JPH0151686B2 - - Google Patents

Description

Detailed Description of the Invention [Industrial Field of Application] The present invention relates to a meshing shaft joint for transmitting torque between two shafts, which includes a driving part and a driven part having the same number of pawls on the driving side and the driven side. a driving part, the two pawls interlock with each other at a distance between their sides, and a movable transmission member is used between the driving pawl and the driven pawl. Regarding.

[Prior Art] A dog shaft joint using a movable transmission member between pawls is already known. In this case, the transmission element is a rigid or compression-elastic element. Dog couplings with sliding keys and elastic rings are also known. A drawback of these dog-shaft joints is that compensation for shaft displacement is limited. Sliding friction between the transmission member and the pawl leads to friction losses and wear. Vibration damping and power density are also low.

In German Patent Application No. 3313277.1-12 a rotationally elastic shaft coupling for compensation of radial, axial and angular displacements is proposed. In the case of this shaft joint, a cylinder hole and a piston that is movable within the cylinder hole are provided in the protrusion of the shaft joint body. The cylinder bores of all the pistons, which each produce a force transmission in one direction, are connected to one another and are filled with fluid for pressure compensation purposes.

[Problems to be Solved by the Invention] An object of the present invention is to provide a meshing shaft joint for transmitting torque between two shafts, which can compensate for any displacement in the radial direction, axial direction, or angle of the shafts. It is in. In this case, radial, axial, and angular vibrations are also damped. Also,
Sliding friction losses and the resulting wear are reduced or largely avoided.

[Means for Solving the Problems] The present invention has solved such problems in the following manner in the dog shaft joint of the type described at the beginning. That is, the chamber formed between the sides of both pawls is narrowed in the radial direction, and each transmission member
On the side opposite the narrow side of the chamber, all supporting members of the transmission member which are supported in each case by a radially movable support member and which produce a transmission effect in the same direction of rotation are each connected to one fluid system. Therefore, they are connected.

[Operation and Effect] The transmission member, which is located between the drive-side pawl and the driven-side pawl and is supported by the support member, transfers the circumferential force from the drive-side pawl to the driven-side pawl. introduce. The driving and driven parts are generally disc-shaped and the pawls are evenly distributed along the outer periphery of the driving and driven parts, so that the pawls can be engaged with each other. At the same time, an intermediate chamber for the transmission member is formed. The transmission member is
It is radially supported and maintained in contact with the pawl by a hydraulically loaded support member. With the transmission of the circumferential force, the transmission member located next to the drive-side pawl in the direction of the torque is loaded, and as a result, this transmission member attempts to displace out of the intermediate chamber of the wedge-shaped pawl and displaces its assigned part. Press the support member. Since the supporting members are all connected by a fluid system, there is a pressure compensation between these supporting members, which makes the torque transmission independent of any displacement of the shaft and its magnitude. It will be done equally on all nails. Suitable fluids include liquids, gases, and flowable solid substances. Due to its sufficiently high fluid compressibility, the shaft coupling can also be adjusted in rotational elasticity, for example if gases or bubble-containing liquids are used.

[Embodiment] According to an advantageous embodiment of the dog shaft joint of the invention, the driving part or the driven part is provided with a housing, which housings are connected to each other and are open on the circumferential side and are filled with fluid. and a support member disposed within the opening of the passageway. In one embodiment, the intermediate pawl chamber is narrowed radially outwards, and the housing is arranged centrally in the shaft coupling. This housing is preferably of cylindrical design and arranged concentrically with respect to the pawl, but radially spaced apart. The fluid enclosed in the passage closed by the support members of each fluid system ensures uniform pressure loading of all support members of the fluid system, so that each support member experiences an equal radial force. effect on the transmission member. Indeed, a radial or angular displacement displaces the transmission body, and thus its support member, and correspondingly forces the fluid into other channels of the fluid system. However, all the support members remain in contact with the transmission member despite any displacement of the shaft. Damping of rotational vibrations and torque impulses is obtained when compressible fluids are used, where the damping characteristics are related to the fluid system passageway arrangement and the compressibility of the fluid. By selecting different fluids for both fluid systems, it is possible to set different damping characteristics depending on the direction of rotation. The individual passages of each fluid system may be connected in a star configuration, thereby providing an adjustable restriction at the confluence of the passages. This adjustable throttle allows an additional influence on the damping effect.

According to another embodiment of the inventive dog-shaft joint, the pawl intermediate chamber is narrowed radially towards the shaft joint axis, and the housing is arranged in a ring-shape along the outer circumference of the drive or driven part. It is located. This embodiment has a radially larger structure than the embodiment with a central housing. The free interior space thus obtained is advantageous for certain applications.

