JP6476942B2 - Torque limiter - Google Patents

Description

  The present invention relates to a torque limiter.

  Conventionally, as a torque limiter, there are some which are indicated in JP, 2011-185401, A (patent documents 1). FIG. 4 is an axial schematic cross-sectional view of the conventional torque limiter.

  The torque limiter is configured by externally fitting the inner peripheral surface 221 of the cylindrical member 201 to the outer peripheral surface 220 of the shaft member 202 and supplying oil to the annular hydraulic expansion chamber 226 of the cylindrical member 201. The diameter of the inner peripheral surface 221 of the cylindrical member 201 is reduced by the above-mentioned oil. Then, the inner peripheral surface 221 is pressed against the outer peripheral surface 220 of the shaft member 202 due to the diameter reduction, and the torque is transmitted by frictionally coupling the shaft member 202 and the cylindrical member 201. The torque limiter seals the oil in the hydraulic expansion chamber 226 with the shear valve 206.

  When a load of a predetermined value or more is applied to the shaft member 202 or the cylindrical member 201, the inner peripheral surface 221 of the cylindrical member 201 slips against the outer peripheral surface 220 of the shaft member 202, and the cylindrical member 201 When the relative rotation is performed, the radial outer end portion 261 of the shear valve 206 is cut by the cutting portion 209 of the shaft member 202, and the oil of the hydraulic pressure expansion chamber 226 is discharged to the outside. As a result, the pressing of the outer peripheral surface 220 of the shaft member 202 by the inner peripheral surface 221 of the cylindrical member 201 is released, the frictional coupling between the shaft member 202 and the cylindrical member 201 is released, and the transmission of torque is interrupted.

  In this torque limiter, the cylindrical member 201 is configured of a first cylindrical member 211 having a hydraulic pressure expansion chamber 226 and a second cylindrical member 210 having a frictional engagement surface. The first cylindrical member 211 is formed by annularly welding two cylindrical members 250 and 251 at one side and the other side in the axial direction. The hydraulic expansion chamber 226 is provided between the annular welding portion 270 on one side and the annular welding portion 271 on the other side. By pressing the outer peripheral surface 223 of the second cylindrical member 210 with the inner peripheral surface 224 of the first cylindrical member 211, the frictional engagement surface (the inner peripheral surface 221) of the second cylindrical member 210 is a shaft member It is in frictional engagement with the frictional engagement surface of 202 (the outer circumferential surface 220).

  Since this torque limiter comprises the cylindrical member 201 with two members, the force generated by the expansion of the hydraulic expansion chamber 226 can be efficiently transmitted to the frictional engagement surface, and a large frictional force is generated on the frictional engagement surface. Can be generated.

2011-185401 gazette

  The inventors have found the following problems with the conventional torque limiter.

  That is, in the above-described conventional torque limiter, the cylindrical member 201 needs to be configured by the two members 210 and 211, so there is a problem that the manufacturing cost is high. In addition, since the first cylindrical member 211 and the second cylindrical member 210 must be fitted by cold fitting or the like, when the size of the cylindrical member 201 is increased, processing and assembly of the two cylindrical members 210 and 211 are performed. It becomes difficult. Further, since the cylindrical member 201 is constituted by the first cylindrical member 211 and the second cylindrical member 210 and the number of parts is large, the thickness of each of the first and second cylindrical members 210 and 211 is thin. Become. Therefore, due to the small thickness of the first and second cylindrical members 210 and 211, the first and second cylindrical members 210 and 211 are easily distorted at the time of processing, and the first and second cylindrical members It is difficult to process 210 and 211.

  On the other hand, when the cylindrical member is constituted by only one member in order to avoid these problems, in order to generate sufficient frictional force on the frictional engagement surface, in comparison with the case where the cylindrical member is constituted by two parts, It is necessary to set the pressure of the oil in the hydraulic expansion chamber to a high pressure. However, in this case, due to the high oil pressure, the weld forming the hydraulic expansion chamber is easily broken.

  Therefore, the object of the present invention is to facilitate assembly, to reduce the manufacturing cost, to easily secure the wall thickness, to be easily processed, and to generate an appropriate frictional force on the frictional engagement surface, An object of the present invention is to provide a torque limiter that can suppress breakage of a weld for defining an expansion chamber.

