CN111749994B - Pressure fluid operation device for friction clutch - Google Patents
Pressure fluid operation device for friction clutch Download PDFInfo
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- CN111749994B CN111749994B CN202010235491.3A CN202010235491A CN111749994B CN 111749994 B CN111749994 B CN 111749994B CN 202010235491 A CN202010235491 A CN 202010235491A CN 111749994 B CN111749994 B CN 111749994B
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- blocking
- release
- ramp
- operating
- pressure fluid
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- 239000012530 fluid Substances 0.000 title claims abstract description 72
- 230000000903 blocking effect Effects 0.000 claims abstract description 183
- 230000015572 biosynthetic process Effects 0.000 claims abstract description 48
- 238000001514 detection method Methods 0.000 claims abstract description 36
- 238000005755 formation reaction Methods 0.000 claims description 42
- 238000006073 displacement reaction Methods 0.000 claims description 21
- 230000013011 mating Effects 0.000 claims description 19
- 238000000034 method Methods 0.000 claims description 10
- 230000003993 interaction Effects 0.000 claims description 9
- 230000002093 peripheral effect Effects 0.000 description 11
- 230000009471 action Effects 0.000 description 9
- 230000008569 process Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 5
- 238000007789 sealing Methods 0.000 description 5
- 230000004323 axial length Effects 0.000 description 4
- 230000036316 preload Effects 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 230000004888 barrier function Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000012535 impurity Substances 0.000 description 2
- 238000011017 operating method Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/087—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation the clutch being actuated by the fluid-actuated member via a diaphragm spring or an equivalent array of levers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/083—Actuators therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/126—Details not specific to one of the before-mentioned types adjustment for wear or play
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/75—Features relating to adjustment, e.g. slack adjusters
- F16D13/755—Features relating to adjustment, e.g. slack adjusters the adjusting device being located in or near the release bearing
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
A pressure fluid operated device for a friction clutch having a compensating assembly, comprising: -a first ramp element which is axially supported relative to the second operating element in the direction of the movement axis and which is preloaded by a first preloading device for rotation relative to the second operating element about the movement axis, the first ramp element having a first ramp formation, -a second ramp element which together with a rotational decoupling bearing is movable in the direction of the movement axis, wherein the second ramp element has a second ramp formation and is supported by means of the second ramp formation at the first ramp formation in the direction of the movement axis, wherein the second ramp element is not rotatable relative to the second operating element about the movement axis, and wherein the axial structural length of the compensating assembly is reduced in the event of a rotation of the first ramp element relative to the second ramp element about the movement axis by the first preloading device, -a release/blocking assembly which is adjustable between a blocking position and a release position, the release/blocking assembly having a counter-blocking formation which is in blocking engagement with the blocking formation at the first operating element in the blocking position, wherein the release/blocking assembly has a detection area which interacts with the first operating element in order to adjust the release/blocking assembly from the blocking position into the release position.
Description
Technical Field
The present invention relates to a pressure fluid operating device, for example, for use in trucks for operating friction clutches.
Background
Such pressure fluid operated devices generally comprise a cylinder fixedly positioned with respect to the vehicle and a piston defining a pressure fluid chamber with the cylinder and displaceable in the direction of the movement axis. The piston can be loaded via a rotary decoupling bearing with a force store, for example a spring tongue of a diaphragm spring, in order to carry out the clutch operation in this way. The insertion position of the diaphragm spring used as a force accumulator in the engaged state of the friction clutch changes as a function of wear occurring in the friction clutch, for example, of the friction linings of the clutch disk, since the diaphragm spring gradually relaxes as the wear increases when moving into the engaged state compared to the state in which no wear is present.
Disclosure of Invention
The object of the present invention is to provide a pressure fluid actuating device for a friction clutch which allows for wear-induced changes in the installation position of a force accumulator of the friction clutch in a simple and reliable manner.
