JP4816702B2 - Anti-vibration joint - Google Patents

Description

  The present invention relates to a vibration-proof joint that couples an input shaft and an output shaft to transmit torque and suppress the occurrence of torsional vibration.

With regard to a joint for connecting an input shaft and an output shaft, for example, in a joint used in a power transmission device of an automobile, it is possible to transmit a large torque and to suppress the generation of torsional vibration over a wide range of rotational speeds. Desired.
Examples of shaft couplings (vibration-proof joints) that are connected between the input and output shafts to transmit torque and suppress the occurrence of torsional vibration are disclosed in, for example, Japanese Patent Application Laid-Open No. 2000-31433 and The one disclosed in Japanese Patent No. 3106310 is known.

  In the joint described in Japanese Patent Application Laid-Open No. 2000-31433, a rubber is interposed between two connectors, a first peak portion and a second peak portion are formed on the rubber, and the first peak portion is deformed by contact. This is intended to provide a vibration-proofing effect, and to secure a required power transmission force by contact deformation of the second peak portion. However, according to this vibration-proof joint, power is transmitted through rubber, so that it is difficult to apply when both high-speed rotation and transmission of large torque are required. In other words, if the rubber coupling has sufficient torque transmission performance, the dimension becomes too large, causing imbalance, and high speed rotation becomes difficult. On the other hand, if the size is reduced so that high-speed rotation is possible, the strength of the rubber will be insufficient, resulting in damage.

  The joint described in Japanese Patent No. 3106310 is provided with two rotating disks, a leaf spring, a viscous coupling and the like between two attachment elements. This joint converts rotational displacement into axial displacement, and can transmit large torque at high speed. However, this joint has a problem that the mechanism is complicated and the axial dimension becomes too large. Furthermore, precise processing such as an inclined disk or a spline is required, which increases the number of parts, which is not preferable in terms of manufacturing man-hours and costs.

  The present invention has been made in view of the above circumstances, and provides a vibration-proof joint that can transmit both large torque and can easily suppress generation of torsional vibration over a wide range of rotation speeds. Objective.

  In order to solve the above-described problem, the vibration-proof joint according to claim 1 includes a first joint element connected to the input shaft or the output shaft, and an input shaft different from the shaft connected to the first joint element or A second joint element coupled to an output shaft, the second joint element being axially displaced with respect to the first joint element and supported rotatably; the first joint element; A plurality of contact indenters interposed between two joint elements, and an elastic member interposed between the contact indenter and at least one of the joint elements and allowing axial displacement of the contact indenter. A plurality of elastic members that transmit a torque of a substantially predetermined magnitude between the two joint elements by balancing with the axial force of the torque transmitted by the contact indenter being displaced in the axial direction by rotation of the joint element. And the contact formed on the contact indenter A damping means for attenuating a torque fluctuation component by sliding friction acting between a child side sliding surface and a surface facing the contact indenter side sliding surface, wherein the first joint element and An intermediate ring element is interposed between the second joint element, and the surface facing the contact indenter side sliding surface is a ring element side sliding surface formed on the intermediate ring element, and the first joint element Between the contact ring and the intermediate ring element, the contact indenter provided such that the sliding surface on the contact indenter side is slidably in contact with the sliding surface on the ring element side of the intermediate ring element; The elastic member interposed between the first joint element and the intermediate ring element is disposed between the intermediate ring element and the second joint element. Slidably contact the ring element side sliding surface It said contact indenter provided to, and wherein said that an elastic member is arranged to be interposed between the this contact indenter second coupling element.

According to this configuration, it is possible to separately receive the steady component and the fluctuation component of the torque transmitted between the input shaft and the output shaft. In other words, the steady torque component is transmitted between the first and second joint elements by the deformation of the elastic member along with the displacement of the contact indenter and the balance with the axial force of the torque. Thus, even a large torque can be easily transmitted by adjusting the number of contact indenters and the elastic constant of the elastic member, and the contact indenter is displaced in the axial direction. It is almost unaffected and becomes substantially constant in all rotation speed ranges. The torque fluctuation component that generates torsional vibration is also attenuated by the sliding friction acting on the contact indenter and can be easily absorbed regardless of the operating rotational speed. Therefore, it is possible to provide a vibration-proof joint that can transmit both large torque and can easily suppress generation of torsional vibration over a wide range of rotation speeds.
Further, an intermediate ring element is disposed between the first joint element and the second joint element, a contact indenter is brought into contact therewith, and an elastic member is provided on each of the first and second joint elements. The elastic constants of the elastic members on the side of the first and second joint elements can be in a parallel coupled state. Thereby, the elastic constant of each elastic member can be set low.

  According to a second aspect of the present invention, in the vibration-proof joint according to the first aspect, the contact indenter side sliding surface is a surface inclined with respect to the displacement direction of the contact indenter, and the ring side sliding surface is the contact indenter side. It is characterized by being capable of sliding contact with a sliding surface.

