JP5836742B2 - Control device for tightening force of hydraulic torque wrench - Google Patents

Description

  The present invention relates to a control device for a tightening force of a hydraulic torque wrench, and more particularly, a control of a tightening force of a hydraulic torque wrench configured to measure a tightening force of a fastening member using an ultrasonic probe. It relates to the device.

  Conventionally, as a hydraulic torque wrench, a hydraulic torque wrench using a hydraulic impact torque generator with low noise and vibration has been developed and put to practical use (for example, see Patent Document 1).

9 to 10 show an example of this hydraulic torque wrench, and the impact torque generator T of this hydraulic torque wrench W fills the liner chamber La formed in the liner L with hydraulic oil. Then, a blade insertion groove Sa and a spring insertion hole Sb are provided on the main shaft S coaxially inserted into the liner L, and the blade Bl is inserted into the blade insertion groove Sa and the spring Sp is inserted into the spring insertion hole Sb. B1 is always urged by the spring Sp in the outer peripheral direction of the main shaft and brought into contact with the inner peripheral surface of the liner chamber La, and a seal surface is formed on the outer peripheral surface of the main shaft S and the inner peripheral surface of the liner chamber La.
When the liner L is rotated by the air motor R, the seal surface formed on the inner peripheral surface of the liner chamber La matches the seal surface formed on the outer peripheral surface of the main shaft S and the blades Bl. A striking torque is generated.

  In addition, as a hydraulic torque wrench, in addition to Patent Document 2 and Patent Document 3 previously proposed by the present applicant in order to solve problems such as wear of members of a conventional hydraulic torque wrench and breakage of a spring, etc. There is a description.

  Among them, the hydraulic torque wrench described in Patent Document 2 uses an air motor as a drive source, as shown in FIGS. 11 to 15. The main shaft 3 and the main shaft 3 are connected to the main shaft 3. The cam 4 is inserted so as to be slidable in the axial direction without rotating, the cam grooves 41a and 41b are formed on the outer peripheral surface, and the oil guide holes 42a and 42b penetrating in the axial direction are formed inside, and the main shaft 3 And the cam 4 of the cam 4 which protrudes on the inner peripheral surface of the cylinder C and the cylinder C which forms the oil chambers A and B filled with the hydraulic oil with the cam 4 interposed therebetween. Pins 81 and 82 inserted into the grooves 41a and 41b, a drive shaft 23 connected to a drive source (not shown) for rotationally driving the cylinder C, and the cam 4 according to the relative rotation angle of the cam 4 and the cylinder C Selectively close the oil guide holes 42a and 42b By, and a check valve 5 for blocking a flow of hydraulic oil between the oil chambers A, B formed across the cam 4.

  In this case, as shown in FIG. 11, the cylinder C is fitted to the outer casing 1 that constitutes one end face wall 11 and the cylinder part 12, and the other end face wall 21, cylinder part 22. The inner casing 2 constituting the drive shaft 23 and the opening end of the cylinder portion 12 of the outer casing 1 are screwed together to fix the inner casing 2 fitted to the outer casing 1 and integrate them. The fixing member 9 is constituted.

  Further, as shown in FIG. 11, the main shaft 3 in which the base end portion is accommodated in the cylinder C has a base hole 31a formed in the end wall 21 of the inner casing 2 via a ball bearing 24a. In order to insert the cam 4 so as to be slidable in the axial direction without rotating with respect to the main shaft 3, the cross-sectional shape of the shaft 31 of this portion is, for example, a polygonal shape, a spline shape, etc. In this example, it is formed in a hexagonal shape, and further, a flange portion 33 is formed on the tip side to prevent it from coming off, and the tip side penetrates and extends through the end face wall 11 of the outer casing 1.

  The cam 4 that is slidably inserted in the axial direction without rotating with respect to the main shaft 3 slides in the axial direction without rotating the cam 4 with respect to the main shaft 3, as shown in FIGS. In order to insert it in a possible manner, the cross-sectional shape of the hole 43 in this portion is formed in a hexagonal shape corresponding to the main shaft 3, for example.

