DE102018101274A1 - clutch release - Google Patents

Abstract

This invention relates to the field of clutches, more particularly to a clutch release system. A clutch release system includes a clutch release bearing and a central release, wherein the central release and the clutch release bearing are interconnected. When the central tripper and the clutch release bearing are in the condition of being connected to each other, the piston of the central releaser abuts directly on the inner ring of the clutch release bearing in the axial direction of the clutch release system. The clutch release system also includes a retaining ring, wherein the retaining ring holds the state of abutment of the piston to the inner ring without being between the piston and the inner ring. In this way, this invention provides a novel clutch release system, wherein in this clutch release system the retaining ring does not protrude into the cavity of the clutch release system for receiving the hydraulic oil, whereby there can be no fin splinters that enter this cavity and cause the problem that the seal failed. And since the retaining ring is not located between the piston and the inner ring, the risk known in the prior art that the retaining ring breaks can not arise.

Description

This invention relates to the field of clutches, more particularly to a clutch release system.

As 1a shows, in clutch release systems for fully hydraulic braking according to the prior art, the clutch release bearing B and the central release C are connected by the retaining ring 50 with each other.

Exactly how 1 b shows, the clutch release bearing B comprises an outer ring 10 and an inner ring 20, which form a roller conveyor for the rollers, rollers and a sealing member 30 for sealing the gap between the outer ring 10 and the inner ring 20, wherein the sealing member 30 in place of the end portion the radial inner side of the inner ring 20 is arranged. By a bent part with approximately U-shaped cross section of an axial side of the retaining ring 50 (left side in 1a and 1b ), the inner ring 20 of the clutch release B, the seal member 30 and a leaf spring 40 are combined with each other; the radial wall 502 of the U-shaped bending part, which is in the middle position on the axis of the retaining ring 50, is clamped between the piston 60 of the central release C and the inner ring 20 of the clutch release bearing B; a circular ring portion 503 of the other axial side of the retaining ring 50 (right side in 1a and 1b ) is mounted on the outer peripheral surface of the piston 60 of the Zentralausrückers C. Furthermore, the other axial end of the inner ring 20 of the clutch release B (right end in 1a and 1b ) is attached to the positioning part 70 of the central release C The Zentralausrücker C also includes a biasing spring 80, wherein the biasing spring 80 exerts on the positioning member 70 a directed on the side biasing pressure on which the inner ring 20 is located. By using the above-described structure, the clutch release bearing B and the central release C can be firmly connected to each other.

One aspect is that in prior art clutch release systems, it is necessary to stamp the annulus portion 503 of the retainer ring 50 to form a flange portion 501 (as in FIG 1c shows), so that by the retaining ring 50, the connection of the clutch release bearing B is realized with the Zentralausrücker C. In the process of forming the flange member 501 by punching, however, burr inevitably arises. Thus, in the operation process of the clutch release system, some burrs will break, enter the cavity of the central release C to receive the hydraulic oil and cause the seal of the piston seal member 90 to fail, which in turn will cause hydraulic oil to leak.

Another aspect is that in prior art clutch release systems when the clutch release system is in operation, the piston 60 of the central release C drives the inner ring 20 of the clutch release bearing B for movement or an unillustrated pressurizing member toward the central release C the clutch release bearing B. drives and, since a part of the retaining ring 50 (namely, the radial wall 502) is located between the piston 60 and the inner ring 20, this results in very strong forces arise at the contact surface between this part of the retaining ring 50 and the piston 60. Therefore, under certain extreme operating conditions, the retainer ring 50 is subjected to a very heavy load and hence the risk of breakage, and possibly fracture occurs between the radial wall 502 and the annulus portion 503.

Based on the above-mentioned deficiency of the prior art, this invention has been made. The object of this invention is to provide a novel clutch release system to overcome the defect that in clutch release systems during assembly burrs of the retaining ring get into the cavity of the central release for receiving the hydraulic oil, and to prevent by the emergence of strong forces between the piston and the retaining ring it comes to breaking the retaining ring.

To realize the stated object of the invention, this invention can use the following technical concepts.