According to the invention, the object is achieved by a pressure fluid operated device for a friction clutch comprising
A first operating element and a second operating element defining a pressure fluid chamber with the first operating element, wherein the second operating element can be moved in an operating direction relative to the first operating element along a movement axis by introducing pressure fluid into the pressure fluid chamber, wherein preferably the second operating element is not rotatable relative to the first operating element about the movement axis,
A rotational decoupling bearing coupled via a compensation assembly to the second operating element for common movement in the direction of the movement axis,
Wherein the compensation assembly comprises:
a first ramp element which is axially supported relative to the second operating element in the direction of the displacement axis and is preloaded by a first preloading device for rotation about the displacement axis relative to the second operating element, said first ramp element having a first ramp formation,
A second ramp element which together with the rotational decoupling bearing can be moved in the direction of the axis of movement, wherein the second ramp element has a second ramp formation and is supported by means of the second ramp formation at the first ramp formation in the direction of the axis of movement, wherein the second ramp element is not rotatable relative to the second operating element about the axis of movement, and wherein the axial structural length of the compensation assembly is reduced in the event of a rotation of the first ramp element relative to the second ramp element about the axis of movement by means of the first pretensioning device,
A release/blocking assembly which can be adjusted between a blocking position and a release position and which has a counter blocking profile which in the blocking position is in blocking engagement with the blocking profile at the first actuating element, wherein the release/blocking assembly has a detection region which interacts with the first actuating element for adjusting the release/blocking assembly from the blocking position into the release position.
In the structure according to the invention of the pressure fluid operating device, excessive movement of the second operating element relative to the first operating element caused by wear in the friction clutch is detected by interaction of the release/blocking assembly with the first operating element, and the first ramp element is released to perform the readjusting movement only when such excessive movement is detected. This readjusting movement results in the axial length of the compensation assembly comprising the two ramp elements being reduced and accordingly the force store of the friction clutch, i.e. for example the diaphragm spring, being provided with the possibility of further loosening in the engaged state of the friction clutch to a degree corresponding to the wear occurring. With the pressure fluid actuating device configured in this way, an improved regulation and in particular an improved dynamics is achieved when executing a clutch actuating process on the basis of the minimum dead volume of the pressure fluid chamber.
For a uniform operation effect, it is proposed that: the first operating element is a cylinder, preferably an annular cylinder, and the second operating element is a piston, preferably an annular piston.
In particular, in the case of an annular design of the two actuating elements, it is advantageous if the first ramp element is formed annularly and has at least one, preferably a plurality of, first ramp formations extending in the circumferential direction, and the second ramp element is formed annularly and has at least one, preferably a plurality of, second ramp formations extending in the circumferential direction.
In order to load the first ramp element for carrying out the readjustment process, the first pretensioning device can comprise a first pretensioning spring extending in the circumferential direction about the displacement axis, wherein the first pretensioning spring is supported with its one end region relative to the second operating element and with its other end region relative to the first ramp element.
In order to provide a mobile coupling between the second ramp element and the rotationally decoupled bearing and at the same time also ensure a defined positioning of the different system components for carrying out the readjustment process, it is proposed that the second ramp element is coupled in a rotationally fixed manner to the second actuating element and is movable relative thereto in the direction of the movement axis.
The second actuating element can be preloaded in the actuating direction by a second preloading device relative to the first actuating element in the direction of the displacement axis. By means of the second pretensioning device, the loose force store is also counteracted, so that a force balance is established in the engaged state of the friction clutch.
For a defined interaction between the release/blocking assembly and the first ramp element, it is proposed that the release/blocking assembly comprises a release/blocking element which is movable at the second operating element substantially in the direction of the movement axis between a blocking position and a release position, wherein the release/blocking element is provided with third pretensioning means for pretensioning the release/blocking element into its blocking position relative to the second operating element.
