JPS60231019A - Claw coupling - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a drive member at the end of a drive shaft, a driven member at the end of a driven shaft, at least six pawls on the drive member, and a drive member at the end of the drive shaft. axial displacement, angular axial displacement or axial displacement with the same number of pawls on the driven member and a movable torque transmission member between the driving pawls. Or they relate to interlocking joints that compensate for combined variations.

[Prior art]

Dog joints having a movable torque transmission member between the pawls are known. This torque transmitting member can be, for example, a drum-shaped rigid or compressively elastic member. Furthermore, dog-like joints (keyed flexible joints) with a sliding key and an elastic ring are known. The disadvantage of all these interlocking joints is that they have very limited variation compensation or that they are too expensive. Furthermore, the sliding friction that occurs between the torque transmitting member and the pawl has the disadvantage of leading to frictional losses and wear.

[Problem that the invention seeks to solve]

It is an object of the invention to be able to compensate for larger radial, angular and/or axial variations between the shafts with a movable torque transmitting member than is the case with known interlocking joints. The goal is to obtain an interlocking joint. Furthermore, the dog joint has a certain degree of rotational elasticity, so rotational vibrations and rotational moment shocks should be able to be damped by this rotational elasticity.

[Failure to solve the problem]

According to the present invention, in the above-mentioned interlocking joint, the space between the driving side pawls is reduced inwardly or outwardly in the radial direction, and the torque transmission member is elastically supported. The invention is solved in that the torque transmitting member is a spherical, drum-shaped or cylindrical member, and is supported by an elastic limit ring adjoining on the outside or on the inside thereof. A resiliently supported torque transmission member between the drive pawl and the drive pawl transmits circumferential force from the drive member pawl onto the driven member pawl. In this case, the drive member and the driven member are generally disc-shaped, and the pawls are arranged uniformly spaced around the periphery of the drive member and the driven member, so that the pawls are arranged staggered and the torque An intermediate space is formed for the transmission member. The torque transmitting member is a torque transmitting member that is present in front of the driving pawl in the direction of the rotational moment, especially when transmitting a circumferential force held in contact with the pawl by a force acting inwardly or outwardly. The members are subjected to compression which causes the torque transmitting members to escape radially outwardly or inwardly from the elastically reduced gap. The torque transmitting element located behind the drive pawl in the direction of the rotational moment is not subject to this compression. This torque transmission member can therefore be moved into a reduced space under the action of elasticity.

The annularly arranged torque transmission member without transmission of rotational moments moves radially inwardly and outwardly alternately under the action of the rotational moment. The design must be such that the radial force directed from the reduction section can be less than or equal to the elastic retention force. The joint according to the invention comprises:
It is possible to compensate for angular, radial, and axial variations in the shaft, or combinations thereof. Although this joint is a rigid torque transmission member, it exhibits significant rotational elasticity. This is because the torque transmitting member is elastically movable in the radial direction and the opposing movement of adjacent torque transmitting members is coupled to the relative rotation of the drive member and the driven member.

Correspondingly, rotational vibrations are also damped by this coupling.

According to a preferred embodiment of the invention, the intermediate space between the pawls is limited by a contoured pawl surface. in this case,
The pawl surfaces are generally flat, parallel surfaces to the joint axis that are inwardly or outwardly approached and contain the torque transmitting member between themselves. This torque transmission element is in particular a spherical, P-ram or cylindrical element.

If the torque transmitting member is axially convex or spherical, i.e. in the form of a ball or a P-ram body, then edge compression of the torque transmitting member and thus essentially wear factors are prevented.

According to a preferred embodiment of the invention, the torque transmitting element is supported by an elastic limit ring, which abuts the torque transmitting element on the outside or on the inside. In this case, one
Only two elastic restriction rings are required. The radial force exerted on the torque transmitting member by this restriction ring depends on the radial displacement position of the torque transmitting member. Since the torque transmitting member loaded when transmitting a rotational moment performs a radial movement similar to that of a dome, the radial force exerted on the torque transmitting member by the elastic restriction ring is equal to the rotational moment. essentially equal to that of a torque transmitting member which is relieved of load during transmission of . In this embodiment, the elastic ring adjoining the torque transmission member on the outside can be surrounded by a rigid limiting ring. The limit ring limits the deformation of the elastic limit ring so that the limit ring cannot be overloaded by outwardly offset torque transmitting members. Similarly, a rigid limiting element, for example a limiting cylindrical element, can be arranged in the elastic limiting ring which adjoins the torque transmitting element on the inside. This limiting cylindrical element also has the purpose of preventing overloading of the elastic limiting ring by means of an inwardly displaced torque transmitting element during the transmission of rotational torques. The elastic limit ring can be assisted by a ZAM elastic material, thereby increasing the damping in the case of rotational vibrations and rotational moment a strikes.