This invention provides a clutch release system as follows, wherein the clutch release system comprises a clutch release bearing and a central release, the central release and the clutch release bearing are interconnected when the Zentralausrücker and the Kupplungsausrücklager are in the state of connecting with each other, the piston of the Zentralausrückers in the axial direction of the clutch release system directly abuts the inner ring of the clutch release bearing, and the clutch release system further comprises a retaining ring, wherein the retaining ring holds the state of abutment of the piston to the inner ring, without being located between the piston and the inner ring.

Preferably, the retaining ring comprises: a retaining ring body, wherein the retaining ring body in its entirety has an annular shape and extends approximately in the axial direction; a bending part, wherein the bending part of an axial End of the retaining ring body extends to the radial outside; and a curvature part, wherein the curvature part extends from the other axial end of the retainer ring body to the radial outside, and the curvature part is attached to the piston from the radial inside of the piston.

More preferably, the bending part extends to both the radial outer side and the axial inner side and abuts the free end of the bending member extending from the retaining body to the inner ring to exert on the inner ring on the side on which the piston is located.

Even more preferably, the free end of the bending part forms an arcuate abutment part which serves to abut the inner ring.

More preferably, the sealing member for sealing the gap between the inner ring and the outer ring of the Kupplungsausrücklagers is arranged on the inner ring, the sealing element comprises a frame which is attached to the inner ring, and abuts the free end of the bent part through the frame on the inner ring.

Even more preferably, a leaf spring is disposed between the bending part and the inner ring abuts an axial end of the leaf spring to the bending part, abuts the other axial end of the leaf spring to the inner ring and exerts the bending part by the leaf spring on the inner ring pressure.

More preferably, the bight portion forms a hook having a backwardly bent shape, and the piston forms a recess for mounting in cooperation with the hook.

Even more preferably, the bending part and the curvature part extend in the circumferential direction of the retaining ring on the entire circumference continuously.

Preferably, the inner ring comprises an inner ring axial part extending approximately in the axial direction of the inner ring and an inner ring radial part extending from one axial end of the inner ring axial part to the radially inner side of the inner ring, the other axial end of the inner ring axial part is attached to the positioning part of the central releaser and the piston abuts the inner ring radial part at.

Even more preferably, the central release includes a biasing spring, the biasing spring exerts on the positioning a directed on the side biasing pressure on which the inner ring is located.

By using the above-mentioned technical concept, a novel clutch release system is presented, in which clutch release system the retaining ring does not protrude into the cavity of the clutch release system for receiving the hydraulic oil, whereby there can be no fin splinters that enter this cavity and cause the problem, that the seal fails, and since the retaining ring is not located between the piston and the inner ring, there may not be the risk known in the art that the retaining ring will break.

list of figures

• 1a Fig. 12 is a partial schematic sectional view of a prior art clutch disengagement system, and provides a clutch release bearing and a central disengager connected together;
• 1b is a partial enlarged schematic representation of a part (left upper part) in 1a ;
• 1c is an overall schematic diagram of a retaining ring of the clutch release system in 1a ,
• 2a Fig. 12 is a partial schematic sectional view of a clutch release system according to this invention;
• 2 B is a partial enlarged schematic representation of a part (including a part of the retaining ring) in 2a ;
• 2c is an overall spatial representation of a retaining ring of in 2a illustrated Kupplungsausrücksystems according to this invention;
• 2d is a partial spatial sectional view of a retaining ring of the 2c illustrated Kupplungsausrücksystems according to this invention;
• 2e is a partial schematic sectional view of a piston in an in 2a illustrated Kupplungsausrücksystem according to this invention.