The spatial separation of the blocking/releasing function and of the second actuating element relative to the first actuating element on the other hand can be achieved in that the releasing/blocking element has a detection section which is arranged at the axial side of the second actuating element facing away from the first actuating element and has a release/blocking section of the mating blocking formation and a detection region which extends through the second actuating element and protrudes for a detection interaction with the first actuating element at the axial side of the second actuating element facing the first actuating element.
In order to pre-load the release/blocking element in a defined manner into its position already present for detecting an excessive movement of the second actuating element, it is proposed that the third pre-load device comprises a pre-load spring that is supported relative to the detection section and the second actuating element and is to pre-load the detection section in the direction of the first actuating element.
In an alternative embodiment, in which the release/blocking assembly is provided essentially separately from the second actuating element, the release/blocking assembly can comprise a release/blocking element having an annular release/blocking element body, which is arranged on the axial side of the second actuating element facing away from the first actuating element, wherein the release/blocking element is provided with a third pretensioning device for pretensioning the release/blocking element body in a release direction opposite to the actuating direction toward the second actuating element.
For the release/blocking interaction with the first ramp element, a release/blocking region with a mating blocking formation can be provided at the release/blocking element body. Furthermore, a detection region is provided at the release/blocking element body for detecting an excessive axial displacement of the second actuating element due to excessive wear of the friction clutch, said detection region being in detecting interaction with the first actuating element.
In order to achieve a simple structure, it is proposed that the release/blocking region comprises a release/blocking part which is fastened to the release/blocking element body and has a mating blocking formation, and that the detection region comprises a detection section which protrudes radially outwards from the annular release/blocking element body for a detection interaction with the first actuating element.
The stable blocking action can be achieved in that the blocking formation comprises at the first ramp element a blocking engagement which is at least partially annularly around the movement axis and which is oriented axially in a direction away from the first operating element, and the counter blocking formation comprises at the release/blocking assembly a counter blocking engagement which is oriented axially in a direction towards the first operating element and which can be brought into blocking engagement and out of blocking engagement with the blocking engagement by axially displacing the release/blocking assembly relative to the second operating element.
The invention also relates to a clutch system comprising a friction clutch having a force store that can be loaded by a pressure fluid operated device according to any of the preceding claims to perform a clutch operation.
Drawings
The present invention is described in detail below with reference to the attached drawings. The drawings show:
FIG. 1 shows a partial longitudinal cross-sectional view of a pressure fluid operated device for a friction clutch;
FIG. 2 shows a cross-sectional view of the pressure fluid operating apparatus of FIG. 1 taken along line II-II in FIG. 1;
Fig. 3 shows a perspective view of the release/blocking element;
fig. 4 shows the pressure fluid operating device of fig. 1 in a state of being loaded with pressure fluid;
FIG. 5 shows the pressure fluid operated device of FIG. 1 in a state where there is little wear of the friction clutch;
Fig. 6 shows the pressure fluid operating device of fig. 1 in a state in which there is a strong wear of the friction clutch to be compensated;
Fig. 7 shows a longitudinal section through an alternative embodiment of a pressure fluid actuating device for a friction clutch;
FIG. 8 illustrates a cross-sectional view of the pressure fluid operated device of FIG. 7 taken along line VIII-VIII in FIG. 7;
fig. 9 shows a perspective view of a portion of the pressure fluid operating apparatus of fig. 7.
Detailed Description
Fig. 1 shows a partial longitudinal section through a pressure fluid-operated device 10, also commonly referred to as a decoupler, for a friction clutch 12. The friction clutch 12 is shown as a force accumulator 14 which is provided in this case and is embodied, for example, as a diaphragm spring.
The pressure fluid operating device 10 comprises a first operating element 16 provided as an annular cylinder, which by means of its substantially annular structure, annularly surrounds the displacement axis a. The second operating element 22, which is substantially engaged between the inner peripheral wall portion 18 and the outer peripheral wall portion 20 of the first operating element 16, provides an annular piston annularly about the movement axis a. The second operating element 22 is guided fluid-tightly against the inner peripheral wall portion 18 and the outer peripheral wall portion 20 of the first operating element 16 and movably in the direction of the movement axis a relative to said first operating element via a plurality of sealing/guiding elements 24.