According to one preferred embodiment of the invention, a ball is used as the torque transmission member, and the claw surface in contact with the ball is
Each is tilted in alternating opposite axial directions. Due to the pawl being axially inclined in addition to being radially inclined, relatively large bending angles of the joint can be achieved.

Ball joint with cruciform ball track (Kugel-Gl)
As in the case of (eichlaufgelenk), mutual compensation of the axial forces acting on the ball during a moment impact can be achieved if there is an even number of torque transmitting members, so that during bending the torque transmitting members It is located on the bisector plane. This ball is axially guided, in particular by a rigid outer ring, which is actually a ball joint (Kugel-Gleich
laufgelenk) o Has the function of a retainer.

In a particular embodiment of the invention, each torque transmitting member consists of a cylindrical central member having an axial pin on its respective front face and a roll rotatably supported on the axial pin; The two surfaces of the pawl in contact with the torque transmitting member are each shaped such that the central member is only displaceable on one surface and the roll is displaceable only on the other surface. The configuration of this torque transmitting member formed as a double □ roll and the corresponding contour of the pawl surfaces allows the torque transmitting member to carry out rotary movements simultaneously on two surfaces, thus reducing friction and wear, e.g. This ensures that the number of transmission bodies is significantly reduced compared to cylindrical transmission bodies.

According to another embodiment, the torque transmission member is rotatably supported between two elastically deformable rings. In this case, the rings are axially adjacent to each other between the torque transmitting members, and the adjacent ring portions can have strut corners. As in the case of the limiting elements for inner or outer elastic limiting rings, this configuration of the ring limits the radial deformation of the ring so that it cannot be overloaded.

According to another embodiment of the invention, the torque transmission member is supported solely elastically on the rigid ring. When supported by a common elastic ring, the rotational elasticity of the joint is unavoidably equal in the two directions of rotation; when supported alone by alternately different spring stiffnesses, the rotational elasticity is equal in the two directions of rotation. Can be selected separately. A spiral spring or a leaf spring can be used as the reservoir for supporting the torque transmission member.

In all embodiments, it is possible to construct a joint for connecting the shaft and the hollow shaft, which is often required, for example, in the case of transmissions for railway vehicles. If the number of torque transmitting members is an even number greater than four, no difficulty arises in the joint being constrained by the torque transmitting members.

〔Example〕

Next, embodiments will be described in detail with reference to the drawings.

According to FIGS. 1 to 3, a disk-shaped moving member 3 is attached to a drive shaft 1.
is formed, and a disc-shaped wave member 4 is formed on the driven shaft 2. On the drive member 6, five wedge-shaped pawls 5 are arranged evenly, that is, with a central angle of 72° and spaced apart along the circumferential direction.

Five horizontal claws 6 are arranged on the disc-shaped wave member 4 in a similar arrangement. Claw surface 5a extending into a wedge shape of drive side mold 5
Ten cylindrical rolls 7 as torque transmitting members are arranged between the cylindrical rolls 7 and the wedge-shaped claw surface 6a of the driven mold 6, and an elastic limit ring 8 is disposed on the outside of the cylindrical rolls. be in contact with

The limiting ring 8 once holds the roll 7 under a radially inwardly directed force in resilient contact as the claw surfaces 5a and 6a. When transmitting the rotational moment from the pawl 5 onto the pawl 6, the pressure-loaded roll 7 is pressed outward against the elastic force of the ring 80, and the pressure-relieved roll 7
is further pressed inwardly between the claws 5 and 6 by the elastic force of the ring 8.

Apart from the small number of pawls, the embodiment according to FIGS. 4 to 6 also shows that the space between the driving mold 5 and the driven mold 6 is reduced radially outward, and the elastic This embodiment is distinguished from the embodiment according to FIGS. 1 to 6 in that the limiting ring 8 is in internal contact with the roll 7 as a torque transmitting member. In this case, the pressure-loaded roll 7 when transmitting the rotational moment is pressed inward against the radial force of the ring 8, and the pressure-relieved roll is forced against the radial force of the ring 8. You can swerve outward.

In the case of the embodiment according to FIG. 7, the driving side mold 5 and the driven side mold 6
do not extend wedge-shaped as in the embodiment according to FIG. 2, but the claw surfaces 5a and 6a on both sides of each claw run parallel to each other. Nevertheless, the space between the driving side mold 5 and the driven side mold 6 is formed by a claw surface 5 extending inwardly in a wedge shape.
a to 6a, so that they function essentially in the same way as in the embodiments according to FIGS. 1 to 6. The elastic limit ring 8 is surrounded by a fixed outer ring 9, which limits the deformation of the ring 8 and prevents its overloading.