The cam grooves 41a and 41b formed on the outer peripheral surface of the cam 4 are the inner casings of the cylinder C that are fitted into the cam grooves 41a and 41b when the cylinder C is rotationally driven through the drive shaft 23 connected to the drive source. For example, an annular spiral is used so that the cam 4 can be slid in the axial direction without rotating with respect to the main shaft 3 by the action of the pins 81 and 82 projecting from the inner peripheral surface of the second cylinder portion 22. Form into shape. By the way, although two cam grooves 41a and 41b are formed in this example, the number of cam grooves is not limited to this, and can be one or more than three. When a plurality of cam grooves 41a and 41b are formed as in this example, pins that protrude from the inner peripheral surface of the cylinder portion 22 of the inner casing 2 of the cylinder C and are inserted into the respective cam grooves are inserted. 81 and 82 are projected so as to have an equal angular interval (180 ° in this example).
Thus, by providing the plurality of cam grooves 41a and 41b and the pins 81 and 82, a large rotational driving force can be smoothly transmitted from the cylinder C to the cam 4 via the pins 81 and 82. The impact torque can be stably generated on the main shaft 3 into which the shaft 4 is inserted.

  Also, the oil guide holes 42a and 42b penetrating in the axial direction inside the cam 4 are oils formed so as to sandwich the cam 4 when the cam 4 slides in the axial direction without rotating with respect to the main shaft 3. Although it is not particularly limited so as to have a sufficient capacity to smoothly distribute the hydraulic oil between the chambers A and B, in this example, it is configured with two through holes. I have to.

  By selectively closing the oil guide holes 42a and 42b formed in the cam 4 according to the relative rotation angle of the cam 4 and the cylinder C, the operation between the oil chambers A and B formed with the cam 4 interposed therebetween. The check valve 5 that shuts off the oil flow is always disposed in one oil chamber A so as to abut against and be urged by one end of the cam 4 by a spring 6. Try to rotate.

  As shown in FIG. 14, the check valve 5 includes a disc-shaped main body portion 51 that is in contact with one end surface of the cam 4 and an annular portion 53 that extends along the inner peripheral surface of the cylinder portion 22 of the inner casing 2 of the cylinder C. It consists of.

  The main body 51 is formed with curved long holes 52a and 52b that are electrically connected to the oil guide holes 42a and 42b formed in the cam 4 and allow the hydraulic oil to flow between the oil chambers A and B. The oil guide holes 42a and 42b formed in the cam 4 are closed by a portion where the hole between the long holes 52a and 52b is not formed. Depending on the position and number of the long holes 52a and 52b formed in the main body 51, the number and magnitude of impact torque generated while the cam 4 and the cylinder C are rotated by 360 ° are determined.

  By forming the long holes 52a and 52b at the positions shown in this example, the oil guide holes 42a and 42b formed in the cam 4 by the check valve 5 each time the cam 4 and the cylinder C rotate 360 ° relatively. And the flow of hydraulic oil between the oil chambers A and B formed with the cam 4 interposed therebetween can be shut off, so that each time the cam 4 and the cylinder C rotate 360 ° relatively. In addition, a large impact torque can be generated once by utilizing the inertia of the cylinder C.

  Further, the cylinder portion 12 of the outer casing 1 of the cylinder C and the cylinder portion 22 of the inner casing 2 are formed with oil guide passages 15 and 25 connecting the oil chambers A and B formed with the cam 4 interposed therebetween, The output adjusting mechanism 13 that can arbitrarily adjust the magnitude of the impact torque generated by restricting the flow rate of the hydraulic oil flowing through the oil guide passages 15 and 25 is screwed into the end face wall 11 of the outer casing 1. It arrange | positions by doing. As a result, the output adjusting mechanism 13 is adjusted to limit the flow rate of the hydraulic oil flowing through the oil guide passage 25 connecting the oil chambers A and B formed with the cam 4 sandwiched between the cylinders C. The magnitude of the hitting torque to be generated can be easily adjusted. Specifically, as the flow rate of the working oil flowing through the oil guide passage 25 is reduced by adjusting the output adjusting mechanism 13, The magnitude can be increased, and conversely, the greater the flow rate of the working oil flowing through the oil guide path 25, the smaller the magnitude of the impact torque that can be generated.

