulic torque wrench with less sliding friction and better energy efficiency.

In addition, by configuring the sealing surface of the propeller blade with a steel rod arranged in a groove formed at both ends of the propeller blade, it is possible to provide a hydraulic torque wrench with less sliding friction and better energy efficiency shock torque generator.

In addition, by forming the cross-sectional shape of the propeller blade to be asymmetrical, the stability of the operation of the propeller blade when used with the rotating shaft in the horizontal direction can be improved, and stable and efficient output can be obtained.

In addition, by imparting the magnetic force to the propeller blade, the magnetic powder generated by the abrasion of the components contained in the hydraulic oil is adsorbed to the propeller vane, thereby preventing the wear of the components due to the magnetic powder. In addition, the magnetic powder adsorbed to the drive vane can be easily removed by simply wiping the drive vane during maintenance.

Hereinafter, embodiments of the impact torque generator of the hydraulic torque wrench of the present invention will be described based on the drawings.

FIG. 13 to FIG. 16 show an embodiment of the impact torque generator of the hydraulic torque wrench according to the present invention.

This hydraulic shock torque generator 5 is a further improvement of the hydraulic shock torque generator 5 described in FIGS. 1 to 6 and 7 to 12, and has a simpler structure and durability. products with less sliding friction and better energy efficiency.

Furthermore, the basic structure is the same as that of the hydraulic impact torque generator 5 described in FIGS. 1 to 6 and 7 to 12. The sleeve 31 is installed in the sleeve case 7, and the The hydraulic oil is filled and sealed in the sleeve 31 , and the main shaft 9 is coaxially assembled into the sleeve 31 .

A substantially elliptical hollow portion is formed inside the sleeve 31 to which the spindle 9 is mounted, and the two sealing surfaces 31 a and 31 b are formed in a 180° rotationally symmetrical position on the inner peripheral surface of the sleeve 31 . The cylindrical sleeve 31 is supported by the sleeve shell 7 at its outer periphery, and the sleeve upper cover 32 and the sleeve lower cover 33 are arranged at both ends of the sleeve 31. The sleeve 31, the sleeve upper cover 32 and the sleeve The lower cylinder cover 33 is constructed by inserting an ejector pin (not shown) into a pin hole provided in the sleeve 31 and a pin hole respectively provided in the upper sleeve cover 32 and the lower sleeve cover 33 to form an integral body. turn. Furthermore, the sleeve upper cover 32 is further fixed in the axial direction with the sleeve case cover 7a, so as to seal the hydraulic oil filled in the sleeve 31. As shown in FIG. In addition, the inner surfaces of the sleeve upper cover 32 and the sleeve lower cover 33 are eccentric to the rotation axis O of the sleeve 31 to form the guide grooves 32c and 33c so that the eccentric direction is 180 degrees rotationally symmetrical. In addition, grooves for releasing hydraulic oil are formed at predetermined positions on the inner surfaces of the sleeve upper cover 32 and the sleeve lower cover 33 .

Here, the hydraulic shock torque generator 5 of the present embodiment is different from the hydraulic shock torque generator 5 described in FIGS. 1 to 6 and 7 to 12. The other sealing surfaces 31a', 31b' of the paired sealing surfaces 31a, 31b, in other words, the sealing surfaces of the sleeve 31 corresponding to the sealing surfaces of the respective propeller blades 34a, 34b described later, are defined as the inner circumference of the cavity. face to form. The inner peripheral surface of the hollow portion of the sleeve 31 constituting the sealing surfaces 31a' and 31b' is formed in a substantially cylindrical shape, and the angle ? This example is 50°). Thereby, by forming the two mountain-shaped sealing surfaces 31a, 31b, it is possible to omit the processing step of substantially forming the hollow portion of the sleeve 31 of the sealing surfaces 31a', 31b', the structure is simplified, and the durability can be provided. The shock torque generating device of the hydraulic torque wrench.

In the main shaft 9 coaxially arranged inside the sleeve 31 , two bosses 35 a and 35 b formed in a smooth shape on the surface are formed at positions that are rotationally symmetric by 180°. The two bosses 35a and 35b of the main shaft 9 are configured to be shorter in the axial direction and in the circumferential direction than any of the hollow parts inside the sleeve 31 so as to form a passage for the flow of hydraulic oil. Both ends in the axial direction and the tip in the circumferential direction.