The embodiment according to FIG. 8 is essentially similar to the embodiment according to FIG. 5, except that there are fewer pawls. However, a cylindrical restriction member 9a is arranged in the elastic restriction ring 8 at a distance from the restriction ring, and this cylindrical restriction member prevents the elastic restriction ring 8 from being significantly inwardly deformed. to prevent

In the embodiment according to FIGS. 9 to 12, the drive member and the driven member each have four pawls, the side faces 5 or 6a of which are not only radially inclined; , is also axially inclined. In particular, as can be seen from FIGS. 10 and 12, the two side faces 5a and 6a of the pawl 5 and 6a are axially inclined toward each other in opposite directions, and this angle of inclination is, in the illustrated embodiment, It is 10°. The inclination in the axial direction is such that when the joint transmits a rotational moment and an impact occurs, an axial force acts on the ball 7 as a torque transmitting member, and this axial force causes the claw surfaces 5a and 6a to alternately move. are slanted in opposite directions, resulting in their being equal in opposite directions. Since the axial forces cancel each other out if there is an even number of balls 7, the outer ring 11, which guides the balls 7 axially, lies on a trisecting plane when bending the joint. In order to guide the Dalere axially, the rigid outer ring 11 has a U-shaped profile in axial section, the center point of the ball 7 being located within the U-shaped profile. In this embodiment, a soft rubber ring 1 is provided between the elastic limit ring 8 and the outer ring 11.
0 is inserted. In this way, the damping of rotational vibrations and torque shocks in the joint is enhanced.

The embodiment according to FIGS. 16-16 essentially consists of pawls 5 and 6.
The intermediate space between the transmission balls 7 and the elastic limit ring 8 is radially outwardly contracted and the elastic limit ring 8 is connected to the transmission ball 7 as a torque transmission member.
It is distinguished from the embodiment according to FIGS. 10 to 12 only by the internal contact with . Similar to the embodiment according to FIGS. 9 to 12, the pawl surfaces 5a and 6a are inclined in axially opposite directions to each other, and the balls 7 are mounted on a rigid inner ring 11 having a U-shaped profile in axial cross section. are guided by.

A soft rubber ring 10 is likewise provided between the inner ring 11 and the limit ring 8 in order to enhance the damping. The functional type of this joint is essentially the same as that of FIGS. 9-12.

FIG. 17 shows a double roll used as the torque transmission member 7. This double roll consists of a cylindrical central member 7a and a front axle bin 7b. A roll 7d is rotatably supported on the shaft pin Zb by a needle bearing 7C. The cylindrical center member 7a and the cylindrical ring-shaped roll 7d have the same diameter. The claw surface 5a of the driving layer 5 has a protruding center portion, and the center portion is recessed on the claw surface 6a of the driven die 6. Double roll roll 7 with claw surfaces 5a and 6a
The edges corresponding to d are opposite to this: the claw face 5a of the drive multiplier 5 is concave on both edges, and in the case of the claw face 6a the edges are protruding. Therefore, the central member 7a of the double roll can roll on the protruding center of the claw surface 5a, and the roll 7d can simultaneously roll on the concave edge of the driven claw surface 6a. . In this way, the transmission body has a pure rolling movement on both sides, and the increased friction and wear that occurs during sliding movements is avoided.

The embodiment shown in FIG. 18 is distinguished from the embodiment according to FIG. 5 by the resiliently supported form of the roll 7, except for the reduced number of pawls. By the way, instead of the elastic limit ring 8 that contacts the torque transmitting member 7 internally, in this embodiment, elastically deformable rings 8a are provided on all sides of the double roll 7. Double roll 7 is rotatably supported on shaft 12 between rings 8a, as shown in detail in FIG. 19th
In the embodiment shown, the two elastic rings 8a have sections 8b adjacent to each other between the rolls 7.

A stopper 16 is attached to the adjacent portion 8b,
This stone ξ- should engage the pawl and limit the radial deformation of the ring 8a.

FIGS. 20 and 21 show a further embodiment of elastic support for the torque transmission element 7, which in this case is designed as a ball. A radially acting spiral spring 17 is supported on the substrate 15 between two parallel rigid support rings 14 which are connected to the spacer by threaded bolts 16, and the ball 7 is in contact with the inside of the spiral spring. ing. By supporting the torque transmitting member alone, a method of selecting alternately different elasticities is elucidated, thereby obtaining a joint with different rotational characteristics in the two rotational directions. The embodiment according to FIG. 22 essentially provides a 20th
This is distinguished from the embodiment according to FIGS. Moreover, this independent support provides a method for variously adjusting the elasticity acting on the sail 7. For this purpose, the leaf springs 18, which act on two adjacent sails 7, are pivotably supported on an axle pin 19 so as to converge. By pivoting the leaf spring 18 on the pin 19, the compressive force on the seal 7 can be varied depending on one another. Furthermore, the webs 14a of the support ring 14 can be configured in such a way that the dale can be guided radially displaceably between the webs.

