KR19980701783A - Release bearings for hydraulic controls with separate clutches - Google Patents

Abstract

The present invention relates in particular to a release bearing comprising an operating device (1) for disengagement of a separate clutch that is mechanically or hydraulically actuated on a vehicle, which in particular consists of a single housing, in which a ring flange (5) is mounted. It has a holding rib (2) is perturbed in the axial direction, the release bearing (3) is directly supported and has a rotating fixed outer ring (6) and a rotating inner ring (10) between the roller body (9) The outer ring 6 is in contact with the angle disk 8 fixed to the ring flange 5 with a suitable load by the projection 7.

According to the invention, the angle disk 8 holds a portion of the ring flange 5 and has a radial outer edge 14 with the u-shaped member radially inward, wherein the inside of the free end is one frame 13. It is formed to hold the inner end of the projection (7) is supported by the cup spring (12).

Description

Release bearings for hydraulic controls with separate clutches

Detailed description of the invention

The present invention relates, in particular, to a release bearing including an operating device for releasing a separation clutch that can be installed hydraulically or mechanically, in a vehicle, in particular consisting of a single housing, in which the actuating ribs have a radial outer side. It is installed to be able to move in the axial direction with the ring flange toward the side, and serves to support the release bearing to the side toward the separating clutch. The release bearing has one rotating fixed outer ring and one rotating inner ring between them. The roller body is installed on the outer ring, and the outer ring is in contact with the ring flange by the cup spring on the opposite side of the radially adjusted projection, while the inner ring is in direct contact with the separating clutch indirectly with respect to the radially located part.

One type of release bearing is available from DE-A 43 27 879. It has a cover to reinforce the operating sleeve made of synthetic resin. At this time, except for the outer ring contact surface of the release bearing, the inner steel plate coated with synthetic resin serves as a reinforcing plate. At this time, the angle disk used is made of a plurality of uneven parts to form a mold-fixed combination with the synthetic resin, the manufacturing cost of the angle disk increases. The known operating ribs require an angle disk to be fixed during the application of the resin to the copper ribs, and at the same time, adversely affect the manufacturing cost.

One release bearing is known from DE-U 93 13 557, whereby the actuating ribs are connected with a part that represents a separate contact surface, on which the release bearing is supported. As a fixing device for the outer ring of the release bearing, a bent cup spring is provided between the operating rib and the inner ring.

The task for developing one release bearing in an alternative shape by the release bearing disclosed in the prior art is the basis of the invention. In other words;

a)-enables reduction of assembly tolerances

-Easy assembly

-Economical production is possible.

Other objects of the invention include the following.

b) to improve the service life or service life of the clutch release bearing.

The task presented in paragraph a) is solved by the features indicated in the indications of paragraphs 1 and 7 of the claims. The solution of the problem under paragraph b) is solved by the features of the marking part of claim 9.

The present invention according to claim 1 allows for an angle disc subjected to external shock buffing in the radial direction, so that the ring flange of the operating sleeve is fixed to the ring flange as an angle disc as part of the noise. This configuration allows for simple and economical assembly. The design of the angle disc is considered such that it covers the entire mounting range of the frame combined with the outer ring of the release bearing at the ring flange. The angle disc seated on the ring flange also has a radially inner cross section with a nearly U-shaped cross section, which has a free contact surface in the shape of a ring flange, which holds the inner end of the outer ring in the assembled state and supports the other cup springs. It will play a role. The shape of the angle disc according to the invention simplifies assembly by enabling the arrangement of the advantageous components of the components joined together by the load of the cup springs. According to the invention, the release bearings are supported on ring flanges of the operating ribs made of synthetic resin by projections of the outer ring away from steel plates, especially angle discs produced by non-cutting. Compared to the contact surface of the angle disk in the projection of the outer ring, the larger contact surface of the angle disk in the ring flange generates an advantageous load distribution, that is, a smaller surface pressure in the ring flange, which is advantageous for the external strength. Affects the associated operation thread. Compared with the prior art, the concept according to the invention also means the reduction of parts under the premise of the angle disc, which also serves as a support for the cup spring. This results in a reduction in assembly tolerances at the same time, which favorably develops the function and life of the release bearing.

In the idea of the invention according to claim 2, the ring joint surface is formed on the angle disk after the combination of the component, the angle disk, the outer ring and the cup spring, which includes the projection of the cup spring and the outer ring. While forming a ring flange on an angle disk attempted by non-cutting, in particular by attachment of a flange, a predetermined load of the cup spring is generated at the same time, which is in contact with the projection of the outer ring.

According to claim 3, the magnitude of the axial distance from the free contact surface to the angle disc is greater than the sum of the projections of the outer ring of cup spring thickness. In addition to this shape, a predetermined load on the cup spring required for the function is made by molding along the contact surface.