The two propeller blades 34a and 34b having a substantially triangular cross-section and having the same size and formed in a smooth shape on the surface are assembled inside the sleeve 31 and divided by the bosses 35a and 35b of the main shaft 9. Inside the cavity. The two transmission vanes 34a and 34b are such that the side surfaces of the transmission vanes 34a and 34b are slidably connected to the inner surfaces of the sleeve upper cover 32 and the sleeve lower cover 33 so that the length in the axial direction is equal to that of the inside of the sleeve 31 . The hollow portion has approximately the same length, and the sealing surfaces corresponding to the sealing surfaces 31a, 31a', 31b, 31b' of the sleeve 31 are formed in the vicinity of both ends thereof, and are assembled to the sleeve upper cover 32 and the sleeve lower cover. The steel balls 37a and 37b of the guide grooves 32c and 33c on the inner surface of 33 are arranged on one of the side surfaces of the transmission blades 34a and 34b. groove 32c, the steel ball 37a of the transmission blade 34a is assembled to the guide groove 33c of the lower cover 33 of the sleeve, and the sealing surfaces 31a, 31a', 31b, 31b' of the sleeve 31 are made to be in contact with each other in each rotation of the sleeve 31. When the sealing surfaces of the transmission vanes 34a, 34b overlap twice, one of them is by assembling the steel balls 37a, 37b of the transmission vanes 34a, 34b to the inner surfaces of the sleeve upper cover 32 and the sleeve lower cover 33 and the sleeve The guide grooves 32c and 33c formed by the eccentricity of the rotating shaft O of the 31 restrict the movement of the transmission blades 34a and 34b to prevent the overlapping, whereby each rotation of the sleeve 31 generates an impact torque on the main shaft 9 .

Here, as described in FIGS. 7 to 12 , the guide grooves 22 c used in the hydraulic impact torque generator 5 for guiding and restricting the motion of the propeller blades 34 a and 34 b may be applied. The pins 27a, 27b of 23c are used in the present embodiment to replace the steel balls 37a, 37b fitted in the guide grooves 32c, 33c for guiding and restricting the movement of the transmission blades 34a, 34b.

Table 1 and Fig. 16 show the output (measured value measured by a digital torque tester) and its waveform of a comparative test using pins 27a, 27b and steel balls 37a, 37b.

From the results of the comparison test using the pins 27a, 27b and the steel balls 37a, 37b, it was confirmed that the steel balls 37a, 37b had lower sliding friction and better energy efficiency when compared with the pins 27a, 27b.

As shown in Fig. 15, the sealing surfaces of the propeller blades 34a and 34b can be constituted by steel rods 34d arranged in grooves 34c formed in both end portions of the propeller blades as necessary. As a result, it is possible to provide an impact torque generator for a hydraulic torque wrench with less sliding friction and better energy efficiency.

On the outer peripheral surface of the sleeve 31, cavities serving as the low-pressure chamber L in the inside of the sleeve 31, which are partitioned by the transmission vanes 34a, 34b and the sealing surfaces 31a, 31a', 31b, 31b' of the sleeve 31, are provided. Connected communication grooves (illustration omitted).

In addition, the sleeve 31 is provided with an output adjustment mechanism 10 that adjusts the magnitude of the impact torque in parallel with the axis of the sleeve 31 . This output adjustment mechanism 10 is conventionally known, and consists of a cavity inside the sleeve 31 that becomes the high-pressure chamber H, which is divided by the transmission vanes 24a, 24b and the sealing surfaces 31a, 31a', 31b, 31b' of the sleeve 31 It consists of a port (not shown) which communicates with the hollow part which becomes the low pressure chamber L, and an output regulating valve 10c which is adjustably screwed into a screw hole provided in the lower sleeve cover 33 .

In addition, an accumulator 39 for absorbing thermal expansion of hydraulic oil in parallel with the axis of the sleeve 31 is provided in the sleeve 31 .

The operation of the impact torque generator 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 the rotor is transmitted to the sleeve 31 .