A pressure fluid chamber 26 is formed between the first operating element 16 and the second operating element 22, which is closed in a fluid-tight manner by means of different sealing/guiding elements 24. A pressure fluid, for example compressed air, can be introduced into the pressure fluid chamber 26 via a not-shown interface in order to build up a force effect in the pressure fluid chamber 26, which acts to charge or move the second actuating element 22 in the actuating direction B relative to the first actuating element 16. When the second actuating element 22 is displaced in the displacement direction B, it acts via a rotary decoupling bearing 28, which is held, for example, on the second actuating element 22, on a radially inner region of the force accumulator 14, which is formed, for example, as a diaphragm spring, for example, a spring tongue which engages radially inwards, in order to displace or pivot it in order to perform a decoupling process in the displacement direction B and in this way to reduce or eliminate the effect of the force accumulator 14 on the pressure plate of the friction clutch 12.
The second operating element 22 is axially supported by means of a compensating assembly 30 relative to the rotational decoupling bearing 28. The compensation assembly 30 comprises a first ramp element 32 annularly surrounding the axis of movement a and a second ramp element 34 connected to the first ramp element, also annularly surrounding the axis of movement a. The first ramp element 32 has a first ramp formation 36 with a plurality of ramp surfaces that are successive in the circumferential direction. Correspondingly, the second ramp element 36 has a second ramp formation 38 with a plurality of ramp surfaces which are successive in the circumferential direction. The slope of the first ramp forming part 36 abuts the slope of the second ramp forming part 38. The ramp elements 32, 34, which bear against one another by means of their ramp surfaces or ramp formations 36, 38, provide such a supporting characteristic of the compensation arrangement 30 that a relative rotation of the two ramp elements 32, 34 with respect to one another causes a change in the axial structural length of the compensation arrangement 30 due to the ramp surfaces of the ramp formations 36, 38 sliding on one another.
The second actuating element 22 is held in a rotationally fixed and axially movable manner relative to the second ramp element 34 by means of an anti-rotation profile 40. The anti-rotation formation 40 comprises, for example, a groove in the second ramp element 34 extending in the direction of the movement axis a and a guide projection engaging into the groove and extending longitudinally in the direction of the movement axis a at the second operating element 22. In a similar manner, an anti-rotation between the first operating element 16 and the second operating element 22, which allows an axial relative movement, can also be caused.
The first ramp element 32 is provided with a first pretensioning device 42. The first pretensioning device 42 comprises a first pretensioning spring 44, which is embodied, for example, as a coil spring, which engages with its one circumferential end on the first ramp element 32 and with its other circumferential end on the second actuating element 22, so that the first ramp element 32 is pretensioned by the first pretensioning device 42 in order to rotate relative to the second actuating element 22.
A second pretensioning device 46 acts between the first operating element 16 and the second operating element 22, which second pretensioning device provides a force action that pretensions the second operating element 22 against the loading action of the force store 14 in the operating direction B relative to the first operating element 16. The second pretensioning spring 48 comprises, for example, a helical compression spring arranged in the pressure fluid chamber 26 about the displacement axis a.
The release/blocking assembly 50 is disposed at the second operating element 22 and substantially blocks the first ramp element 32 from rotating relative to the second operating element 22. The release/blocking assembly 50 comprises a release/blocking element 52 shown in fig. 3, which is adjustably guided at the second operating element 32 in the direction of the axis of movement a. For this purpose, the release/blocking element 52 can comprise a plurality of guide projections 56, for example two, which are arranged at a distance from one another in the circumferential direction, which engage in corresponding guide recesses in the second operating element 22. By means of the guide projection 56 engaging into the guide recess, it is at the same time ensured that the release/blocking element 52 is not rotatable relative to the second operating element 22 about an axis parallel to the axis of movement a.