In order to solve the above problems, the torque limiter of the present invention is
Shaft member,
A cylindrical member externally fitted to the shaft member;
One member of the cylindrical member and the shaft member is an integral member, and the one member is between the one member and the other member of the cylindrical member and the shaft member. When transmitting torque, the peripheral surface pressed against the peripheral surface of the other member, and a hydraulic pressure expansion chamber for pushing the peripheral surface against the peripheral surface of the other member,
The one member has a first annular portion and a second annular portion opposed to the first annular portion via the hydraulic pressure expansion chamber, and the first annular portion and the second annular portion And at one end of the hydraulic pressure expansion chamber, welding is performed by an annular first welding portion, and at the other end of the hydraulic pressure expansion chamber, welding is performed by an annular second welding portion;
In each of the first welding portion and the second welding portion, the first annular portion and the second annular portion overlap in the axial direction of the one member.

  Note that the term “overlap in the axial direction” means that they overlap when viewed from the axial direction.

  As described in detail in the subsequent examples, the inventor examined the stress around the weld portion of the torque limiter with a known residual stress inspection device. As a result, it was found that a large tensile stress was generated at the axial corner of the liquid reservoir connected to the end of the hydraulic pressure expansion chamber.

  According to the present invention, in the first and second welds for welding the first annular portion and the second annular portion, the first annular portion and the second annular portion overlap in the axial direction of one member Therefore, each of the first and second welds is disposed at a position away from the axial corner of the liquid pool where the stress is high. Therefore, since the first and second welded portions are less likely to break, the hydraulic pressure expansion chamber can withstand a larger hydraulic pressure than in the past, and the hydraulic pressure of the hydraulic pressure expansion chamber can be increased. Therefore, sufficient frictional force can be obtained on the frictional engagement surface even if it is an integral and indivisible part which is easy to assemble and process, and it is easy to assemble and process one of the two parts conventionally. Therefore, the assemblability and processability can be improved, the manufacturing cost can be reduced, an appropriate frictional force can be generated on the circumferential surface to be pressed, and the fracture of the weld for defining the hydraulic expansion chamber can also be suppressed. .

In one embodiment,
The one member is the cylinder member,
The hydraulic pressure expansion chamber extends in the axial direction of the cylindrical member,
The cylindrical member communicates with one side in the axial direction of the hydraulic pressure expansion chamber and has one side liquid reservoir extending in the axial direction, and on the other axial side of the hydraulic pressure expansion chamber. Communicating and having the other side liquid reservoir extending in the axial direction,
The first welded portion is exposed to the outer peripheral surface of the cylindrical member and the inner surface of the one side liquid reservoir, while the second welded portion is exposed to the inner peripheral surface of the cylindrical member and the inner surface of the other side liquid pool And
The outer diameter of the portion where the first welded portion is exposed on the outer peripheral surface of the cylindrical member is greater than the outer diameter of the portion overlapping the second welded portion in the radial direction of the cylindrical member on the outer peripheral surface of the cylindrical member small.

  The term “overlap in the radial direction” as used herein means overlap when viewed from the radial direction.

  According to the above embodiment, the first welded portion is exposed to the inner surface of the one side liquid reservoir and reaches the inner surface of the one side liquid reservoir, so the strength of the first welded portion can be increased. It is possible to further suppress breakage of the weld. Similarly, since the second weld is exposed to the inner surface of the other liquid pool and reaches the inner surface of the other liquid pool, the strength of the second weld can be increased. Can be further suppressed.

  Further, according to the above embodiment, the outer diameter of the portion where the first welded portion is exposed in the outer peripheral surface of the cylindrical member is the portion where the outer diameter of the cylindrical member overlaps the second welded portion in the radial direction of the cylindrical member. Since it is smaller than the outer diameter, the material cost of the cylindrical member can be reduced, and the first welded portion can easily reach the inner surface of the one side liquid reservoir.

In one embodiment,
The portion of the inner circumferential surface of the cylindrical member where the second welded portion is exposed is spaced apart from the shaft member.