By the rotation of the sleeve 31, the inside of the sleeve case 7 changes according to Fig. 14 (a)→(b)→(a)... . FIG. 14( a ) shows a state in which impact torque is generated in the main shaft 9 , whereby the state in which the sleeve 31 is rotated approximately 180° is shown in FIG. 14( b ).

When the impact torque is generated by the main shaft 9 as shown in Fig. 14(a), the sealing surfaces 31a, 31a', 31b, 31b' of the sleeve 31 and the sealing surfaces of the propeller blades 34a, 34b overlap, and the hollow inside the sleeve 31 The portion is divided into four chambers, and from the shape of the hollow portion inside the sleeve 31, the moment the impact torque is generated on the main shaft 9, the volume of the high-pressure chamber H side decreases, the volume of the low-pressure chamber L side increases, 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 surfaces 31a, 31a', 31b, 31b' of the sleeve 31 and the sealing surfaces of the propeller blades 34a, 34b reach the overlapping position, the respective chambers become high pressure chamber H and low pressure chamber L, and the transmission vanes 34a, 34b are pushed to the low pressure chamber L side, the sealing surfaces 31a, 31a', 31b, 31b' of the sleeve 31 coincide with the sealing surfaces of the transmission vanes 34a, 34b, the sleeve 31 The hollow portion inside is completely sealed, and the rotational force of the sleeve 31 acts on the bosses 35a, 35b of the main shaft 9 via the transmission blades 34a, 34b, and the impact torque is generated in the main shaft 9. In addition, every time the sleeve 31 is rotated once, necessary operations such as the rotation of the main shaft 9 by the impact torque generated intermittently, and the tightening and loosening of bolts and nuts are performed.

On the other hand, as shown in Fig. 14(b), the sealing surfaces 31a, 31a', 31b, and 31b' of the sleeve 31 overlap with the sealing surfaces of the propeller blades 34a and 34b. The steel balls 37a and 37b of 34a and 34b are assembled in the guide grooves 32c and 33c formed by the eccentricity between the inner surface of the sleeve upper cover 32 and the sleeve lower cover 33 and the rotation axis O of the sleeve 31 to restrict the transmission blades 34a and 33c. By the operation of 34b, since the hollow portion inside the sleeve 31 is not in a sealed state, impact torque is not generated in the main shaft 9. As shown in FIG.

In this way, other than the time shown in Fig. 14(a), the sealing surfaces 31a, 31a', 31b, 31b' of the sleeve 31 and the sealing surfaces of the propeller blades 34a, 34b do not overlap and seal.

In addition, when the rotor 4 is rotated in the reverse direction, an impact torque in the reverse direction can be generated in the main shaft 9 .

In addition, the other structures and functions of the hydraulic shock torque generator 5 are the same as those of the hydraulic shock torque generator 5 described in FIGS. 1 to 6 and 7 to 12. .

In addition, as for the mechanism for generating an impact torque on the main shaft 9 every time the sleeve 31 rotates, the steel fittings in the guide grooves 32c and 33c, which guide and restrict the movement of the transmission blades 34a and 34b, are not included. The balls 37a, 37b; and the guide grooves 22c, 34b that guide and restrict the movement of the propeller blades 34a, 34b described in FIGS. 7 to 12 and are used in the hydraulic impact torque generator 5 In addition to the pins 27a and 27b of 23c, the mechanism disclosed in Patent Document 1 may be employed.

In addition, since the hydraulic shock torque generator 5 has low sliding friction and good energy efficiency, it can be the same as the hydraulic shock torque generator 5 described in FIGS. 1 to 6. Each rotation of 31 generates two shock torques on main shaft 9 .

However, although this hydraulic shock torque generator 5 exhibits the above-mentioned effects, the following problems still exist. (1) The stability of the motion of the propeller blade when the rotating shaft is in the horizontal direction is low. (2) The magnetic powder generated by the abrasion of the parts contained in the hydraulic oil causes the parts to be worn out and reduces the durability of the device.

Figs. 17 to 20 show modified examples of the impact torque generating device of the hydraulic torque wrench of the present invention that can cope with this problem.