According to claim 4, in another advantageous form of the invention the cup spring is centered on the ring shoulder book (shoulder) of the angle disc. As in this example, the contact is centered by the surrounding projection so that the same distance along the radial direction of the cup spring is supported on the shoulder of the outer ring.

It is preferable to fix the angle disc to the ring flange according to claim 5. It is also a good idea to attach flanges that hold over or partially outside the ring flange. At the same time, a fixed angle disk of the ring flange may be considered, in which case, for example, fixing outside the ring flange is considered. Apart from the formation of shape-based fixation, this also prevents warping at the same time.

In order to facilitate assembly, the release bearing according to claim 6 is formed in a completely provided unit including a cup spring and an angle disc. This measure is advantageous in terms of cost as well as the cycle time of the release bearing integrated type.

In the invention according to claim 7, the cup spring design assumes the following dimension ranges:

a)

b)

ΔR is the relation: That is, it is made by the cup spring difference dimension.

S = wall thickness of the cup spring

h _O = inner height of the cup spring

An advantageous method under such dimensional range maintenance is that a characteristic curve is generated which generates the required spring stroke f for the cup spring loaded with the spring load F in the range of Fmin and Fmax. The cup springs designed according to this invention thus become cup springs which maintain assembly tolerances optimally. According to each need, the cup spring can be selected by coupling to the dimensional range according to the two inventions in order to reach a spring stroke of the required size.

In the assembled state, the outer diameter corresponds to the pitch diameter of the roller body, that is, the outer diameter coincides with the center of the roller body. This cup spring form takes full advantage of the existing structural space.

According to the invention according to claim 9, the structural distribution of the roller bearing ring to the roller body is considered, resulting in a contact surface of ≧ 106. The contact, also expressed as the radius of rotation ratio, defines the ratio of curvature between the outer ring and the roller body or between the inner ring and the roller body. Contact has a significant impact on the performance of the roller bearings, in particular with respect to the static load capacity, lubrication film formation and friction and wear.

The roller shape of the release bearing according to the invention also requires a pressure angle of ≧ 45 °. The angle, also called the pressure angle contact angle, occurs radially between the roller track and the connecting line passing through the contacts of the roller track and the roller bearing. According to the invention a pressure angle of ≧ 45 ° is used which is suitable for the deformation of the resulting roller bearing under constant load. The angular values correspond to the actual contact angles that follow. The measures according to the two inventions, the pressure angle and the contact, have a positive effect on the life of the release bearing.

In an advantageous form of the invention different values of contact between the outer ring and the roller body and between the inner ring and the roller body are taken into account. Accordingly, in order to achieve a uniform loading load, the wear- and friction values at the contact surfaces for different arrangements of configurations and the biased diameter ratios between each other are taken into account.

According to claim 10, the contact between the inner ring and the roll body is suitably enumerated at 106 to 112%. A slightly different arrangement is also possible with an arrangement of 110 to 120% contact between the outer ring and the roller body of the release bearing according to the invention according to claim 11.

Compared to the known prior art, this enlarged contact portion improves the friction in the roller contact, ie the contact area between the bearing inner ring or the outer ring of the bearing and the roller body, thereby advantageously reducing heat generation. At the same time the contact point according to the invention led to lubrication in an advantageous direction. In order to support measures for improving the life of such a release bearing, the contact is selected so that the contact between the outer ring and the roller body is smaller than the contact between the inner ring and the roller body.

According to claim 12, it is preferable to extend the inner ring in the cup spring direction while maintaining a small gap between the front face of the inner ring and the cup spring in order to reduce dust inflow into the roller bearing.

The structural forms claimed in claims 13 and 14 relate to measures which have a positive effect on the life of the roller bearings by simultaneously reducing the ingress of harmful dust or contaminants into the roller bearing tracks.

The inner ring that is rotating in accordance with claim 13 becomes a block inwardly in the radial direction from the end side such that dirt reaching the inner ring cannot be transported further due to the sea block which forms a smaller circumferential speed zone. do. According to claim 14, the inner ring is provided with one circumferential groove on the end side in the radial direction of the outer ring to prevent or reduce lubrication loss that may occur in the heated release bearing in the stationary state. In one selected configuration the features for the inner ring claimed in claims 13 and 14 are presented.

In the wound according to the invention according to claim 15, a packing ring is provided for effective airtightness of the ring play between the operating rib and the rotating inner ring. In addition, bearing retaining packing rings are provided on the operating ribs whose packing lips are in contact with the inner ring under preload.

In order to improve the lubrication of the release bearing, a lubricating oil container is installed in the roller bearing according to claim 16, whereby sufficient lubrication is maintained for the life of the roller bearing, such as a vehicle life, in which the release bearing is contained. In this case, the lubricating oil reaches from the lubrication vessel, which is installed in the non-rotating roller ring, to the roll body or roller bearing track by the metering means. Suitable as metering means are wicks which inject the required amount of lubricant into the roller bearings, or instead the means for causing each other capillary action.