  According to the above-mentioned embodiment, since the portion to which the 2nd welding part is exposed in the inner skin of the above-mentioned cylinder member is spaced apart to a shaft member, the 2nd welding part is pressed. It is not exposed to the circumferential surface, and the second welded portion does not constitute a part of the circumferential surface to be pressed. Therefore, the homogeneity of the material property of the peripheral surface to be pressed can be maintained, and a reliable and sufficient frictional force can be generated on the peripheral surface to be pressed.

  According to the torque limiter of the present invention, the assemblability can be improved, the manufacturing cost can be reduced, the thickness can be easily secured, the processing can be facilitated, and an appropriate frictional force can be generated on the frictional engagement surface. Thus, breakage of the weld for defining the hydraulic pressure expansion chamber can also be suppressed.

It is a schematic cross section of the axial direction of the torque limiter of one Embodiment of this invention. It is a figure which shows one test result when the stress around the oil reservoir of a torque limiter is test | inspected with a residual stress test | inspection apparatus. It is a figure which shows one test result when the stress around the oil reservoir of a torque limiter is test | inspected with a residual stress test | inspection apparatus. It is a schematic cross section of the axial direction of the conventional torque limiter.

  Hereinafter, the present invention will be described in detail by the illustrated embodiments.

  FIG. 1 is an axial schematic cross-sectional view of a torque limiter according to an embodiment of the present invention.

  The torque limiter includes an integral and indivisible shaft member 1, an integral and indivisible cylindrical member 2, a shear valve 6, a ball bearing 17 and a ball bearing 18. The cylindrical member 2 constitutes one member, and the shaft member 1 constitutes the other member.

  The shaft member 1 has a main body portion 8 having a substantially cylindrical outer peripheral surface 20 and a cutting portion 9 having a substantially L-shaped cross section protruding from the outer surface of the main body portion 8. The cylindrical member 2 has a substantially cylindrical inner circumferential surface 21 that abuts on the outer circumferential surface 20 of the shaft member 1. The inner circumferential surface 21 of the cylindrical member 2 constitutes a circumferential surface pressed against the circumferential surface of the other member, and the outer circumferential surface 20 of the shaft member 1 constitutes a circumferential surface of the other member. Lubricant oil for preventing seizure is applied between the outer peripheral surface 20 of the shaft member 1 and the inner peripheral surface 21 of the cylindrical member 2.

  The cylindrical member 2 has a shear valve mounting hole 50 and an annular hydraulic expansion chamber 26 extending substantially in the axial direction of the cylindrical member 2. The hydraulic pressure expansion chamber 26 constitutes a hydraulic pressure expansion chamber. The shear valve 6 is inserted into the shear valve mounting hole 50. The shear valve 6 has a tube 27 opened at only one end. The tube 27 extends substantially in the radial direction of the shaft member 1 in a state where the shear valve 6 is inserted into the shear valve mounting hole 50. Further, in a state where the shear valve 6 is inserted into the shear valve mounting hole 50, the other end on the closing side of the tube 27 protrudes outward in the radial direction from the outer peripheral surface of the cylindrical member 2. An opening on the opposite side to the closed side of the tube 27 communicates with the hydraulic expansion chamber 26. With the shear valve 6 fitted in the shear valve mounting hole 50, the other end of the shear valve 6 protrudes radially outward from the outer peripheral surface of the cylindrical member 2.

  The cut portion 9 having a substantially L-shaped cross section has a radially extending portion 30 and an axially extending portion 31. The radially extending portion 30 extends substantially in the radial direction and axially faces the end surface of the cylindrical member 2. On the other hand, the axially extending portion 31 is connected to the radially outward end of the radially extending portion 30. The axially extending portion 31 extends in the axial direction along the outer peripheral surface of the cylindrical member 2. The other end portion of the shear valve 6 circumferentially overlaps the axially extending portion 31 of the cutting portion 9.