In order to cope with the above-mentioned problem (1), in this modified embodiment, the cross-sectional shapes of the propeller blades 34a and 34b are formed to be asymmetrical. Specifically, as shown in Fig. 17(c), in the cross-sectional shape of the propeller blades 34a and 34b, a raised portion 34e is formed on the left side with the center line Lo interposed therebetween, and the volume of the left half is formed to be smaller than that of the right side. Half the volume is large so that the center of gravity does not lie on the centerline Lo. As a result, as shown in FIG. 20 , in particular, when the rotating shaft whose motion of the propeller blades 34a and 34b is not easily stabilized is used in the horizontal direction, compared with the case in which the rotating shaft is used in the vertical direction with respect to the horizontal plane. The stability of the movement of the transmission blades 34a and 34b is improved, and stable and efficient output can be obtained.

Next, in order to cope with the above-mentioned problem (2), the transmission blades 34a and 34b are provided with magnetic force in this modified embodiment. Specifically, except as shown in Fig. 18(a) and Fig. 18(b), the magnet 38 is embedded in a portion not in contact with other members of the propeller blades 34a and 34b, or as shown in Fig. 18(c) As shown in the figure, in addition to attaching the magnet 38, the propeller blades 34a and 34b themselves may be magnetized. In addition, 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, and the like. Thereby, it is not affected by the resistance and the balance surface due to the contact with other members, and the magnetic powder generated by the abrasion of the components contained in the hydraulic oil is adsorbed to the transmission blades 34a and 34b, thereby preventing the A condition where magnetic powder wears out parts. In addition, the magnetic powder adsorbed to the transmission blades 34a and 34b can be easily removed by simply wiping the transmission blades 34a and 34b at the time of maintenance.

In addition, other structures and functions of the hydraulic shock torque generator 5 are the same as those of the hydraulic shock torque generator 5 described in FIGS. 13 to 16 .

In the above, the impact torque generating device of the hydraulic torque wrench of the present invention has been described based on its embodiment, but the present invention is not limited to the structure described in the above-mentioned embodiment. In addition to the motor, an electric motor or the like may be used, and the configuration may be appropriately changed within a range that does not deviate from the gist. [Industrial availability]

The impact torque generating device of the hydraulic torque wrench of the present invention has less sliding friction and better energy efficiency, less temperature rise of the hydraulic oil, and stable hydraulic The output has the characteristics of small size, simple structure, and durability, so it can be applied to hydraulic torque wrenches that use electric motors that cannot expect the air cooling effect brought by the high pressure air of the power source, and that require high tightening accuracy. In addition to the use of the hydraulic torque wrench, for example, it can also be applied to the use of the hydraulic torque wrench using an air motor.