According to claim 17, a high strength and mold stability heat-resistant synthetic resin is considered as a material of the operating ribs. Particularly, PA 66 GF can be used to improve strength in addition to reinforcement.

The ring flange of the manipulating ribs of the invention according to claim 18 contains vents distributed around them, which act as outlets of the air circulation and act by the bearing ring shape of the ale bearings to produce a suction effect. Advantageous discharge of the air flow generated by the ring flange is another feature that prevents penetrating roller bearing penetration of dirt particles.

[Brief Description of Drawings]

Other features of the present invention are based on the drafting surface and accompanying drawings.

1 is a half sectional view of a release bearing according to the invention associated with an operating rib

2 is a cup spring cross-sectional view according to the present invention.

3 shows the load curve of the cup spring according to the invention.

In Fig. 1, a cross-sectional view of 1/2 of the operation politics is shown in (1), and includes an operation rib 2 and a release bearing 3. The manipulator 1 is part of a mechanical or hydraulic manipulator which is not presented in more detail of the separation clutch installed in the vehicle between the internal combustion engine and the transmission. The ring piece cone 2 is installed so as to perturb in the axial direction on the drive shaft not shown in FIG. The operating rib 2 is integrally coupled with the ring flange 5 and is parallel to the center of the operating rib 2 with respect to the front surface 4. In the ring flange 5, the release bearing 3 is axially supported by the outer ring 6, and the projection 7 in the vertical radius thereof has a front surface between the ring flange 5 and the shoulder 6. It is in contact with the angle disk 8. The release pair 3, which consists of a single row radial tapered roller bearing, also spans the roller body 9, whereby the outer ring 6 is engaged with the inner ring. When pushing the operating device 1 in the direction of the arrow, the load transfer by the operating sleeve 2 is shown in FIG. It is transmitted to the separating clutch, which is not shown in more detail.

The outer ring 6 is supported on the angle disk 8 by the projection 7 at an appropriate load via the cup spring 17. In it, the cup spring 12 is supported by the rim 13 spaced in the longitudinal direction of the angle disk 8.

The formation of the rim 13 is carried out by subassembly whereby the components, angle discs 8 projections 7 and the cup springs 12 are formed by the ends holding the cup springs 12 outward. Are bonded to each other. Molding results in a structure of the preload of the intended cup spring. The axial spacing of the shoulders of the angle disc 8 is then greater than the sum of the thickness of the cup spring 12 and the protrusion 7. For the positioning and rotational fixation of the angle disc 8 this is a right angled fold 14 outward, in particular supported in parallel in the corresponding groove of the ring flange 5. As an alternative this is also suitable for stiffness between the angle disc 8 and the ring flange 5. The ring flange 5 is also arranged with a circumferentially vented opening 15 arranged in a circumferential circle, which flows into the circulating groove 19 cut into the ring flange 5 and the hole of the angle disk 8. It coincides with or cooperates with the clearance (16) or the clearance (17) and discharges the air flow by the shape of the release bearing (3). The air flow accompanying these contaminants is thus effectively discharged and does not reach the release bearing 3. As another measure to prevent or reduce dirt penetration in the release bearing 3, the inner ring 10 is pushed toward the cup spring 12 under the retention of limited clearance dimensions 18. The inner ring 10 also has a reference edge 19 facing inward, which forms a slower circumferential speed and prevents the inflow of dirt particles inwardly contacting the inner ring 10.

The inner ring 10 has one circumferential groove 20 on the outward side along the radial direction, which prevents the lubricant from being discharged while the release bearing 3 is stopped. In order to effectively seal the ring gap 21 between the inner ring 10 and the ring piston 2, a packing ring 23 is included in the front surface 22 of the operating rib 2 so that the body 11 of the inner ring 10 The chew 24 is preloaded in the ring gap 21 is effectively sealed.

Another packing 25 is fixed to the outer ring 6, the seal lip 26 of which is in contact with the inner ring 10 while being dragged. The seal 25 is at the same time provided with a lubricant container 27 fixed adjacent to the outer ring 6 from which, for example, the wick, accurately metered lubricant is metered by the metering means 28 and the roller body 9 and / or the roller. Is injected into the body track. The foregoing enforcement measures for preventing dust penetration in the release bearing 3 associated with the lubricant container 27 are adapted to the life of the vehicle by increasing the life of the release bearing 3.

In order to influence the loading capacity and wear, the release bearing 3 has a pressure angle of? ≧ 45 ° under load. In addition, the contact, that is, the radius ratio is considered, whereby the radius ratio between the outer ring 6 and the roller body 9 and the inner ring and the roller 9 is set to ≧ 106%. In addition, the roller center line coincides with the outer diameter of the cup spring 12 and the assembled state of the cup spring 12.