  The cylindrical member 2 has a first annular portion 61 and a second annular portion 62 opposed to the first annular portion 61 via the hydraulic pressure expansion chamber 26. The first annular portion 61 and the second annular portion 62 are welded together by an annular first welding portion (welding portion of welding) 71 at one end side of the hydraulic expansion chamber 26, while the first annular portion 61 and the second annular portion 62 are At the other end side, welding is performed by an annular second welding portion (welding portion of welding) 72. As shown in FIG. 1, in each of the first welding portion 71 and the second welding portion 72, the first annular portion 61 and the second annular portion 62 overlap in the axial direction of the cylindrical member 2 (cylindrical member They overlap when viewed from the 2 axis direction).

  The cylindrical member 2 includes a first oil reservoir 81 as a first liquid reservoir and a second oil reservoir 82 as a second liquid reservoir. As shown in FIG. 1, the one side oil reservoir 81 communicates with one side of the hydraulic expansion chamber 26 in the axial direction, while the other oil reservoir 82 communicates with the other side of the hydraulic expansion chamber 26 in the axial direction. ing. Each of the one side oil reservoir 81 and the other side oil reservoir 82 extends in the axial direction. As shown in FIG. 1, while the said 1st welding part 71 is exposed to the radial direction outward side of the outer peripheral surface 28 of the cylinder member 2, and the inner surface of the one side oil reservoir 81, the 2nd welding part 72 is a cylinder. The radially inner side of the inner circumferential surface 29 of the member 2 and the inner surface of the other side oil reservoir 82 is exposed.

  As shown in FIG. 1, the outer diameter of the portion 91 where the first welded portion 71 is exposed at the outer peripheral surface 28 of the cylindrical member 2 is the same as that of the cylindrical member 2 at the second welded portion 72 at the outer peripheral surface 28 of the cylindrical member 2. The diameter is smaller than the outer diameter of the radially overlapping portion (portion overlapping when viewed from the radial direction of the cylindrical member 2) 92. The inner diameter of the portion 93 where the second welded portion 72 is exposed in the inner peripheral surface 29 of the cylindrical member 2 matches the inner diameter of the inner peripheral surface 21 of the cylindrical member 2. On the other hand, the outer peripheral surface of the shaft member 1 has an outer peripheral surface (frictional engagement surface) 20 having a large outer diameter, and an outer peripheral surface 25 having a smaller outer diameter, and the outer peripheral surface 25 having a small outer diameter is The inner circumferential surface 29 of the cylindrical member 2 is radially opposed to a portion 93 where the second welded portion 72 is exposed. The portion 93 where the second welded portion is exposed on the inner peripheral surface 29 of the cylindrical member 2 is located at a distance from the shaft member 1.

  The ball bearing 17 is disposed between the inner ring 40 externally fitted and fixed to the outer surface of the shaft member 1, the outer ring 41 internally fitted and fixed to the inner surface of the cylindrical member 2, and the raceway surface of the inner ring 40 and the raceway surface of the outer ring 41 And a ball 42 disposed. Further, the ball bearing 18 includes an inner ring 44 fixed to the outer surface of the shaft member 1, an outer ring 45 fixed to the inner surface of the cylindrical member 2, a raceway surface of the inner ring 44 and a raceway surface of the outer ring 45. And a ball 46 disposed between them. The ball bearings 17 and 18 rotatably support the shaft member 1 with respect to the cylinder member 2 when the shaft member 1 is rotating relative to the cylinder member 2. In FIG. 1, reference numerals 51 and 52 denote seal members. The seal member 51 seals the opening on one side in the axial direction of the ball bearing 17, and the seal member 52 seals the opening on the other side in the axial direction of the ball bearing 18.

  In the above configuration, when a load (a load in a range for transmitting torque) is applied to the shaft member 1 or the cylindrical member 2 after being applied to the shaft member 1 or the cylinder member 2, after being injected into the hydraulic pressure expansion chamber 26 via a coupler not shown. The inner peripheral surface 21 (corresponding to the frictional engagement surface of the cylindrical member 2) of the cylindrical member 2 is reduced in diameter by the sealed oil for hydraulic expansion, and the outer peripheral surface 20 of the shaft member 1 (axial member 1), the inner peripheral surface 21 of the cylindrical member 2 and the outer peripheral surface 20 of the shaft member 1 are frictionally coupled to transmit torque between the shaft member 1 and the cylindrical member 2 Do. Each of the inner circumferential surface 21 of the cylindrical member 2 and the outer circumferential surface 20 of the shaft member 1 constitutes a frictional engagement surface.