According to this configuration, it is possible to easily displace the contact indenter in the axial direction by the rotation of the joint element, thereby deforming the elastic member together with the displacement of the contact indenter to balance the torque with the axial force, Can communicate.
In addition, when a torque meter is attached to the joint to measure the torque between the input and output shafts, it is necessary to hang a weight by attaching an arm to the end of the joint when calibrating the torque meter. If the relative rotation angle between the one joint element and the second joint element is large, the calibration work cannot be performed without removing the joint itself or newly installing a lock mechanism for preventing rotation. However, according to the configuration of the second aspect, the torque is transmitted through the contact of the sliding surface inclined with respect to the displacement direction of the contact indenter. Therefore, the sliding distance when the torque acts can be shortened, The relative rotation angle between the first joint element and the second joint element can be reduced. Therefore, it is possible to prevent troubles in calibration of the torque meter.

  According to a third aspect of the present invention, in the vibration-proof joint according to the first or second aspect, in addition to the friction between the contact indenter side sliding surface and the ring element side sliding surface, the damping means includes the side surface of the contact indenter and the first The torque fluctuation component is attenuated by friction with one joint element or the second joint element.

  According to this configuration, in the vibration-proof joint including the contact indenter provided in slidable contact with the first joint element and the contact indenter provided in slidable contact with the second joint element, the damping function can be efficiently performed. It is possible to easily realize a damping means that can be exhibited.

  A vibration-proof joint according to a fourth aspect of the present invention is the vibration-proof joint according to any one of the first to third aspects, wherein the intermediate ring element is a first joint element or a second joint as another damping means that attenuates torque fluctuation components in addition to the damping means. A sliding contact portion capable of sliding contact with the joint element by relative displacement in the rotational direction is formed in the intermediate ring element and the first joint element or the second joint element.

  According to this configuration, the number of places where relative friction occurs due to the torque fluctuation component increases, so that a higher damping effect can be exhibited.

  According to a fifth aspect of the present invention, in the vibration-proof joint according to any one of the first to fourth aspects, the first joint element is provided with a projecting shaft portion projecting at a shaft center portion, and around the projecting shaft portion. An encircling cylindrical elastic cylindrical member is disposed, the intermediate ring element is formed with a cylindrical boss portion in the center, and the protruding shaft portion penetrates the boss portion together with the other cylindrical elastic member. It is characterized by that.

  According to this configuration, sliding friction can be generated with respect to the cylindrical elastic member by the relative rotational displacement generated between the protruding shaft portion of the first joint element and the boss portion of the intermediate ring element. Thereby, in addition to the damping means by the sliding friction between the first and second joint elements or the intermediate ring element and the contact indenter, other damping means for damping the torque fluctuation component can be easily attached by mounting the cylindrical elastic member. Can be configured. In addition, the presence of the cylindrical elastic member can realize a structure in which radial eccentricity and inclination between the input and output shafts are easily allowed.

  According to a sixth aspect of the present invention, in the vibration-proof joint according to any one of the second to fifth aspects, the contact indenter side sliding surface and the ring element side sliding surface are formed in a conical shape.

  According to this configuration, a contact indenter having a sliding surface inclined with respect to the displacement direction of the contact indenter can be easily formed, and mass production can be easily performed even when a large number of contact indenters are required. Further, since both the contact indenter side sliding surface and the ring element side sliding surface are formed in a conical surface, the contact state between the sliding surfaces is easily kept substantially constant, and galling is not likely to occur. A structure that easily allows the inclination between the input and output shafts can be realized.

  According to the first aspect of the present invention, the steady component and the fluctuation component of the torque transmitted between the input shaft and the output shaft can be separately received. In other words, the steady torque component is transmitted between the first and second joint elements by the deformation of the elastic member along with the displacement of the contact indenter and the balance with the axial force of the torque. Thus, even a large torque can be easily transmitted by adjusting the number of contact indenters and the elastic constant of the elastic member, and the contact indenter is displaced in the axial direction. It is almost unaffected and becomes substantially constant in all rotation speed ranges. The torque fluctuation component that generates torsional vibration is also attenuated by the sliding friction acting on the contact indenter and can be easily absorbed regardless of the operating rotational speed. Therefore, it is possible to provide a vibration-proof joint that can transmit both large torque and can easily suppress generation of torsional vibration over a wide range of rotation speeds. Further, an intermediate ring element is disposed between the first joint element and the second joint element, a contact indenter is brought into contact therewith, and an elastic member is provided on each of the first and second joint elements. The elastic constants of the elastic members on the side of the first and second joint elements can be in a parallel coupled state. Thereby, the elastic constant of each elastic member can be set low.

According to the second aspect of the present invention, it is possible to easily displace the contact indenter in the axial direction by rotation of the joint element, thereby deforming the elastic member together with the displacement of the contact indenter to balance the axial force of the torque. Torque can be transmitted.
In addition, when a torque meter is attached to the joint to measure the torque between the input and output shafts, it is necessary to hang a weight by attaching an arm to the end of the joint when calibrating the torque meter. If the relative rotation angle between the one joint element and the second joint element is large, the calibration work cannot be performed without removing the joint itself or newly installing a lock mechanism for preventing rotation. However, according to the configuration of the second aspect, the torque is transmitted through the contact of the sliding surface inclined with respect to the displacement direction of the contact indenter. Therefore, the sliding distance when the torque acts can be shortened, The relative rotation angle between the first joint element and the second joint element can be reduced. Therefore, it is possible to prevent troubles in calibration of the torque meter.