2 shows a half cross-sectional view of a cup spring 12 constructed in accordance with the invention and is designed with the following dimensions in mind:

a)

Where ΔR is a relational expression Consists of

b)

On the special curve of FIG. 3, the conventional cup spring of a release bearing is compared with the cup spring by invention. The y-coordinate in the diagram is the spring load F and the spring stroke f is plotted at the χ coordinate. The characteristic curve A is the load-stroke relationship curve for the previous cup spring, and f _A between the spring loads Fmin and Fmax is relatively small. On the contrary, the characteristic curve B of the cup spring according to the invention shows that the spring stroke f _B is quite large (see display). In the same loads Fmin and Fmax, accordingly, a significantly larger value is set in the case of the cup spring 12 according to the invention, which is particularly effective for the tolerance balance and the vortex wheel 6 at the angle disc 8 or the ring flange 5. This is necessary for devices suitable for safer loads.

Claims (18)

In particular, it is applied to a vehicle and operated hydraulically or mechanically. In particular, it has a single housing, in which a control rib 2 is provided in the axial direction and has a ring flange 5 facing outward in the radial direction and on its clutch. It serves to support the release bearing (3) with the facing side, wherein the release bearing (3) has a fixed fixed outer ring (6) and a rotating inner ring (10) and a roller body (9) is provided between the outer ring (6) is fixed to the ring flange (5) in contact with the angle disk (8) by an appropriate load on the radially located projection (7) by the cup spring (12) and the projection (7) and ring flange ( In the release bearing (3) as the operating device (1) for canceling the separation clutch covering the shared contact surface of 5), The angle disc 8 is supported by the fold portion 14 holding the ring flange 5 outwardly along the radial direction and the inner end face of the angle disc 8 radially outwards in the radial direction toward the end side. Together with the edge 13, it forms an almost u-shaped cross-section, which holds the inner end of the projection 7 of the vortex 6 in the assembled state of the release bearing 3, wherein the cup spring is supported. bearing. The method of claim 1, After the combination of the parts and the angle disc 8, the outer ring 6, the cup spring 12, and the rim 13 are attached to the angle disc and hold part of the projection 7 of the cup spring 12 and the outer ring 6 Release bearing characterized in that. The method of claim 1, An axial gap from the rim 13 to the angle disc 8 is characterized in that the cup spring 12 is greater than the sum of the thicknesses of the projections 7. The method of claim 1, A release bearing characterized in that it coincides with the center of the cup spring (12) from the rim (13). The method of claim 1, A release bearing, characterized in that the angle disc (8) is fixed and / or fixedly supported by the ring flange (5) in an appropriate form by the end. The method of claim 1, Frame (13), component, release bearing (3) of the angle disk (8) The release spring, characterized in that the cup spring (12) and the angle disk (8) are combined in a subassembly unit. The method of claim 1, Release bearings characterized by the following dimension ranges for the design of the cup springs 12: a) ΔR is the difference between the cup spring radii b) S is thickness h _O is inside height The method of claim 7, wherein The closed cup spring (12) is a release bearing, characterized in that the outer diameter thereof is the same as the pitch diameter of the Rollum body (9) in the assembled state. The method of claim 1, The release bearing (3) of the roller bearing type is characterized in that the pressure angle is ≧ 45 ° and the radial ratio is ≧ 106%. The method of claim 9, A release bearing, characterized in that a radius ratio in the range of 106 to 112% is set between the inner ring (10) and the roller body (9). The method of claim 9, A release bearing, characterized in that the radius ratio between the outer ring 6 and the roller body 9 takes a value of 110 to 120%. The method according to claim 1 or 9, Release ring, characterized in that the inner ring (10) extends in the direction of the cup spring (12) under the maintenance of the limited clearance dimension (18). The method according to claim 1 or 9, Inner ring (10) is a release bearing characterized in that it has a corner toward the inside in the radial direction at its free end. The method according to claim 1 or 9, The circumferential groove is a release bearing, characterized in that the outer ring free end. The method according to claim 1 or 9, The packing 23 is a release bearing, characterized in that the position is fixed to the operating rib (2) and is in contact with the inner ring (10) by the packing lip (24). The method according to claim 1 or 9, Release bearing (3) characterized in that the lubricant container (27) located on the inner ring (10) or outer ring (6) is provided for lubrication of the roll stop body (9) and / or the roller body track. The method of claim 1, wherein The operating rib 2 is made of a high strength shape stability heat-resistant synthetic resin, and in particular, PA66GF is a release bearing characterized in that it is reinforced to achieve improved strength. The method of claim 17, A ring bearing (5) of the operating rib (2) is a release bearing characterized in that vent holes (15) are arranged in the circumferential direction and are distributed along the circumference.