According to one embodiment, the support member is designed as a piston that can be moved in the passage. In this case, it is advantageous for the passage to be a straight cylinder bore,
The piston is sealed and fitted into this cylinder hole. According to a further embodiment, the support element is designed as a diaphragm that closes off the passage. Also,
A closure piece, for example a rubber metal molding, can also be used as a support member.

According to a preferred embodiment, the transmission element is designed as a roller, a spherical roller or a ball. Transmission elements in the form of spherical rollers are effectively used when large angular displacements need to be compensated.

According to one embodiment, the transmission member consists of a cylindrical intermediate part with an axial pin on each end face and a roller rotatably mounted on each pin, In this case, the side surface of one of the pawls that contacts the transmission member is raised in the middle region, and the side surface of the other pawl is raised in both line regions. When this double roller is used as a transmission member, sliding friction between the pawl and the transmission member is completely avoided. This is because the cylindrical intermediate part rolls in the central region of the side surface of one pawl, and the two rollers roll in the edge region of the side surface of the other pawl.

According to another embodiment, balls are used as transmission members, the sides of each pawl contacting the balls being inclined in alternating opposite axial directions. In this way, since the side surfaces of the pawls are sloped in the axial direction in addition to the slope in the radial direction, a relatively large bending angle of the shaft joint can be tolerated. As in the case of constant velocity ball joints with cross-shaped ball races, an even number of transmission members allows them to mutually compensate for the axial forces exerted by the balls during torque transmission. , so the sphere lies in the bisector plane of the joint during bending. The ball can be guided in the axial direction in this case by means of a rigid molded ring. This molded ring effectively functions as a cage for the constant velocity ball joint.

When the number of transmission members is an even number greater than four, the dog shaft joint of the present invention does not suffer from imbalances such as those caused by the transmission members. If constructed accordingly, the inventive dog shaft joint is also suitable for coupling axles and hollow shafts, as is often necessary in railway vehicle drives.

[Example] The embodiment of the interlocking shaft joint shown in Fig. 1 has three pawls 1 on the driving side and three pawls 2 on the driven side, and these pawls 1 and 2 mesh in the axial direction. It's on. The sides 1a and 2a of the claws 1 and 2 are
A radially outwardly wedge-shaped intermediate chamber 3 is formed in which the transmission elements 4, 4' are arranged. Inside the shaft joint, a cylindrical housing 5 is provided concentrically with respect to the pawls 1 and 2 on the drive disk side.
Six radial cylinder holes 5a, 5b are formed in this housing 5 in correspondence with the transmission members 4, 4', and a piston 6 is slidably guided in these cylinder holes 5a, 5b. . These pistons 6 are in contact with the transmission members 4, 4' on the outside and support them in the radial direction.
In this case, the three cylinder holes 5a, which support the three transmission members 4 by means of the cylinder holes 5a, i.e. the pistons 6, open in a star shape to the first pressure compensation system, and the cylinder holes 5b, i.e. the pistons 6 by 3
The three cylinder bores 5a carrying the two transmission members 4' open in a star-shaped manner into the second pressure compensation system.
The cylinder hole 5a has a separate flow path from the cylinder hole 5b, and in this case, the merging points of the cylinder holes 5a and 5b, which merge into each other in a star shape, are shifted in position in the axial direction of the shaft joint. The first and second pressure compensation systems may have the same fluid medium or different fluid media. Both media may differ in viscosity and/or compressibility. Radial as well as angular vibrations can be damped by selecting the viscosity of the medium or by adjusting a throttle (not shown) arranged at the merging point. When using liquid or gaseous fluids,
Due to its compressibility, this fluid exerts a damping effect on rotational vibrations as well as torque impacts. By using fluids with different viscosities in both pressure compensation systems and by arranging the connection holes differently, it is possible to provide mutually different damping characteristics in both rotational directions.

The embodiment shown in FIG. 2 has three claws 1 on the driving side and three claws 2 on the driven side, like the embodiment in FIG.
A cylindrical transmission member 4, 4' is arranged in an intermediate chamber 3 between the two. In this embodiment, a cylindrical housing 5 is provided concentrically with the pawls 1 and 2 on the shaft coupling (not shown) on the driven side. Inside this housing 5, there are 3 parts that merge in a star shape in the radial direction.
Three holes 5a are formed, and these three holes 5a are formed.
A is filled with fluid, and an opening on the circumferential surface of the housing is closed by a diaphragm 7. The diaphragm 7 supports cylindrical transmission members 4, which are loaded when circumferential forces are transmitted in one direction of rotation. The housing 5 further includes three radial holes 5b which are axially displaced from the housing 5a and circumferentially offset by an angle of 60°.
A fluid system consisting of This fluid system is separated from the fluid system consisting of the holes 5a by a flow path, and is only shown schematically by broken lines in the figure. The diaphragm 7, which is under pressure from the fluid in the hole 5b, supports a transmission member 4' which transmits the circumferential force from the driving pawl to the driven pawl. The embodiment of FIG. 2 operates substantially like the embodiment of FIG. 1, with the radial displacement of the transmission members 4, 4' being limited by the maximum deflection of the diaphragm.