  According to the invention of claim 3, in the vibration-proof joint including the contact indenter provided in slidable contact with the first joint element and the contact indenter provided in slidable contact with the second joint element, Attenuating means that can exhibit the attenuating function can be easily realized.

  According to the fourth aspect of the present invention, the number of places where relative friction is generated by the torque fluctuation component increases, so that a higher damping effect can be exhibited.

  According to the invention of claim 5, sliding friction can be generated with respect to the cylindrical elastic member by the relative rotational displacement generated between the protruding shaft portion of the first joint element and the boss portion of the intermediate ring element. Thereby, in addition to the damping means by the sliding friction between the first and second joint elements or the intermediate ring element and the contact indenter, other damping means for damping the torque fluctuation component can be easily attached by mounting the cylindrical elastic member. Can be configured. In addition, the presence of the cylindrical elastic member can realize a structure in which radial eccentricity and inclination between the input and output shafts are easily allowed.

  According to the invention of claim 6, a contact indenter having a sliding surface inclined with respect to the displacement direction of the contact indenter can be easily formed, and mass production is easy even when a large number of contact indenters are required. Yes. Further, since both the contact indenter side sliding surface and the ring element side sliding surface are formed in a conical surface, the contact state between the sliding surfaces is easily kept substantially constant, and galling is not likely to occur. A structure that easily allows the inclination between the input and output shafts can be realized.

  Hereinafter, vibration-proof joints according to reference embodiments and embodiments of the present invention will be described with reference to the drawings. The vibration-proof joint according to the embodiment described below is widely applicable as a shaft joint that connects the input shaft and the output shaft, but for example, as a joint used in a power transmission device of an automobile or the like. This is suitable when it is required to transmit a large torque and to suppress the generation of torsional vibrations over a wide range of rotational speeds. Further, it is particularly suitable when used in a test apparatus for automobiles.

(First Reference Embodiment)
FIG. 1 shows a vibration-proof joint 1 according to a first reference embodiment. Fig.1 (a) is the schematic diagram which showed the axial direction cross section of the vibration proof joint 1, and FIG.1 (b) has shown principal part sectional drawing. In FIG. 1A, a vibration-proof joint 1 includes a first joint element 11 connected to an input shaft or output shaft (not shown), and an input shaft or output shaft different from the shaft connected to the first joint element 11. And a second joint element 12 to be connected. That is, when the first joint element 11 is connected to the input shaft, the second joint element 12 is connected to the output shaft, and when the first joint element 11 is connected to the output shaft, the second joint element 12 is connected to the input shaft. Concatenated with

  And the 1st joint element 11 and the 2nd joint element 12 are each formed with the flange parts 13 and 14 which oppose. That is, the flange surface 13a in the flange portion 13 on the first joint element 11 side and the flange surface 14a in the flange portion 14 on the second joint element 12 side face each other, and the relative distance between these flange surfaces 13a and 14a. They are supported by an angular bearing or the like (not shown) so that L is constant. As a result, the second joint element 12 is supported rotatably with respect to the first joint element 11 while restraining the axial displacement.

  A plurality of recesses 15 are formed on the flange surface 13a, and a plurality of recesses 16 are formed on the flange surface 14a. These recessed parts 15 and 16 are arrange | positioned on the same periphery in each flange surface (13a, 14a), and the recessed part 15 and the recessed part 16 are provided in the position which mutually opposes. A pair of (two) recesses 15 are located on the flange surface 14a at positions where the pair of (two) recesses 15 are symmetric with respect to each other about the axis C on the flange surface 13a. It is arranged at a position that is point-symmetric about the axis center C.

  A plurality of contact indenters 17 and a plurality of elastic members 18 are interposed between the first joint element 11 and the second joint element 12. Each contact indenter 17 is provided so as to be slidably in contact with the first joint element 11 so that a part of the contact indenter 17 is fitted in each recess 15 of the first joint element 11. The elastic member 18 is made of a spring and is disposed so as to be housed in the recess 16 of the second joint element 12, and is interposed between each contact indenter 17 and the second joint element 12. Yes. Due to the expansion and contraction of the elastic member 18, the axial displacement of the contact indenter 17 is allowed.

  FIG. 1A shows an axial cross section of the vibration-proof joint 1, and a pair of contact indenters 17 and an elastic member 18 are illustrated. On the other hand, FIG.1 (b) has shown the principal part cross section which illustrated in part the AA arrow directional cross section of Fig.1 (a). As shown in FIGS. 1A and 1B, the contact indenter 17 is formed as a short columnar block having a hexagonal cross section in which a trapezoid and a rectangle are combined, and is formed so as to protrude into a trapezoid shape. The contact indenter 17 and the first joint element 11 are in contact with each other so that the formed portion (trapezoidal portion 19) is fitted into the recess 15.