  Further, the annular portion 53 is formed with a long hole 55 into which a pin 54 projecting from the inner peripheral surface of the cylinder portion 22 of the inner casing 2 of the cylinder C is inserted, whereby the check valve 5 is connected to the cylinder C. While being driven and rotated, the cam 4 is driven to slide while being in contact with one end surface of the cam 4.

  Further, a plug 14 for injecting hydraulic oil into the oil chambers A and B is disposed on the end surface wall 11 of the outer casing 1 by screwing or the like.

  Also, seals such as O-rings that prevent leakage of hydraulic fluid are provided between the outer casing 1 and the inner casing 2 of the cylinder C, between the outer casing 1 and the main shaft 3 of the cylinder C, the output adjusting mechanism 13, the plug 14, and the like. The members 71, 72, 73, 74 are arranged.

  Hereinafter, the operation of the impact torque generator of the hydraulic torque wrench will be described with reference to FIG. First, the cylinder C is rotationally driven (rotated clockwise as viewed from the drive shaft 23 side) via a drive shaft 23 connected with an air motor as a drive source.

  When the cylinder C is rotationally driven, the inside of the impact torque generating device is as shown in FIG. 15 (1) → (2) → (3) → (4) → (5) → (6) → (1). It changes as follows. FIG. 15 (1) shows a state in which no hitting torque is generated in the main shaft 3. From this, the state in which the cylinder C and the cam 4 are rotated by 60 degrees relative to each other in order (referenced to the cam 4) is shown in FIG. 2), (3) (state in which impact torque is generated in the main shaft 3), (4), (5), and (6).

  First, as shown in FIG. 15 (1), when the oil guide holes 42a and 42b formed in the cam 4 and the long holes 52a and 52b formed in the check valve 5 are electrically connected, the oil chambers A and B Therefore, the cam 4 in which the pins 81 and 82 projecting from the inner peripheral surface of the cylinder C are inserted and inserted freely in the axial direction without rotating with respect to the main shaft 3. The cam 4 can be slid from the right side to the left side when viewed from the front (in FIG. 11), and the hydraulic oil flows from the oil chamber B to the oil chamber A. In this state, Since the cylinder C and the cam 4 are not restrained, no hitting torque is generated.

  When the cylinder C is further rotated from this state, as shown in FIG. 15 (2), the oil guide holes 42 a and 42 b formed in the cam 4 and the long holes 52 a and 52 b formed in the check valve 5 become conductive. (The same state as FIG. 15 (1) where no impact torque is generated. However, the cam 4 slides from the left side to the right side when viewed from the front, and the hydraulic oil flows from the oil chamber A. The oil guide holes 42a and 42b formed in the cam 4 and the long holes 52a and 52b formed in the check valve 5 are electrically connected as shown in FIG. 15 (3). No state.

  In the state shown in FIG. 15 (3), the cam 4 slides from the left side to the right side when viewed from the front (in FIG. 11), so that the oil chamber A in the sliding direction is at a high pressure. The oil chamber B in the opposite direction becomes a low pressure. Then, the flow of hydraulic oil from the high-pressure oil chamber A to the low-pressure oil chamber B is interrupted. In this state, when the cylinder C is further driven to rotate and the cam 4 is slid in the axial direction, the oil Chamber A is at a higher pressure and oil chamber B is at a lower pressure. At this time, the pins 81 and 82 projecting from the inner peripheral surface of the cylinder C are strongly brought into contact with the side surfaces of the cam grooves 41a and 41b formed on the outer peripheral surface of the cam 4 on the high pressure oil chamber A side. However, since the flow of the hydraulic oil from the high pressure oil chamber A to the low pressure oil chamber B is blocked, the cam 4 is prevented from sliding, so that the side surfaces of the cam grooves 41a and 41b and the pins 81 and 82 Thus, a large frictional force is generated and the cylinder C and the cam 4 are restrained. Thereby, a rotational driving force can be transmitted from the cylinder C to the cam 4 via the pins 81 and 82, and an impact torque can be generated in the main shaft 3 into which the cam 4 is inserted.