In the above embodiment, the cylindrical transmission member 4,
4' is in line contact with the side surfaces 1a, 2a of the pawl.
If as a result of mutual displacement of the shafts the transmission members 4, 4'
When dislocation occurs between the claws 1 and 2, sliding friction loss also occurs. This sliding friction loss becomes larger as the displacement to be compensated becomes larger. Such sliding friction can be completely avoided if double rollers are used instead of simple cylindrical rollers as the transmission member.

An embodiment of such a double roller is shown in FIG. This double roller consists of a cylindrical intermediate portion 4b having pins 4a on both end faces, and two rollers 4c rotatably supported on the pins 4a via needle bearings 8. Cylindrical middle part 4
b and the cylindrical ring-shaped roller 4c have the same diameter. The side surface of the driving-side pawl 1 has a slightly raised central area 1b, while the central area of the side surface of the driven-side pawl 2 has a slightly raised central area. I am doing it. Roller 4
The edge area 1c of the side surface of the pawl 1 corresponding to c is slightly rounded, and the edge area 2b of the side surface of the pawl 2
is slightly elevated. In this way, the cylindrical middle part 4b of the double roller rolls over the central area 1b of the driving pawl 1, and the two rollers 4c roll over the edge area 2b of the driven pawl 2. .

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view showing the first embodiment of the dog-shaft joint of the present invention, FIG. 2 is a cross-sectional view showing the second embodiment, and FIG. 3 is a longitudinal cross-sectional view of the embodiment of the transmission member. be. 1... Drive side claw, 1a... Side surface, 1b... Raised central range, 1c... Edge range, 2... Driven side claw, 2a... Side surface, 2b... Raised edge range,
3... intermediate chamber, 4... transmission member, 4'... transmission member, 4
a... Pin, 4b... Cylindrical middle part, 4c... Roller, 5... Housing, 5a... Passage, 5b... Passage,
6... Piston, 7... Diaphragm, 8... Needle bearing.

Claims (1)

[Scope of Claims] 1. A meshing shaft joint for transmitting torque between two shafts, which is composed of a driving part and a driven part having the same number of pawls on the driving side and the driven side. are in engagement with each other at intervals between their side surfaces, and in a type in which a movable transmission member is used between the driving side pawl and the driven side pawl, the side surfaces 1 of both pawls 1 and 2
A chamber 3 formed between a and 2a is narrowed in the radial direction, and each transmission member 4, 4' has a radially movable chamber 3 on the side opposite to the narrow side of the chamber 3.
The transmission member 4; 4' is supported by two support members 6 and 7 and produces a transmission action in the same rotational direction.
A dog-shaped shaft joint, characterized in that all supporting members 6, 7 of are each connected by a fluid system. 2. The driving or driven part is provided with a housing 5, which accommodates two separate flow channels each consisting of a plurality of fluid-filled passages 5a, 5b connected to each other and open on the circumferential side. 2. A dog-shaft joint according to claim 1, wherein the support members 6, 7 are arranged in the openings of the passages 5a, 5b. 3. A dog coupling according to claim 2, wherein the pawl intermediate chamber 3 is narrowed radially outwardly and the housing 5 is centrally arranged within the coupling. 4. The meshing shaft joint according to claim 3, wherein the passages 5a and 5b of each fluid system are connected in a star shape, and an adjustable crest is provided at the confluence point. 5. The pawl intermediate chamber 3 narrows in the radial direction toward the shaft coupling axis, and the housing 5 is arranged in a ring shape along the outer periphery of the driving or driven part. The meshing shaft coupling described in . 6. A dog joint according to claim 1, wherein the support member is constructed as a piston 6 that is movable in the passages 5a, 5b. 7. A meshing shaft joint according to any one of claims 1 to 5, wherein the support member is configured as a diaphragm 7 that closes the passages 5a, 5b. 8. A meshing shaft joint according to any one of claims 1 to 7, wherein the transmission members 4, 4' are configured as rollers, spherical rollers, or balls. 9. The transmission members 4, 4' consist of a cylindrical intermediate portion 4b having one axial pin 4a on each end face, and one roller 4c rotatably supported on each pin 4a. , the side surface of one pawl 1 that contacts the transmission members 4, 4' has an intermediate region 1b raised, and the side surface of the other pawl 2 has both line portion ranges raised. The dog-shaft joint described in item 8. 10. Claims 1 to 9, in which a number of balls are used as transmission members 4, 4', the sides of each pawl contacting these balls being inclined in alternating opposite axial directions. The meshing shaft joint described in any one of the preceding paragraphs.