  A contact indenter side sliding surface 19 a that is inclined with respect to the displacement direction (axial direction) of the contact indenter 17 is formed in the trapezoidal portion 19 (portion in contact with the first joint element 11). The sliding surfaces 19 a are formed on both side surfaces of the trapezoidal portion 19, and both sliding surfaces 19 a, 19 a are arranged on the same circumference with the axis center C as the center. And in the recessed part 15 of the 1st joint element 11, the joint element side sliding surface 15a which can be slidably contacted with the contact indenter side sliding surface 19a is formed.

  For example, when the first joint element 11 is an input shaft and rotation is started, the contact indenter 17 is pushed in the axial direction via the slip between the joint element side sliding surface 15a and the contact indenter side sliding surface 19a. 2 Displacement toward the joint element 12 side. At this time, the spring 18 is elastically deformed and contracted between the contact indenter 17 and the recess 16, so that the axial force for transmitting the torque between the first joint element 11 and the second joint element 12 is increased. Will occur. The reaction force generated by elastic deformation of the spring 18 is balanced with the axial force of the torque, so that a torque having a substantially predetermined magnitude is transmitted between the joint elements. Note that the angle α formed by the contact indenter side sliding surface 19a and the rotational circumferential direction of the first joint element 11 (the angle α formed by the sliding surface 19a and the flange surface 13a) is set smoothly in the range of 20 to 70 °. Although a predetermined torque can be transmitted to the motor, it is easy to maintain a balanced state between the reaction force of the spring 18 and the axial force of the torque by setting it in the vicinity of 45 °. Further, since the torsion spring constant of the vibration-proof joint 1 is proportional to the magnitude of α, the desired torsion spring constant can be set by adjusting α.

  In addition, the vibration-proof joint 1 includes a damping unit that attenuates a torque fluctuation component by sliding friction acting on the contact indenter 17. This damping means attenuates the torque fluctuation component by friction between the first joint element 11 and the contact indenter 17, and attenuates the torque fluctuation component by friction between the contact indenter side sliding surface 19a and the joint element side sliding surface 15a. And a damping means D2 that attenuates torque fluctuations by friction between the side surface 20 of the contact indenter 17 and the inner wall surface 21 of the recess 16 in the second joint element 12.

  In addition to the above-described damping means, the vibration-proof joint 1 includes other damping means D3 that attenuates torque fluctuation components. The other damping means D3 is constituted by a throttle mechanism formed by a gap between the side surface 20 of the contact indenter 17 and the second joint element 12. That is, an orifice is formed by the gap t between the side surface 20 of the contact indenter 17 and the inner side surface 21 of the recess 16, and the dynamic pressure resistance when air flows through the gap t along with the axial displacement of the contact indenter 17. Can exhibit a damping function.

  Next, the operation of the vibration-proof joint 1 will be described. In FIG. 1, it is assumed that the first joint element 11 is connected to the input shaft and the second joint element 12 is connected to the output shaft. When the first joint element 11 starts rotating together with the input shaft, a slip occurs between the joint element side sliding surface 15a and the contact indenter side sliding surface 19a, the contact indenter 17 is pushed in the axial direction, and the spring 18 is deformed. To do. The slip is stopped when the axial force generated by the rotational torque and the reaction force by the spring 18 are balanced. In this state, a predetermined magnitude of torque (steady torque) is transmitted from the first joint element 11 to the second joint element 12.

  When the rotational speed is increased in a state where the steady torque is being transmitted and the rotational speed reaches the vicinity of the resonance frequency f of the vibration system in which the vibration proof joint 1 is used, the torque fluctuation component becomes the vibration proof component. Acting on the joint 1, a slight slip occurs at a frequency f between the joint element side sliding surface 15a and the contact indenter side sliding surface 19a. With respect to this small slip, a damping effect is exhibited by friction by the damping means D1, and the small slip is suppressed. Further, when a slight slip occurs between the sliding surfaces 15a and 19a, the contact indenter 17 is displaced little by little in the axial direction. Along with this small displacement in the axial direction, friction occurs between the side surface 20 of the contact indenter 17 and the inner side surface 21 of the recess 16, and the damping effect by the damping means D2 is also exhibited. Further, with the slight displacement of the contact indenter 17 in the axial direction, air flows through the orifice t to generate a dynamic pressure resistance, and the damping effect by the other damping means D3 is exhibited. With the above three damping means (D1 to D3), the torque fluctuation component can be attenuated and absorbed, and the occurrence of torsional vibration in the vicinity of the resonance frequency f can be suppressed. In the vibration-proof joint 1, since the sliding surfaces 19 a are provided on both side surfaces of the contact indenter 17, the damping function can be effectively exhibited with respect to torque in both positive and negative directions.

  Further, when an excessive torque is generated due to a trouble of the device or the like, an excessive axial force is generated between the joint element side sliding surface 15a and the contact indenter side sliding surface 19a. The trapezoidal portion 19 is pushed closer to the second joint element 12 side than the flange surface 13a of the first joint element 11, and the first joint element 11 and the second joint element 12 are idled. Thereby, the torque limit function is exhibited and it is possible to prevent damage to the equipment (for example, damage to the torque measuring instrument when the torque measuring instrument is attached) due to excessive torque being generated.