  On the other hand, a load (a load greater than the range for transmitting the torque) having a predetermined value or more is applied to the shaft member 1 or the cylindrical member 2, and the outer peripheral surface 20 of the shaft member 1 is against the inner peripheral surface 21 of the cylindrical member 2 When the axial position of the shaft member 1 and the cylinder member 2 changes, the cutting unit 9 cuts the other end of the shear valve 6 and oil for hydraulic expansion in the hydraulic expansion chamber 26 Is discharged to the outside through the shear valve 6 whose other end is cut. Thus, the pressing force of the inner peripheral surface 21 of the cylindrical member 2 against the outer peripheral surface 20 of the shaft member 1 is eliminated, and the friction coupling between the shaft member 1 and the cylindrical member 2 is broken to block the transmission of torque. ing. In this manner, when an overload occurs on the shaft member 1 or the cylinder member 2, the transmission of torque is interrupted to protect the expensive machine connected to the torque limiter device.

  FIGS. 2 and 3 are diagrams showing one inspection result when the stress around the oil reservoir 181 of the torque limiter is inspected by a known residual stress inspection device. The oil reservoir 181 shown in FIGS. 2 and 3 is an oil reservoir corresponding to the one-side oil reservoir 81 of the above embodiment. Further, referring to FIGS. 2 and 3, in the upper right column, the hatching indicated by the direction of arrow A (lower side of the drawing) indicates a portion where tensile stress is higher.

  As shown in FIGS. 2 and 3, in the axially extending oil reservoir 181 communicating with the hydraulic expansion chamber 126 in the axial direction, a large stress (tensile stress) is opposite to the hydraulic expansion chamber 126 in the axial direction. The curved portion 141 of the On the other hand, as shown in FIG. 3, no large stress is generated around the radially outer surface 151 of the oil reservoir 181 and the radially inner surface 152 of the oil reservoir 181. Therefore, when welding is performed on the radially outer side and the inner side of the oil reservoir 181, breakage of the welded portion can be suppressed.

  According to the above embodiment, in the first and second welded portions 71 and 72 for welding the first annular portion 61 and the second annular portion 62, the first annular portion 61 and the second annular portion 62 are cylindrical members. Since the first and second welds 71 and 72 overlap with each other in the axial direction of the second embodiment, the first and second welds 71 and 72 can be disposed radially outward and inward of the oil reservoirs 81 and 82, respectively. Each of the welds 71 and 72 is disposed at a position away from the curved part on the opposite side of the high stress oil reservoirs 81 and 82 in the axial direction of the hydraulic expansion chamber 26. Therefore, since the first and second welded portions 71 and 72 are less likely to break, the hydraulic expansion chamber 26 can withstand a larger hydraulic pressure than in the past, and the hydraulic pressure of the oil in the hydraulic expansion chamber 26 can be increased. Therefore, even if one of the cylindrical member and the shaft member, which has conventionally been constituted by two parts, is an integral integral part that is easy to assemble, sufficient frictional force is obtained at the frictional engagement surfaces 20 and 21. Can. Therefore, the assemblability can be improved, the manufacturing cost can be reduced, and an appropriate frictional force can be generated on the frictional engagement surfaces 20 and 21, and fracture of the welds 71 and 72 for defining the hydraulic expansion chamber 26. Can also be suppressed.

  Moreover, since the cylindrical member 2 which was conventionally comprised by two components can be made into one component, the grinding process of the mating surface of one cylinder component and the other cylinder component is unnecessary, and an assembly becomes easy. Further, although not described in detail, in contrast to the conventional case, a collar portion for positioning the other cylindrical member with respect to one cylindrical member can be omitted. Therefore, the manufacturing cost can also be reduced. In addition, since the cylindrical member, which is conventionally constituted by two parts, can be made into one part, the dimension in the radial direction can be reduced, and the dimension in the radial direction can be made compact. Further, unlike the conventional case, since the oil reservoirs at both ends of the hydraulic pressure expansion chamber extend in the axial direction, the radial size of the hydraulic pressure expansion chamber is reduced, and as a result, the radial dimension can be reduced. From this, material costs and processing costs can be reduced. In addition, the welded portion on one side in the axial direction can be changed from the end face in the axial direction of the cylindrical member 2 to the outer peripheral surface of the cylindrical member 2 so that the structure can be easily processed.