A release/blocking section 60 of the release/blocking element 52 is provided on an axial side 58 of the second actuating element 22 facing away from the first actuating element 16. In association with a mating blocking formation 62 provided at the release/blocking section 60, a blocking formation 64 is provided at the second operating element 22 at its axial side 58. The blocking formation 64 can have, for example, a blocking engagement 66 at the second actuating element 22, which is formed completely and around the displacement axis a and is oriented axially in a direction away from the first actuating element 16, i.e. has teeth extending in this direction away from the first actuating element 16, with teeth formed between them in the circumferential direction. In a manner corresponding to this blocking engagement 66, a mating blocking engagement 68 providing a mating blocking formation 62 is provided at the release/blocking section 60. The counter blocking engagement has a plurality of teeth which are successive to one another in the circumferential direction and which extend axially toward the first actuating element 16, with tooth gaps formed between them in the circumferential direction. The mating blocking engagement portion 68 can be brought into engagement with the blocking engagement portion 66 by axial movement onto the blocking engagement portion. The blocking engagement portion 66 and the mating blocking engagement portion 68 can be disengaged by the opposite axial relative movement.
At the release/blocking element 52, a detection section 72 is provided which extends through the second operating element 22 and protrudes at the axial side of the second operating element 22 facing the first operating element 16 toward the first operating element 16 and essentially provides a detection region 71 which extends through an opening 73 in the second operating element. In order to avoid leakage of pressure fluid from the pressure fluid chamber 26, a sealing element 75, for example, in the form of an O-ring, acts between the detection section 72 and the second actuating element 22. The third pretensioning device 74 comprises a third pretensioning spring 76, which is formed in the manner of a diaphragm spring, surrounds the detection section 72 and is supported relative to the detection section and the second actuating element 22. By means of this third pretensioning spring, the release/blocking element 52 is pretensioned with its release/blocking section 60 in the direction of the second actuating element 22 and at the same time with its counterpart blocking engagement 68 in the direction of the blocking engagement 66 or in engagement therewith. In this blocking state, the first ramp element 32 is blocked against rotation relative to the second operating element 22.
Fig. 1 shows a state of a pressure fluid operating device 10, which is used, for example, in conjunction with a new or wear-free friction clutch 12, and the friction clutch 12 is in the engaged state. This means that the force store 14 via the rotary decoupling bearing 28 and the compensation assembly 30 moves or pretensions the second actuating element 22 into a basic position relative to the first actuating element 16, in which the force between the second pretensioning spring 48 and the force store 14 is balanced and the pressure fluid chamber 26 provides a dead volume which allows the second actuating element 22 to move slightly beyond the basic position onto the first actuating element 16 in a release direction F opposite to the actuating direction B. The second operating element 22 can be moved beyond the basic position in the release direction F still further onto the first operating element at least as great as the axial engagement depth of the blocking engagement 66 with the counter blocking engagement 68, which can lie in the range of approximately 3mm.
To perform the operating procedure, a pressure fluid, for example compressed air, is introduced into the pressure fluid chamber 26. As a result of the fluid pressure that is built up, a force is exerted on the second operating element 22, which forces it to the left in the view of fig. 3. Via the compensation assembly 30, the rotary decoupling bearing 28 is displaced axially in the operating direction B, so that it acts on a radially inner region of the force accumulator 14, i.e. a radially inner end of a spring tongue, for example of a diaphragm spring, and thus the friction clutch 12 is disengaged. In order to engage the friction clutch, the fluid pressure in the pressure fluid chamber 26 is released, so that the second actuating element 22 is again moved by the loose force accumulator 14 and by the pretensioning action of the second pretensioning spring 48 into its basic position shown in fig. 1 relative to the first actuating element 16, in which the already mentioned dead volume is present, i.e. the axial distance between the two actuating elements 16, 22 is also present.