  Finally, the case where the vibration-proof joint 1 is used in the rotation test apparatus for automobiles will be described as an example. In an automobile test apparatus, torque is transmitted from a motor to a specimen, and a torque measuring device is disposed between the motor and the specimen. When the spring constant of this torque measuring device is K, the moment of inertia of the motor is I1, and the moment of inertia of the specimen is I2, a torsional resonance system having the following resonance frequency f exists.

The number of test operations of the test apparatus for automobiles is in the range of 500 to 10000 rpm, and generally the value of K is about 10 ¹ to 10 ² Nm / rad and is very small. Therefore, accurate torque cannot be measured at the number of rotations at which resonance occurs. And at the rotation speed which a resonance generate | occur | produces, an abnormal noise generate | occur | produces and an accurate noise measurement cannot be performed. For this reason, attempts have been made to prevent this resonance by applying damping, or to design the resonance frequency to be outside the range of the operating rotational speed, but it is not sufficient, and is described in the conventional technology In the anti-vibration joints described in these two publications, there are problems as described in the problem to be solved by the invention, and an appropriate anti-vibration joint cannot be provided.

  However, according to the vibration proof joint 1, the steady component and the fluctuation component of the torque transmitted between the input shaft and the output shaft can be separately received. That is, the steady component of torque is transmitted between the first and second joint elements (11, 12) as the spring 18 is deformed along with the displacement of the contact indenter 17 to balance the axial force of the torque. Thereby, even a large torque can be easily transmitted by adjusting the number of contact indenters 17 and the spring constant of the spring 18, and the contact indenter is displaced in the axial direction. Is almost constant in all the rotation speed ranges. The torque fluctuation component that generates torsional vibration is also attenuated by the attenuating means D1 to D3 and can be easily absorbed regardless of the operating rotational speed. Therefore, when the vibration-proof joint 1 is used, a large torque can be transmitted and the generation of torsional vibrations can be suppressed over a wide range of rotational speeds in the automobile test apparatus. Thereby, even if it is the rotation speed which a resonance generate | occur | produces, generation | occurrence | production of a resonance can be suppressed and an exact torque can be measured.

  Further, in a test apparatus for automobiles, it is necessary to hang a weight by attaching an arm to the end of the joint when calibrating the torque meter. For example, a shaft joint described in Japanese Patent No. 3106310 is used. In this case, it is necessary to allow a very large rotation angle because of its structure when transmitting torque. However, if the allowable rotation angle during torque transmission is very large, this calibration operation cannot be performed. Therefore, in order to avoid this, there is a problem that the joint itself must be removed or a lock mechanism for preventing rotation must be newly provided.

  However, when the vibration-proof joint 1 is used, torque is transmitted through the contact of the sliding surfaces 15a and 19a inclined with respect to the displacement direction of the contact indenter 17, so that the sliding distance when the torque acts can be shortened. The relative rotation angle between the first joint element 11 and the second joint element 12 can be reduced. Therefore, troubles can be prevented from occurring when the torque meter is calibrated. Some torque measuring devices require electrical insulation with respect to the shaft, but the contact indenter 17 in the vibration-proof joint 1 is made of a nonconductive material such as polyacetal, MC nylon, ceramic, etc. It is possible to easily realize a vibration-proof joint having a proper insulation.

(Second Reference Embodiment)
2 to 4 show a vibration-proof joint 2 according to a second reference embodiment. Note that, in the following description, elements that perform the same functions as those in the first reference embodiment will be omitted as appropriate using the same names. 2 is a cross-sectional view in the axial direction of the vibration-proof joint 2 (a cross-sectional view taken along the line B-B in FIG. 3), and FIG. 3 is a front view of the vibration-proof joint 2. FIG. 4 is a perspective view of each component before assembling the vibration-proof joint 2. 2 and 3, the vibration-proof joint 2 includes a first joint element 22 connected to an input shaft or output shaft (not shown), and an input shaft or output shaft different from the shaft connected to the first joint element 22. And a second joint element 23 to be connected.

  First, the second joint element 23 includes a flange portion 24 connected to the input shaft or the output shaft, and a ring portion 26 that is fastened to the flange portion 24 by a bolt 25 and is formed in a cylindrical shape. Yes. And the 1st joint element 22 is the cylindrical part surrounding the circumference of the flange part 27 connected with an input shaft or an output shaft, the edge part 28 facing the ring part 26 of the 2nd joint element 23, and the ring part 26. The outer cylinder part 29 is formed and extended from the end part 28, and the ring-shaped cover part 30 is attached to the front end part of the outer cylinder part 29 by a bolt 31.

  Further, between the end portion 28 of the first joint element 22 and the ring portion 26 of the second joint element 23, a contact indenter 32 in contact with the end portion 28 and a spring 33 (spring 33) as an elastic member are interposed. It is disguised. And between the ring part 26 and the cover part 30 of the 1st coupling element 22, the contact indenter 34 which contact | connects the cover part 30, and the spring 35 (spring 35) which is an elastic member are interposed. That is, the ring portion 26 is formed with a concave portion 36 opened on the end portion 28 side and a concave portion 37 opened on the cover portion 30 side in the circumferential direction, and each concave portion 36 and the concave portion 37 are formed in the drilling direction. Are provided so as to be located on the same axis. A spring 33 is held in the recess 36 and a spring 35 is held in the recess 37 so as to be received.