LIST OF REFERENCE NUMBERS

10 outer ring; 20 inner ring; 30 sealing element; 40 leaf spring; 50 retaining ring; 501 flange part; 502 radial wall; 503 circular ring part; 60 pistons; 70 positioning part; 80 biasing spring; 90 piston seal element

1 outer ring; 2 inner ring; 21 inner ring axial part; 22 inner ring radial part; 3 sealing element; 31 frames; 4 retaining ring; 41 retaining body; 42 bending part; 43 curvature part; 44 kick-off part; 5 pistons; 51 deepening; 6 positioning part; 7 biasing spring

B clutch release bearing; C central release

A axial direction; R radial direction

Hereinafter, the concrete embodiments of this invention will be described in detail with reference to the drawings for description. In this specification, and without any specific reference, "axial direction A" denotes the axial direction of the retainer ring, "axial inner side" the side near the center axis of the retainer ring, "axial outside" means the side remote from the central axis of the retainer ring; "Radial direction R" denotes the radial direction of the retaining ring; "circumferential direction" refers to the circumferential direction of the retaining ring.

As in 2a and 2 B As shown, in a clutch release system according to this invention, the clutch release system comprises a clutch release bearing B and a central release C, which are interconnected.

In this embodiment, the clutch release bearing B in its entirety has an annular shape. The clutch release B includes an outer ring 1 and an inner ring 2 which form a roller conveyor for the rollers, as well as rollers. The inner ring 2 includes an inner ring axial part extending approximately in the axial direction of the clutch release bearing B. 21 and one from an axial end of the inner ring axial part 21 to the radial inner side of the clutch release bearing B extending Innenringradialteil 22 , The clutch release B also includes a sealing element 3 for sealing the gap between the outer ring 1 and the inner ring 2 , where the frame made of metal 31 of the sealing element 3 at the location of the end portion of the radial inner side of the inner ring 2 is attached. The Zentralausrücker C includes mainly components such as a piston 5 , one on the outside of the piston 5 located positioning part 6 and a biasing spring 7, and since the other components of the central release C are identical to the components of prior art central release, description of their structure and functions will be omitted here.

To pass through the retaining ring 4 to cause the connection of the clutch release bearing B to the central release C, is an axial end of the retaining ring 4 as a bending part 42 executed (its structure is described in detail below), wherein by the bending part 42 the inner ring radial part 22 the clutch release B and the sealing element 3 be combined with each other to A in the axial direction to the piston 5 the Zentralausrückers C directed to the inner ring part 22 the clutch release B exercise pressure; and is the other axial end of the retaining ring 4 as a curvature part 43 (its structure will be described in detail below), with the curvature part 43 from the outside of the cavity of the central release C for receiving the hydraulic oil on the piston 5 the central release C is attached.

By using the structure described above, one aspect is that the retaining ring 4 does not have to be between the clutch release bearing B and the central release C, that is, not between the Innenringradialteil 22 the clutch release bearing B and the piston 5 of the central release C must be to the state of abutment of the Innenringradialteils 22 and the piston 5 to hold on, so in this way on the retaining ring 4 not readily the fractures mentioned in the prior art occur.

In addition, it is not necessary on the retaining ring 4 To punch flange parts according to the prior art, which causes the ridges of the retaining ring 4 greatly shrink and the retaining ring 4 can not extend into the cavity of the central release C for receiving the hydraulic oil. This will prevent foreign objects such as burrs on the retaining ring 4 get into the above cavity, eliminating the risk of the prior art that the seal of the piston 5 failed.

Furthermore, the other axial end of the inner ring axial part is 21 of the inner ring 2 of the clutch release B at the positioning 6 the central release C attached. The Zentralausrücker C also includes a biasing spring 7 , wherein the biasing spring 7 on the positioning part 6 exerts a biasing pressure directed to the side on which the inner ring 2 located.

In the following, in connection with the drawings for description, the exact structure of the retaining ring 4 as well as the corresponding structure of the piston 5 described in detail.

In this embodiment, the retaining ring 4 in its entirety an annular shape. Exactly, as in 2c and 2d shown, the retaining ring comprises 4 the retaining ring body 41, the bending part 42 and the curvature part 43 , The retaining ring body 41 has an annular shape and extends in a straight shape approximately in the axial direction A. The bent part 42 is from an axial end of the retaining body 41 bent and extends to the outside in the radial direction R. The curvature part 43 extends from the other axial end of the retaining body 41 to the outside in the radial direction R, which is from the retaining body 41 out extending free end of the curvature part 43 in the recess below 51 of the piston 5 stuck.