The first ramp element 32 is preloaded by its associated first pretensioning device 42 for rotation in the circumferential direction relative to the second operating element 22. Because the mating blocking engagement portion 68 of the release/blocking element 52 is in engagement with the blocking engagement portion 66 at the first ramp element 32, the first ramp element 32 is not able to rotate relative to the second operating element. Furthermore, the slope of the two ramp formations 36, 38 is set such that they are self-locking and the axial forces acting when performing the operating procedure do not result in a forced rotation of the two ramp elements 32, 34 relative to each other. The self-locking effect can also be enhanced in that impurities can enter into the spatial region in which the two ramp formations 36, 38 are contained, which can also place the impurities between the ramp surfaces against one another, which can in turn cause enhanced friction.
If wear occurs in the friction clutch 12, this causes the force store 14 to relax further when engaged than if there were little or no wear. This means that the radially inner region of the force store 14 continues to move in the release direction F and the second actuating element 22 moves more closely beyond the basic position toward the first actuating element 16. This is basically possible because of the aforementioned dead volume of the pressure fluid chamber 26 in the case of the second operating element 22 being arranged in the basic position. This state is shown in fig. 5. It can be seen that the detection section 72 of the release/blocking element 52 abuts against the first operating element 16 and that the release/blocking element 52 cannot follow the movement of the second operating element 22 beyond the basic position in the release direction F. However, the wear occurring in the friction clutch 12 is also so small in this state that the counter blocking engagement 68 is also brought into engagement with the blocking engagement 66, despite the release/blocking element 52 being moved axially relative to the second actuating element 22. In this state, the first ramp element 32 is blocked against rotation relative to the second operating element 22 as before. By introducing pressure fluid into the pressure fluid chamber 26, the separation process can also be performed without compensation for wear that has occurred.
If further wear occurs in the friction clutch 12, this results in a state in which the force accumulator 14 relaxes when the friction clutch 12 is engaged to such an extent that it moves the second actuating element 22 axially still further than the basic position via the rotational decoupling bearing 28 and the compensation assembly 30. This state is shown in fig. 6. The detection section 72 again abuts against the first operating element 16 and the counter blocking engagement 68 is no longer engaged with the blocking engagement 66 by excessive axial movement of the second operating element 22 in the release direction F beyond the basic positioning. From now on, the pretensioning force generated by the first pretensioning spring 44 is sufficient to rotate the first ramp element 32 relative to the second operating element 22 about the displacement axis a. As a result of the ramp formations 36, 38 abutting one another and sliding relative to one another in this rotational movement, the axial overall length of the compensation assembly 30 decreases in this rotational movement of the first ramp element 32.
Because the second ramp element 34 is held in a defined axial position by the force store 14, the second actuating element 32 is displaced axially away from the first actuating element under the pretensioning action of the second pretensioning spring 48 when the axial overall length of the compensation assembly 30 decreases. The first ramp element 32, which is under axial load of the second operating element 22, rotates until the blocking engagement 66 and the counter blocking engagement 68 again come into engagement with each other as the axial structural length of the compensation assembly 30 decreases. This can be the case, for example, when the teeth of the blocking engagement 66 and the counter blocking engagement 68 rotate one tooth relative to one another during the course of the rotational movement of the first ramp element 32. In the event that the blocking engagement 66 and the counter blocking engagement 68 then engage one another again, a force balance is established between the pretension of the force store 14, which is relaxed in the engaged state of the friction clutch 12 and acts essentially in the release direction F, and the pretension of the second pretension spring 48, which acts in the actuating direction B. The second actuating element 22 essentially again carries out the wear compensation process in the manner and method described above in its basic position relative to the first actuating element 16, in which the actuating process can then again be carried out taking into account the dead volume of the pressure fluid chamber 26 that is present for the subsequently compensated state, and then the second actuating element 22 reaches the state shown in fig. 6 in the engaged state of the friction clutch 12 when such wear again occurs in the friction clutch 12.