  FIG. 4A shows a perspective view of the second joint element 23. In the ring portion 26, the contact indenter 32 protrudes from each concave portion 36 arranged in the circumferential direction. Is shown. As shown in this figure, the contact indenter 32 has a conical surface at the tip that contacts the end 28 of the first joint element 22. The contact indenter 34 is also formed in a conical surface shape. The conical surface portions of the contact indenters 32 and 34 constitute contact indenter side sliding surfaces 32a and 34a, respectively.

  FIG. 4B is a perspective view of the flange portion 27 and the outer cylinder portion 29 in the first joint element 22, and FIG. 4C is a perspective view of the cover portion 30 of the first joint element 22. As shown in FIGS. 2, 4 (b), and 4 (c), the end 28 of the first joint element 22 is provided with a conical recess 28 a arranged in the circumferential direction. Similarly, the cover 30 is also provided with a conical recess 30a disposed in the circumferential direction. These conical recesses 28a and 30a constitute joint element side sliding surfaces 28a and 30a, respectively.

  Thus, the sliding surfaces (28a, 30a, 32a, 34a) can be easily formed by making the contact indenter side sliding surfaces 32a, 34a and the joint element side sliding surfaces 28a, 30a conical. Further, the contact indenters (32, 34) can be easily formed, and mass production can be easily performed even when a large number of contact indenters (32, 34) are required. Further, since both the contact indenter side sliding surfaces (32a, 34a) and the joint element side sliding surfaces (28a, 30a) are formed in a conical shape, the contact state between the sliding surfaces can be easily kept constant. Therefore, it is possible to realize a structure in which radial direction eccentricity and inclination between input and output are easily allowed.

In FIG. 2, the vibration-proof joint 2 includes a plurality of rubber rings 38 that surround the ring portion 26 between the outer cylinder portion 29 of the first joint element 22 and the ring portion 26 of the twelfth joint element 23. Is arranged. By disposing the rubber ring 38, sliding friction can be generated on the rubber ring 38 due to the relative rotational displacement generated between the outer cylinder portion 29 and the ring portion 26. Thus, in addition to the damping means by sliding friction between the first joint element 22 and the contact indenters 32 and 34, other damping means D4 for damping the torque fluctuation component can be easily configured only by mounting the rubber ring 38. it can. In addition, a high damping effect can be exhibited by disposing the rubber ring 38 at a portion having a large diameter where a high relative speed can be obtained. Furthermore, the presence of the rubber ring can easily realize a structure that easily allows radial eccentricity and inclination between the input and output shafts.

  In the vibration-proof joint 2, as in the vibration-proof joint 1 in the first reference embodiment, the torque fluctuation component is attenuated by the friction between the joint element-side sliding surfaces 28a, 30a and the contact indenter-side sliding surfaces 32a, 34a. Attenuating means D1 and an attenuating means D2 for attenuating torque fluctuations by friction between the side surfaces of the contact indenters 32 and 34 and the inner wall surfaces of the concave portions 36 and 37 of the ring portion 26 are provided. Further, a clearance functioning as an orifice is provided between the side surfaces of the contact indenters 32 and 34 and the inner wall surfaces of the recesses 36 and 37 of the ring portion 26, and, like the vibration-proof joint 1, the dynamic pressure resistance when air flows is provided. Another damping means D3 that exhibits a damping function may be configured.

  The anti-vibration joint 2 described above has the same operational effects as the anti-vibration joint 1 of the first reference embodiment, and thus detailed description of the operation is omitted. The spring 33 provided on the side and the spring 35 provided on the cover portion 30 side cause reaction force due to the axial force of the torque to act on the ring portion 26 of the second joint element 23 in opposite directions. it can. For this reason, the reaction forces are canceled out, and the axial force of the torque can be prevented from acting on the outside. Further, by bringing the contact indenters 32 and 34 into contact with the end portion 28 side and the cover portion 30 side, respectively, more contact indenters can be brought into contact with the first joint element 22 and a larger torque can be obtained. Can be transmitted.

(Third reference embodiment)
FIG. 5 shows a vibration-proof joint 3 according to the third reference embodiment. In addition, in the following description, about the part which overlaps with 1st reference embodiment and 2nd reference embodiment, description is omitted by using the same name. FIG. 5 shows a schematic diagram of an axial cross section of the vibration-proof joint 3. This anti-vibration joint 3 corresponds to the anti-vibration joint 2 according to the second reference embodiment connected in series. That is, the vibration-proof joint 3 includes a first joint element 39 and a second joint element 40, and the second joint element 40 includes a connecting shaft 41 and a ring portion 42 connected in series by the connecting shaft 41, 43 and a flange portion 44 attached to the ring portion 43 are provided. The first joint element 39 is provided with a flange part 45, an outer cylinder part 46, a cover part 47, an outer cylinder part 48, and a cover part 49 in series.