  When the cylinder C is further rotated from this state, the oil guide holes 42a and 42b formed in the cam 4 and the check valve 5 are formed again as shown in FIGS. 15 (4) and 15 (5). State in which the long holes 52a and 52b are conducted (the same state as FIG. 15 (1) in which no impact torque is generated. However, in FIG. 15 (4), the cam 4 is viewed from the front (in FIG. 11). The hydraulic oil flows from the oil chamber A to the oil chamber B from the left side to the right side, while in FIG. 15 (5), the cam 4 is viewed from the front (in FIG. 11) from the right side. The hydraulic oil slides to the left and flows from the oil chamber B to the oil chamber A.), and as shown in FIG. 15 (6), the oil guide holes 42a and 42b formed in the cam 4 and the check valve 5, the long holes 52a and 52b formed in the state 5 are not conductive.

  In the state shown in FIG. 15 (6), the cam 4 slides from the right side to the left side when viewed from the front (in FIG. 11), so that the oil chamber B in the sliding direction is at a high pressure. The oil chamber A in the opposite direction becomes a low pressure. However, when the oil chamber B reaches a high pressure, unlike the state shown in FIG. 15 (3), the hydraulic pressure of the hydraulic oil in the oil chamber B passes through the oil guide holes 42 a and 42 b formed in the cam 4. The check valve 5 acting on the check valve 5 and resisting the urging force of the spring 6 is retracted so that the check valve 5 that is in contact with one end surface of the cam 4 is retracted, and the hydraulic oil from the high-pressure oil chamber B to the low-pressure oil chamber A Since the circulation is allowed, the cam 4 in which the pins 81 and 82 projecting from the inner peripheral surface of the cylinder C are inserted can be freely slid in the axial direction without rotating with respect to the main shaft 3. As a result, the cylinder C and the cam 4 are not restrained, so that no striking torque is generated.

  When the cylinder C is further rotated from this state, as shown in FIG. 15 (1), the oil guide holes 42a and 42b formed in the cam 4 and the long holes 52a and 52b formed in the check valve 5 are again formed. It is in a conductive state (a state where no hitting torque is generated).

  Thus, according to the impact torque generating device of this hydraulic torque wrench, the oil guide hole formed in the cam 4 by the check valve 5 substantially every time the cylinder C and the cam 4 rotate 360 ° relatively. 42a and 42b can be closed, and the flow of hydraulic oil between oil chambers A and B formed with the cam 4 interposed therebetween can be blocked, so that the cam 4 and the cylinder C are relatively 360 °. Each time it rotates, a large impact torque can be generated once using the inertia of the cylinder C.

  Further, when the air motor as the drive source is rotated in the reverse direction (left rotation as viewed from the drive shaft 23 side), the inside of the impact torque generating device is as shown in FIGS. 15 (1) → (6) → (5). → (4) → (3) → (2) → (1)... In this case, in the state of FIG. 15 (6), it is possible to generate a striking torque in the opposite direction to the main shaft 3.

  For example, by changing the position and number of the long holes 52a and 52b formed in the main body 51, the impact torque is generated a plurality of times while the cam 4 and the cylinder C relatively rotate 360 °. In addition to an air motor, an electric motor can be used as a drive source.

  By the way, the conventional hydraulic torque wrench is provided with an output adjustment mechanism so that the magnitude of the generated impact torque can be arbitrarily adjusted. This output adjustment mechanism limits the flow rate of hydraulic oil. It adjusts the magnitude of the impact torque generated by this, and does not directly measure the tightening force of a fastening member such as a bolt, so the tightening force of the fastening member could not be confirmed.

On the other hand, as a measuring device for directly measuring the fastening force of a fastening member such as a bolt, a measuring device that measures the fastening force of the fastening member using an ultrasonic probe Has been put into practical use (see, for example, Patent Documents 4 and 5).
However, this measuring device is generally configured separately from the wrench as described in Patent Document 4, and when configured integrally with the wrench, the rotating spindle is rotated. Since it is necessary to derive an electrically connected cable from the ultrasonic probe disposed at the tip, the electrical connection mechanism between the rotating member (main shaft) and the stationary member is particularly complicated, and the patent As described in Document 5, there is a problem that the socket body and the measurement socket are increased in size, and it is difficult to incorporate the measurement device into a hand-held hydraulic torque wrench.