If, for example, completely worn clutch disks are replaced in the friction clutch 12 or a new friction clutch is installed in the vehicle, it is necessary that the hydraulic fluid actuating device 10 is also placed in a state which is associated with the new state of the friction clutch. For this purpose, after release of the blocking effect of the release/blocking assembly 50, the first ramp element 32 must be pivoted back again against the pretensioning effect of the first pretensioning spring 44 in order to thereby increase the axial overall length of the compensation assembly 30 again and to make possible a subsequent operation of the friction clutch in which a rotation of the first ramp element 32 can occur again to an extent corresponding to wear and a reduction in the axial overall length of the compensation assembly 30 can occur.
In order to ensure that the pressure fluid operating device 10 can be operated in emergency operation and that the friction clutch 12 can be operated as before in the event of failure of the compensating assembly 30, for example in the event of complete collapse of the axially mutually supported ramp elements 32, 34, the second operating element 22 can be moved to the greatest extent at the inner 18 and outer 20 peripheral wall portions of the first operating element 16, so that in this case complete disengagement of the friction clutch 16 is ensured.
With reference to fig. 7-9, an alternative design of the pressure fluid operating device 10 is described below. In the basic terms, this embodiment corresponds in particular also to the structure described above in terms of transmitting the actuating forces via the two ramp elements 32, 34 which are in contact with one another by means of the respective ramp formations 36, 38, so that reference can be made to the above-described embodiments.
The basic construction differs in that the release/blocking assembly 50 is structurally decoupled from the second operating element 22. The release/blocking assembly 50 comprises a release/blocking element 52 which is formed by means of an annular release/blocking element body 78. The release/blocking element body 78 is annularly about the axis of movement a and is also located substantially radially outside the ramp elements 32, 34 or outside the ramp formations 36, 38 thereof or radially inside the peripheral wall portion 20 of the first operating element 16. The detection region 71 is provided integrally at the release/blocking element body 78 and is provided by a radially outwardly projecting flange-shaped detection section 72 which preferably radially overlaps an axial end of the peripheral wall portion 20 of the first operating element 16 over the entire circumference about the displacement axis a. By means of a third pretensioning spring 76 of the third pretensioning device 74, which is in the form of a helical compression spring, for example, and which surrounds the displacement axis a, the release/blocking element body 78 is pretensioned in the release direction F in the direction of the first ramp element 32, the second actuating element 22 or also the first actuating element 16. The third pretensioning spring 76 is supported here, for example, at the second ramp element 34. By this pretensioning action, the detection section 72 is substantially pretensioned against the outer peripheral wall portion 20 of the first operating element 16.
A release/blocking region 80 is provided in the circumferential region at the radially inwardly engaging region of the release/blocking element body 78. The release/blocking region is formed separately in the example shown and comprises a release/blocking part 82 which is fastened to the release/blocking element body 78 by riveting. At the release/blocking part 82, a mating blocking formation 62 and its mating blocking engagement 68 are formed.
The blocking formation 64 is provided with its blocking engagement 66 at least in the circumferential region of the first ramp element 32 which interacts with the release/blocking region 80. In this embodiment too, the blocking engagement 66 is formed into a mating blocking engagement 68 having teeth protruding in the axial direction, so that the teeth can be brought into and out of engagement by an axial relative movement between the first ramp element 32 and the release/blocking element 52.