In this embodiment, the bent part extends 42 both to the radial outside and in a straight shape to the axial inside, that is, the bending part 42 and the retaining body 41 Make an angle smaller than 90 degrees, and the free end of the holder body 41 out extending bending part 42 abuts the sealing element 3 at. In this way, the free end exerts itself from the retaining body 41 out extending bending part 42 on the inner ring radial part 22 a directed on the side of pressure on which the piston 5 located. When the bending part 42 Forming the above shape can by the bending part 42 the action of the prior art leaf spring can be realized, and therefore the leaf spring of the prior art can be omitted, thus causing a lowering of the production cost. Furthermore, the free end of the bending part 42 forms an arcuate abutment part 44 which is the abutment against the sealing element 3 serves. The impulse part 44 causes the bending part 42 unhindered on the sealing element 3 can be attached and it between the free end and the sealing element 3 does not easily come to a jamming.

In this embodiment, the curvature part forms 43 a hook having a backward bent shape and the piston 5 a depression 51 for clamping in conjunction with the hook on (as in 2e shown). By clamping the hook in the recess 51 can be the bumping of the bending part 42 on the inner ring radial part 22 be promoted to the state of abutment of the piston 5 on the inner ring radial part 22 to keep.

Because the retaining ring 4 using the above concrete structure becomes the flange part 501 omitted in the prior art, which not only the manufacturing cost of the retaining ring 4 but also greatly reduces the occurrence of burrs.

1. 1. Zwar wird in den konkreten Ausführungsformen beschrieben, dass die spezifische Struktur, die der Biegeteil 42 aufweist, die Wirkung der Blattfeder ersetzen kann, doch ist diese Erfindung nicht darauf beschränkt. Es kann auch gemäß dem Stand der Technik so sein, dass sich der Biegeteil 42 in Radialrichtung R in gerader Form zur radialen Außenseite erstreck und dass zwischen dem Biegeteil 42 und dem Dichtungselement 3/ Innenring 2 eine Blattfeder angeordnet ist, so dass ein axiales Ende der Blattfeder an den Biegeteil 42 anstößt, das andere axiale Ende der Blattfeder an das Dichtungselement 3/ den Innenring 2 anstößt und auf diese Weise der Biegeteil 42 durch die Blattfeder auf den Innenring 2 einen Druck ausübt.
2. 2. Zwar erfolgt in den vorstehenden Ausführungsformen keine detaillierte Beschreibung, vorzugsweise jedoch erstrecken sich der Biegeteil 42 und der Krümmungsteil 43 in Umfangsrichtung am gesamten Umfang durchgehend. Natürlich können sich in einigen Fällen der Biegeteil 42 und der Krümmungsteil 43 in Umfangsrichtung am gesamten Umfang mit Unterbrechungen erstrecken.
3. 3. Des Weiteren sind der Krümmungsteil 43 und die Vertiefung 51 des Kolbens 5 nicht auf die oben genannte Form beschränkt, solange erfüllt werden kann, dass der Kolben 5 des Zentralausrückers C und der Innenringradialteil 22 des Kupplungsausrücklagers B den Zustand des gegenseitigen Anstoßens halten.
4. 4. Es ist nachvollziehbar, dass das Weglassen des Dichtungselements 3 keineswegs die Funktionen des Halterings 4 dieser Erfindung und die Vorteile dieser Erfindung beeinträchtigt.