1‧‧‧Main body 2‧‧‧Main valve 3‧‧‧Forward and reverse switching valve

4: Rotor

5: Impact torque generating device

6: Front shell

7: Sleeve shell

8: Sleeve

9: Spindle

10: Output adjustment mechanism

11: Sleeve

11a: sealing surface

11b: sealing surface

12: Sleeve upper cover

13: Sleeve lower cover

14a: Drive blades

14b: Drive blades

15a: Raised part

15b: Raised part

16: Connecting grooves

17: Ejector pin

21: Sleeve

21a: sealing surface

21b: sealing surface

22: Sleeve upper cover

22c: Guide groove

23: Sleeve lower cover

23c: Guide groove

24a: Drive blades

24b: Drive blades

25a: Raised part

25b: Raised part

26: Connecting grooves

27a: Pin

27b: pin

29: Accumulator

31: Sleeve

31a: sealing surface

31a’: sealing surface

31b: sealing surface

31b’: sealing surface

32: Sleeve upper cover

32c: Guide groove

33: Sleeve lower cover

33c: Guide groove

34a: Drive blades

34b: Drive blades

34c: groove

34d: Gangbang

34e: Bulge

35a: Raised part

35b: Raised part

37a: Steel ball

37b: Steel ball

38: Magnets

39: Accumulator

H: high pressure chamber

L: low pressure chamber

Lo: center line

S: spring

Fig. 1 shows an example of an impact torque generator of a hydraulic torque wrench, (a) is a front cross-sectional view, and (b) is an I-I cross-sectional view thereof. FIG. 2 is a diagram showing a propeller blade of the impact torque generator of this example. FIG. 3 is a diagram showing the main shaft of the impact torque generator of this example. FIG. 4 is a view showing a sleeve upper cover of the impact torque generator of this example. FIG. 5 is a view showing a sleeve lower cover of the impact torque generator of this example. FIG. 6 is a diagram showing the operation of the impact torque generator of this example. Fig. 7 shows another example of the impact torque generator of the hydraulic torque wrench, (a) is a front cross-sectional view, and (b) is a II-II cross-sectional view thereof. FIG. 8 is a diagram showing a propeller blade of the impact torque generator of this example. FIG. 9 is a diagram showing the main shaft of the impact torque generator of this example. Fig. 10 is a view showing a sleeve upper cover of the impact torque generator of this example. FIG. 11 is a view showing a sleeve lower cover of the impact torque generator of this example. FIG. 12 is a diagram showing the operation of the impact torque generator of this example. Fig. 13 shows an embodiment of the impact torque generator of the hydraulic torque wrench of the present invention, wherein (a) is a front cross-sectional view, and (b) is a III-III cross-sectional view thereof. Fig. 14 is a diagram showing the operation of the impact torque generating device of the embodiment. Fig. 15 is an exploded view of the propeller blade of the embodiment, (a) is a front view and (b) is a side view. Fig. 16 is a diagram showing an output and a waveform of a comparative test performed with a pin and a steel ball for restricting the motion of the propeller blade. Fig. 17 shows a modified example of the impact torque generator of the hydraulic torque wrench according to the present invention, (a) is a front sectional view, (b) is a IV-IV sectional view thereof, and (c) is a transmission Side view of the blade. Fig. 18 is an exploded view of the propeller blade according to the modified example, (a) is a front view, (b) is a side view, and (c) is a side view showing a different example. FIG. 19 is a diagram showing the operation of the impact torque generator of the modified example. FIG. 20 is a diagram showing an output waveform of a comparative test according to the modified example. Fig. 21 is a diagram showing the entirety of a hydraulic air wrench to which a conventional impact torque generator is attached.

10: Output adjustment mechanism

31a: sealing surface

31a’: sealing surface

31b: sealing surface

31b’: sealing surface

33c: Guide groove

34a: Drive blades

34b: Drive blades

35a: Raised part

35b: Raised part

37a: Steel ball

37b: Steel ball

39: Accumulator

H: high pressure chamber

L: low pressure chamber

Claims (4)

An impact torque generating device for a hydraulic torque wrench, comprising: a sleeve having a hollow portion filled with hydraulic oil inside, a sealing surface protruding from the inner peripheral surface of the hollow portion and being rotated by a rotor; a main shaft having two A raised portion is coaxially arranged inside the sleeve; and two transmission vanes have sealing surfaces at both ends and are assembled in the hollow portion of the sleeve filled with hydraulic oil. The interior is divided into a high-pressure chamber and a low-pressure chamber, and the impact torque is generated on the main shaft. It is characterized in that the cross-sectional shape of the transmission blade is asymmetrical, and the sealing surface of the sleeve is at a 180° rotationally symmetrical position in the cavity. Two are formed. When the sealing surface of the sleeve coincides with one of the sealing surfaces of each transmission blade, the other sealing surface is slidably connected to the inner peripheral surface of the cavity for sealing, so that the transmission blade and the sleeve are sealed. The internal area of the fuselage is divided into a high pressure chamber and a low pressure chamber, so that the impact torque is generated on the main shaft. The impact torque generating device of the hydraulic torque wrench according to the claim 1, wherein the guide grooves formed on the inner surfaces of the upper cover and the lower cover of the sleeve are assembled to restrict the movement of the transmission blades. The actuating steel ball is arranged on one side surface of each of the aforementioned transmission blades, so that an impact torque is generated on the main shaft every time the sleeve rotates. The impact torque generator for a hydraulic torque wrench according to claim 1 or claim 2, wherein the sealing surface of the propeller blade is a steel rod arranged in a groove formed at both ends of the propeller blade to constitute. The impact torque generating device for a hydraulic torque wrench according to claim 1 or claim 2, wherein the transmission blade has a magnetic force.

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