By the way, in view of the problems of the conventional hydraulic torque wrench, the applicant of the present application measures the tightening force of the fastening member using an ultrasonic probe, and electrical connection therefor. A device for controlling the tightening force of a hydraulic torque wrench has been proposed (see, for example, Patent Document 6) that allows the mechanism to be simply configured.
This measuring device can solve the problems of the conventional hydraulic torque wrench, but the control device for the tightening force of the hydraulic torque wrench is built into the hydraulic torque wrench, so the maintenance effort and cost are reduced. A new problem of requiring a problem arises.

Japanese Utility Model Publication No. 1-29012 Japanese Patent No. 3361794 Japanese Patent No. 2804904 JP 2004-114182 A JP 2000-74764 A JP 2008-333471 A

  In view of the problems of the conventional hydraulic torque wrench described above, the present invention measures the tightening force of a fastening member using an ultrasonic probe and simplifies the electrical connection mechanism for the measurement. It is an object of the present invention to provide a tightening force control device for a hydraulic torque wrench that is configured as described above and that can be easily maintained.

In order to achieve the above object, the hydraulic torque wrench tightening force control device according to the present invention generates a striking torque via a striking torque generator rotated by a motor. In the control device for the tightening force of a hydraulic torque wrench with an ultrasonic probe arranged on the tip side of the spindle, the ultrasonic probe is arranged in a socket detachably arranged on the tip of the main shaft and, connecting the cable derived from the ultrasonic probe to the two electrodes of the pin-shaped and arranged in the axial direction of the position of the staggered diagonal positions of the socket, and the electrode, the outer peripheral portion of the socket A U-shaped composite in which two annular electrodes arranged on a support that rotatably supports the arranged socket and an inner end face of the electrode arranged in the socket are arranged in the center of the socket Supported by the outer surface of the resin spring member Each biasing toward the electrodes disposed on the body, potentially connected by sliding contact, characterized in that the electrode arranged on the support were to be connected to an external controller.

  In this case, a fitting member fitted to the fastening member can be detachably disposed at the tip of the socket.

  In addition, at least one of the electrodes in sliding contact can be made of a conductive solid lubricant material.

According to the tightening force control device for a hydraulic torque wrench of the present invention, an ultrasonic probe is disposed in a socket that is detachably disposed at the tip of the main shaft, and the ultrasonic probe is derived from the ultrasonic probe. The cable is connected to an electrode disposed on the socket, and the electrode is electrically connected by sliding the electrode disposed on the support body rotatably supporting the socket disposed on the outer periphery of the socket. By connecting the electrode disposed on the support to an external controller, it is possible to measure the tightening force of the fastening member using an ultrasonic probe, and an electrical connection mechanism. It can be easily arranged by placing it outside the wrench body, it can be easily applied to hand-held hydraulic torque wrench, and a socket with an ultrasonic probe is attached to the wrench body. Can be separated from the maintenance Kill for, it is possible to reduce the labor and cost required for the maintenance work.
In this case, the fastening force of the fastening member can be measured in real time while the fastening member is fastened or immediately after the fastening member is fastened, and the fastening force of the fastening member is controlled (fastening of the fastening member). (Control of the end time of work) and quality control can be performed with high accuracy.

  In addition, by providing a fitting member that fits to the fastening member in a detachable manner at the tip of the socket, a plurality of types of fitting members corresponding to fastening members such as bolts are prepared. The socket in which the ultrasonic probe is disposed can be shared, and the workability can be improved.

  Further, by forming at least one of the electrodes in sliding contact with a conductive solid lubricant material, a signal with little electrical noise can be stably transmitted over a long period of time.

  In addition, by urging the electrode disposed on the socket to the electrode disposed on the support by a U-shaped synthetic resin spring member, a signal with little electrical noise can be transmitted over a long period of time. Can be transmitted stably.