  Further, according to the above-described embodiment, since the first welded portion 71 is exposed to the inner surface of the first oil reservoir 81 and reaches the inner surface of the first oil reservoir 81, the strength of the first welded portion 71 can be reduced. It can be enlarged, and the fracture of the first welded portion 71 can be further suppressed. Similarly, since the second welded portion 72 is exposed to the inner surface of the other oil reservoir 82 and reaches the inner surface of the other oil reservoir 82, the strength of the second welded portion 72 can be increased, Breakage of the second welded portion 72 can be further suppressed.

  Further, according to the above embodiment, the outer diameter of the portion 91 where the first welded portion 71 is exposed in the outer peripheral surface 28 of the cylindrical member 2 is the cylindrical member in the second welded portion 71 in the outer peripheral surface 28 of the cylindrical member 2 Since the material cost of the cylindrical member 2 can be reduced because it is smaller than the outer diameter of the radially overlapping portion 92, the first welded portion 71 can easily reach the inner surface of the one-side oil reservoir 81.

  Further, according to the above-described embodiment, the portion 93 where the second welded portion 72 is exposed in the inner peripheral surface 29 of the cylindrical member 2 is located at a distance from the shaft member 1. The welded portion 72 is not exposed to the inner peripheral surface (frictional engagement surface) 21 of the cylindrical member 2, and the second welded portion 72 is a part of the inner peripheral surface (frictional engagement surface) 21 of the cylindrical member 2. There is no configuration. Therefore, the homogeneity of the material characteristics of the inner peripheral surface (frictional engaging surface) 21 can be maintained, and the outer peripheral surface 20 of the shaft member 1 which is the frictional engaging surface and the inner peripheral surface 21 of the cylindrical member 2 are reliable and sufficient. It can generate frictional force.

  Further, according to the above-described embodiment, the portion of the inner circumferential surface 29 of the cylindrical member 2 where the second welded portion 72 is exposed is located radially outward of the frictional engagement surface 21 of the cylindrical member 2. Therefore, the material cost of the cylindrical member 2 can be reduced, and the second welded portion 72 can easily reach the inner surface of the other oil reservoir 82.

  In the above embodiment, the first and second welds (penetration parts of the weld) 71 and 72 are exposed on the inner surfaces of the oil reservoirs 81 and 82 and reach the oil reservoirs 81 and 82, respectively. However, one or both of the first and second welds (penetration of welds) may not be exposed to the inner surface of the oil sump, and may not reach the oil sump.

  Further, in the above embodiment, the outer diameter of the portion 91 where the first welded portion 71 is exposed in the outer peripheral surface 28 of the cylindrical member 2 corresponds to the second welded portion 71 in the outer peripheral surface 28 of the cylindrical member 2. The diameter is smaller than the outer diameter of the radially overlapping portion 92. However, the outer diameter of the portion where the first welded portion is exposed on the outer peripheral surface of the cylindrical member is the same as the outer diameter of the portion overlapping the second welded portion in the radial direction of the cylindrical member on the outer peripheral surface of the cylindrical member Also, it may be larger than that.

  In the above embodiment, the outer peripheral surface of the shaft member 1 has the friction engagement surface 20 having a large outer diameter and the outer peripheral surface 25 having a smaller outer diameter, and the outer peripheral surface 25 has a small outer diameter. The second welded portion 72 is formed on the inner peripheral surface 29 of the cylindrical member 2 so as to face in the radial direction with an interval in the portion where the second welded portion 72 is exposed in the inner peripheral surface 29 of the cylindrical member 2. The exposed portion 93 was prevented from contacting the shaft member 1. However, the inner circumferential surface of the cylindrical member has a portion where the second welding portion is exposed, which has a large inner diameter, and a frictional engagement surface which has a smaller inner diameter than that, and a portion where the second welding portion is exposed is You may make it not contact a shaft member.