Although the specific embodiments of this invention are described in detail above, the following explanations must still be made:

1. 1. Although it is described in the concrete embodiments that the specific structure that the bending part 42 can replace the action of the leaf spring, but this invention is not limited thereto. It may also be according to the prior art that the bent part 42 in the radial direction R in a straight shape to the radial outside and that between the bent part 42 and the sealing element 3 / Inner ring 2 a leaf spring is arranged so that an axial end of the leaf spring to the bending part 42 abuts the other axial end of the leaf spring to the sealing element 3 / the inner ring 2 abuts and in this way the bending part 42 through the leaf spring on the inner ring 2 exerts a pressure.
2. 2. Although in the above embodiments, no detailed description, but preferably the bending part extend 42 and the curvature part 43 continuous in the circumferential direction on the entire circumference. Of course, in some cases, the bending part 42 and the curvature part 43 extend in the circumferential direction on the entire circumference with interruptions.
3. 3. Furthermore, the curvature part 43 and the depression 51 of the piston 5 not limited to the above form, as long as it can be met that the piston 5 the Zentralausrückers C and the Innenringradialteil 22 of the clutch release B hold the state of mutual abutment.
4. 4. It is understandable that omitting the sealing element 3 By no means the functions of the retaining ring 4 of this invention and the advantages of this invention.

By using the above-mentioned technical concept, a novel clutch release system is presented, wherein in this novel clutch release system on the retaining ring no flange part needs to be punched, no flange protrudes into the cavity of the clutch release system for receiving the hydraulic oil, whereby there may be no burrs, the get into this cavity and thereby lead to the problem that the seal fails; and since the retaining ring is not between the piston and the inner ring, the risk known in the prior art that the retaining ring breaks can not arise.

Furthermore, the scope of this invention is not limited to the specific embodiments of the specific embodiments described above, but as long as the claims of this invention can be met, a combination of technical features falls within the scope of this invention.

Claims (10)

A clutch release system, wherein the clutch release system comprises a clutch release bearing and a central release, the central release and the clutch release bearing are interconnected, characterized in that when the Zentralausrücker and the Clutch release bearing are in the state of connecting to each other, the piston of the central release in the axial direction of the Kupplungsausrücksystems abuts directly to the inner ring of the clutch release bearing, and the Kupplungsausrücksystem also comprises a retaining ring, the retaining ring holds the state of abutment of the piston to the inner ring without him located between the piston and the inner ring. Coupling release system according to Claim 1 characterized in that the retainer ring comprises: a retainer body, the retainer body in its entirety having an annular shape and extending approximately in the axial direction; a bending part, wherein the bending part extends from an axial end of the retaining ring body to the radial outside, and a curving part, wherein the curving part extends from the other axial end of the retaining ring body to the radial outside and the curving part from the radial inside of the piston is attached to the piston. Coupling release system according to Claim 2 , characterized in that the bent part extends to both the radial outer side and the axial inner side and abuts the free end of the retaining ring body extending from the bending part to the inner ring to exert on the inner ring directed to the one side pressure on which the Piston is located. Coupling release system according to Claim 3 , characterized in that the free end of the bending part forms an arcuate abutment part, which serves to abut on the inner ring. Coupling release system according to Claim 3 or 4 characterized in that the sealing member for sealing the gap between the inner ring and the outer ring of the Kupplungsausrücklagers is arranged on the inner ring and the sealing element comprises a frame which is attached to the inner ring, and abuts the free end of the bent part through the frame on the inner ring. Coupling release system according to Claim 2 , characterized in that between the bending part and the inner ring, a leaf spring is arranged, an axial end of the leaf spring abuts the bending part, the other axial end of the leaf spring abuts against the inner ring and the bending part by the leaf spring on the inner ring exerts a pressure. Coupling release system according to Claim 2 characterized in that the curvature part forms a hook having a backwardly bent shape, and the piston forms a recess for mounting in cooperation with the hook. Coupling release system according to Claim 2 , characterized in that the bent part and the curvature part extend continuously in the circumferential direction of the retaining ring over the entire circumference. Coupling release system according to Claim 1 characterized in that the inner ring comprises an inner ring axial part extending approximately in the axial direction of the inner ring, and an inner ring radial part extending from one axial end of the inner ring axial part to the radially inner side of the inner ring, the other axial end of the inner ring axial part being attached to the positioning part of the central releaser, and the piston abuts the inner ring radial part. Coupling release system according to Claim 9 , characterized in that the Zentralausrücker also comprises a biasing spring and the biasing spring exerts on the positioning a directed on the side biasing pressure on which the inner ring is located.

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