It is explanatory drawing which shows the Example of the hydraulic torque wrench to which the control apparatus of the clamping force of the hydraulic torque wrench of this invention is applied. It is a front view of a socket and a support body. It is a side view of a socket and a support body. It is front sectional drawing of a socket and a support body. It is side surface sectional drawing of a socket and a support body. A spring member is shown, (A) is a front view, (B) is a side view. It is front sectional drawing of the deformation | transformation Example of a socket and a support body. The fitting member is shown, (A) is a cross-sectional view, and (B) is a front view showing a state of being disposed in the socket. It is front sectional drawing which shows the hitting torque generator of the conventional hydraulic torque wrench. It is explanatory drawing which shows operation | movement of the hit | damage torque generator of the conventional hydraulic torque wrench. It is front sectional drawing which shows the hitting torque generator of the conventional hydraulic torque wrench. (A) is XX sectional drawing of FIG. 11, (B) is YY sectional drawing of FIG. A cam is shown, (A) is a front view, (B) is a side view. A check valve is shown, (A) is a front sectional view and (B) is a side view. It is explanatory drawing which shows operation | movement of the hit | damage torque generator of the conventional hydraulic torque wrench.

  Embodiments of a tightening force control device for a hydraulic torque wrench according to the present invention will be described below with reference to the drawings.

  FIG. 1 shows an embodiment of a hydraulic torque wrench to which a control device for tightening force of a hydraulic torque wrench according to the present invention is applied.

Various types of hydraulic torque wrench, such as normal pulse wrench, torque sensor built-in pulse wrench, torque sensor built-in stall tool, etc., can be applied to the hydraulic torque wrench. For example, as in the conventional impact torque generating device described in FIGS. 9 to 10, the blade chamber groove La is formed in the liner L, filled with hydraulic oil, and inserted into the main shaft S coaxially with the liner L. Sa and a spring insertion hole Sb are provided, the blade Bl is inserted into the blade insertion groove Sa, the spring Sp is inserted into the spring insertion hole Sb, and the blade Bl is always urged by the spring Sp toward the outer periphery of the main shaft. A striking torque generator is used which is brought into contact with the inner peripheral surface of the chamber La and has a seal surface formed on the outer peripheral surface of the main shaft S and the inner peripheral surface of the liner chamber La. To have.
When the liner L is rotated by the air motor R, the seal surface formed on the inner peripheral surface of the liner chamber La matches the seal surface formed on the outer peripheral surface of the main shaft S and the blades Bl. A striking torque is generated.

  The hydraulic torque wrench W is a measuring means for tightening the hydraulic torque wrench so that an ultrasonic probe Se is disposed on the distal end side of the main shaft S of the hydraulic torque wrench W and is necessary. Accordingly, an angle sensor and a torque sensor (not shown) are provided.

  The ultrasonic probe Se uses a property in which a fastening member such as a bolt is tightened to cause elastic deformation, and the propagation time of the ultrasonic wave propagating through the fastening member changes according to the elongation. The probe of the ultrasonic probe Se is brought into contact with the head surface of the fastening member, and the difference in propagation time until the ultrasonic wave transmitted toward the tip of the fastening member is received as an echo is measured. It calculates the tightening force (axial force) of the tightened fastening member, and can measure the tightening force with high accuracy.

  In this embodiment, as shown in FIGS. 2 to 6, the ultrasonic probe Se is disposed in a socket So that is detachably disposed at the distal end portion of the main shaft S. A cable Ca1 led out from the probe Se is connected to a pin-shaped electrode E1 disposed on the socket So, and a support body Su that rotatably supports the electrode E1 and the socket So disposed on the outer periphery of the socket So. The electrode E1 disposed on the support Su is electrically connected by sliding contact with the annular electrode E2 disposed on the outer surface of the support Su, specifically, the sensor controller Con1 or The tool controllers Con2, Con3, etc. are connected.

  In this case, the support body Su supports the socket So via the bearing Be and fixes it to the hydraulic torque wrench W via an appropriate attachment (not shown).

Further, as shown in the modified examples shown in FIGS. 7 to 8, the fitting member So <b> 1 that fits the fastening member can be detachably disposed at the tip of the socket So.
Thus, by preparing a plurality of types of fitting members corresponding to fastening members such as bolts, the socket So provided with the ultrasonic probe Se can be shared, and the workability is improved. be able to.

In addition, at least one of the electrodes E1 and E2 that are in sliding contact with each other, in this embodiment, the electrode E1 disposed in the socket So, an electrically conductive solid lubricant material, specifically, copper, tin, nickel, etc. The conductive metal is made of a sintered metal in which a solid lubricant made of a layered lattice structure material such as tungsten disulfide or graphite is dispersed.
Thereby, a signal with little electrical noise can be stably transmitted over a long period of time.