  A contact indenter 50 and a spring 54 (elastic member, spring) are interposed between the flange portion 45 and the ring portion 42, and a spring 55 (elastic member) is interposed between the ring portion 42 and the cover portion 47. , A spring) and a contact indenter 51 are interposed, and a contact indenter 52 and a spring 56 (elastic member, spring) are interposed between the cover portion 47 and the ring portion 43, and the ring portion 43 and the cover portion 49. Between them, a spring 57 (elastic member, spring) and a contact indenter 53 are interposed. A rubber ring 58 is attached between the ring portions 42 and 44 and the outer cylinder portions 46 and 48.

  As described above, since the vibration-proof joint 3 has a configuration in which the vibration-proof joint 2 is coupled in two stages in series, it is possible to transmit a larger torque without applying an axial force of the torque to the outside. it can. Further, instead of transmitting a larger torque, the diameter of the joint can be reduced, and in this case, higher speed rotation is possible. By repeating this configuration in multiple stages, it is also possible to provide a vibration isolation joint having a configuration in which the vibration isolation joint 2 is connected in series in three or more stages.

(Embodiment of the present invention)
FIG. 6 shows a vibration-proof joint 4 according to an embodiment of the present invention. In the following description, the same name is used for an element that exhibits the same function as the first reference embodiment or the second reference embodiment, and the description is omitted as appropriate. FIG. 6 is a schematic diagram of an axial cross section of the vibration-proof joint 4. The vibration proof joint 4 includes a first joint element 59, a second joint element 60, and an intermediate ring 61 interposed between the first joint element 59 and the second joint element 60. In addition, the 1st joint element 59 and the 2nd joint element 60 are supported by the displacement of an axial direction being restrained similarly to the vibration proof joint 1, and being mutually rotatable.

  Between the first joint element 59 and the intermediate ring element 61, a contact indenter 62 that is slidably in contact with the intermediate ring element 61 is interposed between the contact indenter 62 and the first joint element 64. And a spring 64 (elastic member, spring). Further, a contact indenter 63 slidably contacting the intermediate ring element 61 and a contact indenter 63 and the second joint element 60 are interposed between the intermediate ring element 61 and the second joint element 60. A spring 65 (elastic member, spring) is provided. A plurality of these contact indenters (62, 63) and springs (64, 65) are arranged in the circumferential direction. The contact indenters 62 and 63 are provided in a positional relationship facing each other with the intermediate ring element 61 interposed therebetween.

  Further, the contact indenters 62 and 63 are formed with contact indenter side sliding surfaces 62 a and 63 a that are inclined with respect to the displacement direction of the contact indenters 62 and 63 at a portion in contact with the intermediate ring element 61. The ring element side sliding surfaces 61a and 61b are formed so as to be in sliding contact with the contact indenter side sliding surfaces 62a and 63a, respectively. The contact indenter side sliding surfaces 62a and 63a are formed as conical protrusions, and the ring element side sliding surfaces 61a and 61b are formed as conical depressions.

  The damping means for damping the torque fluctuation component includes damping means D1 due to friction between the contact indenter side sliding surfaces 62a and 63a and the ring element side sliding surfaces 61a and 61b, the side surfaces of the contact indenters 62 and 63, and the first joint. A damping means D2 by friction with the element 59 or the second joint element 60 is provided. These functions are the same as those of the attenuation means D1 and D2 in the first to third reference embodiments.

  In addition to the damping means D1 and D2, as the other damping means D5 for damping the torque fluctuation component, the intermediate ring element 61 slides relative to the first joint element 59 or the second joint element 60 in the rotational direction. A slidable contact portion that can be contacted is formed in the intermediate ring element 61 and the first joint element 59 or the second joint element 60. That is, the first joint element 59 is provided with a protruding shaft portion 66 at the shaft center portion, and the intermediate ring element 61 is formed with a cylindrical boss portion 67 at the center. The outer peripheral edge portion 66a formed around the end portion of the protruding shaft portion 66 and the outer peripheral edge portion 67a formed around the end portion of the boss portion 67 are provided so as to be in sliding contact with each other. The sliding contact portion is configured. Also, the inner peripheral edge 60a formed on the inner peripheral side of the second joint element 60 and the outer peripheral edge 67a of the boss 67 are provided in a positional relationship that allows sliding contact, and this constitutes the second sliding contact part. Yes. A torque fluctuation component is generated in the vibration-proof joint 4 during high-speed rotation, and a slight slip occurs between the contact indenters 62 and 63 and the intermediate ring element 61, whereby the intermediate ring element 61 and the first joint element 59 or When relative displacement in the rotational direction occurs between the second joint element 60 and the second joint element 60, the torque fluctuation component is attenuated by the sliding friction generated at the first and second sliding contact portions.