  Further, in the above embodiment, while the cylindrical member 2 is one member, the shear valve mounting hole 50 and the hydraulic expansion chamber 26 exist in the cylindrical member 2, the shaft member 1 is the other member, and the shaft member 1 is There was a cutting portion 9 for cutting one end of the shear valve 6. However, while the shaft member is one member, the shear valve mounting hole and the hydraulic pressure expansion chamber exist in the shaft member, the cylindrical member is the other member and the one end of the shear valve is cut into the cylindrical member. A cut may be present. In this configuration, for example, the shaft member is provided with a shear valve mounting hole opened in the axial direction at the end face in the axial direction of the shaft member, while the cylindrical member is radially extended along the above end face of the shaft member And an end portion of the shear valve fitted in the shear valve mounting hole at an end portion of the shear valve axially projecting from the end face of the shaft member. It can implement | achieve easily by providing the cutting part which overlaps with the circumferential direction of an axial member.

  In the above embodiment, the hydraulic pressure expansion chamber 26 is an annular chamber, but the hydraulic pressure expansion chamber may not be annular. In the above embodiment, the liquid filled in the hydraulic expansion chamber 26 as the hydraulic expansion chamber is oil, but the liquid filled in the hydraulic expansion chamber may be any liquid other than oil, such as water. . Of course, a new embodiment can be constructed by combining two or more of all the configurations described in the above embodiment and the modification.

Reference Signs List 1 shaft member 2 cylinder member 6 shear valve 26 hydraulic expansion chamber 61 first annular portion of cylinder member 62 second annular portion of cylinder member 71 first welded portion of cylinder member 72 second welded portion of cylinder member 81 one of cylinder members Side oil reservoir 82 The other side oil reservoir 91 of the cylindrical member 91 A portion where the first welded portion is exposed on the outer peripheral surface of the cylindrical member 92 A portion that overlaps the second welded portion in the radial direction of the cylindrical member on the outer peripheral surface of the cylindrical member The exposed part of the second weld on the inner circumferential surface of the member

Claims (3)

Shaft member,
A cylindrical member externally fitted to the shaft member;
One member of the cylindrical member and the shaft member is an integral member, and the one member is between the one member and the other member of the cylindrical member and the shaft member. When transmitting torque, the peripheral surface pressed against the peripheral surface of the other member, and a hydraulic pressure expansion chamber for pushing the peripheral surface against the peripheral surface of the other member,
The one member has a first annular portion and a second annular portion opposed to the first annular portion via the hydraulic pressure expansion chamber, and the first annular portion and the second annular portion And at one end of the hydraulic pressure expansion chamber, welding is performed by an annular first welding portion, and at the other end of the hydraulic pressure expansion chamber, welding is performed by an annular second welding portion;
In each of the first welding portion and the second welding portion, the first annular portion and the second annular portion overlap in the axial direction of the one member ,
The one member is the cylinder member,
The hydraulic pressure expansion chamber extends in the axial direction of the cylindrical member,
The cylindrical member communicates with one side in the axial direction of the hydraulic pressure expansion chamber and has one side liquid reservoir extending in the axial direction, and on the other axial side of the hydraulic pressure expansion chamber. Communicating and having the other side liquid reservoir extending in the axial direction,
The first welding portion is exposed to the outer peripheral surface of the cylindrical member,
The outer diameter of the portion where the first welded portion is exposed on the outer peripheral surface of the cylindrical member is greater than the outer diameter of the portion overlapping the second welded portion in the radial direction of the cylindrical member on the outer peripheral surface of the cylindrical member A torque limiter characterized by its small size . In the torque limiter according to claim 1,
The torque is characterized in that the first welding portion is exposed to the inner surface of the one side liquid reservoir, and the second welding portion is exposed to the inner peripheral surface of the cylindrical member and the inner surface of the other side liquid reservoir. limiter. In the torque limiter according to claim 2,
A torque limiter characterized in that a portion of the inner circumferential surface of the cylindrical member where the second welded portion is exposed is spaced apart from the shaft member.

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