Further, the electrode E1 disposed in the socket So is biased to the electrode E2 disposed on the support body Su by a U-shaped synthetic resin spring member Usp.
In this case, a synthetic resin such as a polycarbonate resin, a polyacetal resin, or a polyether ether ketone resin can be used as the synthetic resin constituting the spring member Usp.
Thereby, a signal with little electrical noise can be stably transmitted over a long period of time.

According to this tightening force control device for a hydraulic torque wrench, the tightening force of the fastening member can be measured using the ultrasonic probe Se, and the electrical connection mechanism is connected to the wrench body W0. It can be arranged outside and can be easily constructed, and can be easily applied to a hand-held hydraulic torque wrench W. Further, a socket So provided with an ultrasonic probe Se is provided with a wrench body. Since maintenance can be performed separately from W0, it is possible to reduce the labor and cost required for maintenance work.
In addition, when the socket So is consumed, a member such as the ultrasonic probe Se can be detached from the worn socket So and assembled to a new socket So.
In this case, the fastening force of the fastening member can be measured in real time while the fastening member is fastened or immediately after the fastening member is fastened, and the fastening force of the fastening member is controlled (fastening of the fastening member). (Control of the end time of work) and quality control can be performed with high accuracy.

  As described above, the control device for the tightening force of the hydraulic torque wrench according to the present invention has been described based on a plurality of embodiments. However, the present invention is not limited to the configuration described in the above-described embodiments, Other known systems (for example, a hitting torque generating device described in Patent Document 3) may be applied to the device, or an electric motor may be applied instead of an air motor as a drive source motor. The configuration can be changed as appropriate without departing from the spirit of the invention, such as application to a stationary hydraulic torque wrench having a plurality of main shafts.

  The tightening force control device for a hydraulic torque wrench according to the present invention measures the tightening force of a fastening member using an ultrasonic probe, and easily configures an electrical connection mechanism therefor. In addition, since maintenance can be performed easily, it can be suitably used for hand-held hydraulic torque wrenches that require high-precision management of the tightening force of the fastening members, as well as other hydraulic pressures. It can also be used for the application of a torque wrench.

W Hydraulic Torque Wrench W0 Wrench Main Body A Oil Chamber B Oil Chamber C Cylinder T Impact Torque Generator L Liner La Liner Chamber S Spindle Sa Blade Insertion Slot Sb Spring Insertion Hole Bl Blade Su Support Sp Spring So Socket So1 Fitting Member R Air motor (motor)
Se ultrasonic probe Ca1 cable Ca2 cable Con controller E1 electrode E2 electrode Usp Spring member 1 Outer casing 11 End face wall 12 Cylinder part 13 Output adjustment mechanism 2 Inner casing 21 End face wall 22 Cylinder part 3 Main shaft 4 Cam 41a, 41b Cam groove 42a, 42b Oil guide hole 5 Check valve 6 Spring 71, 72, 73, 74 Seal member 81, 82 Pin 9 Fixing member

Claims (3)

Tightening of a hydraulic torque wrench in which an ultrasonic probe is disposed on the tip side of a main shaft of a hydraulic torque wrench that generates a hammering torque via a hammering torque generator rotated by a motor in the control unit of the force, arranged an ultrasonic probe into the socket which is detachably attached to the distal end of the main shaft, the cable derived from the ultrasonic probe by shifting the axial position of the socket Two annular electrodes connected to two pin-shaped electrodes disposed at diagonal positions and disposed on a support that rotatably supports the electrodes and the socket disposed on the outer periphery of the socket Are supported by the outer surface of a U-shaped spring made of synthetic resin disposed at the center of the socket and directed toward the electrode disposed on the support. biasing potential connected by sliding contact The support control unit of the clamping force of the hydraulic torque wrench, characterized in that the provided with electrodes to be connected to an external controller.   2. The apparatus for controlling a tightening force of a hydraulic torque wrench according to claim 1, wherein a fitting member fitted to a fastening member is detachably disposed at a front end portion of the socket.   3. The control device for a tightening force of a hydraulic torque wrench according to claim 1, wherein at least one of the electrodes in sliding contact is made of a conductive solid lubricating material.

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