  A cylindrical elastic member 68 made of, for example, rubber is disposed around the protruding shaft portion 66. The protruding shaft portion 66 penetrates the boss portion 67 together with the cylindrical elastic member 68. By arranging the cylindrical elastic member 68 in this way, sliding friction can be generated with respect to the cylindrical elastic member 68 due to the relative rotational displacement generated between the protruding shaft portion 66 and the boss portion 67. Thereby, in addition to the damping means (D1, D2) due to sliding friction between the first and second joint elements (59, 60) or the intermediate ring element 61 and the contact indenter (62, 63), the torque fluctuation component is attenuated. The other damping means can be easily configured by attaching a cylindrical elastic member. In addition, the presence of the cylindrical elastic member can realize a structure that easily allows radial eccentricity and inclination between the input and output shafts.

  The anti-vibration joint 4 described above has the same operational effects as the anti-vibration joint 1 of the first reference embodiment, and thus detailed description of the operation is omitted. An intermediate ring element 61 is disposed between the element 59 and the second joint element 60, contact indenters 62 and 63 are brought into contact therewith, and springs 64 and 65 are provided on the first and second joint element sides, respectively. Thus, the spring constants (elastic constants) of the springs on the first and second joint elements can be set in a parallel coupled state. Thereby, the spring constant of each spring (63, 64) can be set low. In the anti-vibration joint 4 shown in FIG. 6, the springs are arranged in two rows, but the spring constant can be set lower as the number of rows is increased.

Fig.1 (a) shows the schematic diagram of the axial direction cross section of the vibration-proof coupling which concerns on 1st reference embodiment, FIG.1 (b) is the AA line arrow view of Fig.1 (a). The principal part cross section which illustrated a cross section partially is shown. It is an axial sectional view of the vibration-proof joint according to the second reference embodiment, and shows a sectional view taken along line BB in FIG. It is a front view of the vibration proof joint which concerns on 2nd reference embodiment. It is each component perspective view before assembling the vibration proof joint which concerns on 2nd reference embodiment. The schematic diagram of the axial direction cross section of the vibration-proof joint which concerns on 3rd reference embodiment is shown. The schematic diagram of the axial cross section of the vibration-proof joint which concerns on embodiment of this invention is shown.

Explanation of symbols

1, 2, 3, 4 Vibration-proof joint 11, 22, 39, 59 First joint element 12, 23, 40, 60 Second joint element 17, 32, 34, 50-53, 62, 63 Contact indenter 18, 33 , 35, 54 to 57, 64, 65 Elastic member D1, D2 Damping means

Claims (6)

A first joint element connected to the input shaft or the output shaft;
A second joint element coupled to an input shaft or an output shaft different from the shaft coupled to the first joint element, the axial displacement of the first joint element being constrained and rotatably supported A second joint element to be
A plurality of contact indenters interposed between the first joint element and the second joint element;
An elastic member interposed between the contact indenter and at least one of the joint elements and allowing axial displacement of the contact indenter, wherein the contact indenter is displaced in the axial direction by rotation of the joint element. A plurality of elastic members that transmit a torque of a substantially predetermined magnitude between the joint elements by balancing with the axial force of the torque transmitted at
A damping joint comprising damping means for attenuating torque fluctuation components by sliding friction acting between a contact indenter side sliding surface formed on the contact indenter and a surface facing the contact indenter side sliding surface; ,
An intermediate ring element is interposed between the first joint element and the second joint element,
The surface facing the contact indenter side sliding surface is a ring element side sliding surface formed on the intermediate ring element,
The contact indenter provided between the first joint element and the intermediate ring element so that the contact indenter side sliding surface is slidably in contact with the ring element side sliding surface of the intermediate ring element; The elastic member interposed between the contact indenter and the first joint element is disposed,
The contact indenter provided between the intermediate ring element and the second joint element so that the contact indenter side sliding surface is slidably in contact with the ring element side sliding surface of the intermediate ring element; An anti-vibration joint comprising the elastic member interposed between the contact indenter and the second joint element. The contact indenter side sliding surface is a surface inclined with respect to the displacement direction of the contact indenter,
The vibration-proof joint according to claim 1, wherein the ring-side sliding surface is slidable in contact with the contact indenter-side sliding surface.   The damping means attenuates a torque fluctuation component by friction between the side surface of the contact indenter and the first joint element or the second joint element in addition to friction between the contact indenter side sliding surface and the ring element side sliding surface. The vibration-proof joint according to claim 1 or 2, wherein   In addition to the attenuating means, as another attenuating means for attenuating the torque fluctuation component, a sliding contact portion that can be slidably contacted with the intermediate ring element relative to the first joint element or the second joint element in the rotational direction is provided. The anti-vibration joint according to any one of claims 1 to 3, wherein the intermediate ring element and the first joint element or the second joint element are formed. The first joint element is provided with a projecting shaft portion at the shaft center portion and a cylindrical elastic member surrounding the projecting shaft portion,
The intermediate ring element is formed with a cylindrical boss at the center,
The vibration-proof joint according to any one of claims 1 to 4, wherein the protruding shaft portion penetrates the boss portion together with the cylindrical elastic member.   The vibration-proof joint according to any one of claims 2 to 5, wherein the contact indenter side sliding surface and the ring element side sliding surface are formed in a conical surface shape.

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