[Brief explanation of the drawing]

FIG. 1 is a side view showing a first embodiment of the interlocking joint according to the present invention, FIG. 2 is an enlarged cross-sectional view showing the joint according to FIG. 1, and FIG. 6 is taken along line m--i in FIG. FIG. 4 is a side view showing a second embodiment of the interlocking joint according to the present invention, FIG. 5 is an enlarged cross-sectional view showing the joint according to FIG. 4, and FIG. FIG. 7 is a cross-sectional view showing a sixth embodiment of the interlocking joint according to the present invention, and FIG. 8 is a cross-sectional view showing a fourth embodiment of the interlocking joint according to the present invention. 9 is a side view showing a fifth embodiment of the interlocking joint according to the present invention, FIG. 10 is an enlarged cross sectional view showing the joint according to FIG. 9, and FIG. 11 is taken along the line of FIG. 12 is a partial side view showing the joint according to FIG. 10; FIG. 16 is a side view showing a sixth embodiment of the interlocking joint according to the present invention; FIG. 14 is an enlarged cross-sectional view showing the joint according to FIG. 16,
15 is a longitudinal sectional view showing a cross section taken along the line xv-xv in FIG. 14, FIG. 16 is a partial side view showing the joint according to FIG. 14, and FIG. 17 is a shaft showing one embodiment of the transmission body. 18 is a schematic view showing a seventh embodiment of the interlocking joint according to the invention; FIG. 19 is a partial vertical sectional view showing an embodiment of the joint different from FIG. 18; 20 is a partial plan view showing a support ring in the case of an eighth embodiment of a coupling according to the invention with a single support member for the transmission body; FIG. 21 is a longitudinal section taken along the line XM--X in FIG. FIG. 22 is a plan view of a ninth embodiment of the joint according to the invention, with the support ring partially removed. 5... Drive number, 5a, 6a... claw surface, 6... driven side type, 7... torque transmission member, 7a... center member, 7b... shaft pi/, 7C.・・Needle bearing, 7d・
...Roll, 8...Restriction ring, 8a...Elastically deformable ring, 8b...Adjacent ring portion, 9...
- Rigidity limiting ring, 9a... Rigidity limiting member, 11...
- Ring, 16... Stopper, 14... Rigid ring, 17... Spiral spring, 18... Leaf spring.

Claims (1)

[Scope of Claims] 1) A driving member at the end of the driving shaft, a driven member at the end of the driven shaft, at least six pawls on the driving member, and the same number of pawls on the driven member as pawls on the driving member. and a meshing mechanism having a movable torque transmitting member between the drive layer and the driven die, which compensates for axial movement in the raw direction, angular direction, axial movement, or a combination thereof. In the joint,
The space between the driving die and the driven die (6) is reduced inwardly and outwardly in the radial direction, and the torque transmitting member is elastically supported, and the torque transmitting member is spherical or drum-shaped. or a cylindrical member with an elastic restriction ring (
8) An interlocking joint characterized by being supported by. 2) A joint according to claim 1, wherein the torque transmitting member is held in contact with the pawls (5, 6) by a force directed into the constriction. 6) The joint according to claim 1 or 2, wherein the intermediate space is defined by the claw surfaces (5a, 6a) running in a wedge shape. 4) Attach the shaft pin (7) on the front surface of each torque transmitting member.
b) with a cylindrical central member (7a) and an axial pin (7b)
) consisting of a roll (7d) rotatably supported on
The side surface of one claw (5) in contact with the torque transmission member (7) (
5a) is raised at the center, and the side surface (6a) in contact with the torque transmission member of the other claw (6) is raised at both edges. The joint according to any one of the above. 5) A ball is used as the torque transmitting member, and the claw surfaces (5a, 6a) in contact with the sail are each inclined alternately in opposite axial directions.
The joint described in any one of the preceding paragraphs. 6) Joint according to claim 5, in which the sail is axially guided by a rigid profiled ring (11). 7) The joint according to claim 1, wherein the outer limiting ring 0 is surrounded by a rigid limiting ring (2). 8) Restriction ring that contacts on the inside (rigidity restriction member (9) in D)
A joint according to claim 1, in which a) is arranged. 9) The torque transmission member consists of two elastically deformable rings (
A joint according to any one of claims 1 to 6, which is rotatably supported between 8a). 10) Joint according to claim 9, in which the rings (8a) are axially adjacent to each other between the torque transmitting members, and the adjacent ring parts (8b) have stops (16). 11) A joint according to any one of claims 1 to 6, in which the torque transmission member is supported solely elastically on a rigid ring (14). 12) Claim 11, wherein the torque transmission member is supported by a spiral spring (17) or a leaf spring (18).
Fittings listed in section.