In the state shown in fig. 7, the second actuating element 22 is in its basic position relative to the first actuating element 16 in the engaged friction clutch 12, for example, in the absence of wear. In this embodiment of the second pretensioning device 46, a second pretensioning spring 48, which is embodied, for example, as a bellows spring or the like, holds the second actuating element 22 at a distance from the first actuating element 16, so that basically the second actuating element 22 can be moved in the release direction F toward the first actuating element 16 beyond the basic position. By the pretensioning action of the second pretensioning device 46 on the one hand and the third pretensioning device 74 on the other hand, the blocking engagement 66 is held in engagement with the counter blocking engagement 68 such that the first ramp element 32, which is under pretensioning by the first pretensioning device 42, cannot be rotated, so that the relative positioning of the first actuating element 22 relative to the defined axial direction of the rotary decoupling bearing 28 is preset and the friction clutch 12 can be actuated correspondingly defined by introducing pressure fluid into the pressure fluid chamber 26.
If wear occurs in the friction clutch 12, this causes a further loosening when the force accumulator 14 is engaged, so that its radially inner region moves further in the release direction F toward the first actuating element 16. By the force action of the force store 14, the second actuating element 23 and the release/blocking element 52, which is preloaded against it by the third preloading device 74, are displaced in the release direction F until the detection section comes to rest against the peripheral wall 20 when the basic positioning is reached. Since in this state the force store 14 is still further relaxed, the second actuating element 22 is moved further in the release direction F against the pretensioning action of the second pretensioning device 46 beyond the basic position toward the first actuating element 16. The release/blocking element 52 is not able to follow this movement. As a result of the relative movement occurring between the release/blocking element 52 and the second operating element 22 or the first ramp element 32 axially supported thereon, the blocking engagement 66 and the counter blocking engagement 68 are disengaged, with the result that, from now on, the first ramp element 32 is released to rotate about the axis of rotation a and rotates relative to the second ramp element 34 under the pretensioning action of the first pretensioning device 42. The axial length of the compensation assembly 30, which comprises the two ramp elements 32, 34, is reduced here. The second actuating element 22, which is acted upon by the second pretensioning device 46 in the actuating direction B, follows this reduction in axial length and is moved in the actuating direction B away from the first actuating element 16 in the direction of its basic positioning. The blocking engagement 66 and the counter blocking engagement 68 are again engaged with one another, so that after wear compensation, the two ramp elements 32, 34 are again firmly prevented from rotating relative to one another by the release/blocking assembly 50 and an operating process can again be carried out with a shortened axial length of the compensation assembly 30.
In a pressure fluid actuating device of a pressure fluid chamber, which is designed according to the invention, the dead volume reserved for carrying out the compensation process is relatively small and does not substantially impair the accuracy of actuation of the friction clutch. In particular, the dead volume remains substantially constant over the operating life of the friction clutch, so that a constant operating characteristic can also be ensured over the operating life.
List of reference numerals
10. Pressure fluid operation device
12. Friction clutch
14. Force storage
16. A first operating element
18. Inner peripheral wall portion
20. Peripheral wall part
22. A second operating element
24. Sealing/guiding element
26. Pressure fluid chamber
28. Rotary decoupling bearing
30. Compensation assembly
32. First ramp element
34. Second ramp element
36. First slope forming part
38. Second slope forming part
40. Anti-rotation forming part
42. First pretensioning device
44. First pretension spring
46. Second pretensioning device
48. Second pretension spring
50. Release/barrier assembly
56. Release/blocking element
58. Axial side
60. Release/blocking section
62. Mating blocking forming part
64. Barrier forming part
66. Blocking engagement
68. Mating blocking engagement
70. Axial side
71. Detection area
72. Detection section
73. An opening
74. Third pre-tightening device
75. Sealing element
76. Third pre-tightening spring
78. Release/blocking element body
80. Release/blocking area
82. Release/blocking member
Aaxis of movement
B direction of operation
C release direction
Claims (17)
1. A pressure fluid operated device for a friction clutch, comprising:
A first operating element (16) and a second operating element (22) defining a pressure fluid chamber (26) with the first operating element (16), wherein the second operating element (22) is movable in an operating direction (B) along a movement axis (A) relative to the first operating element (16) by introducing pressure fluid into the pressure fluid chamber (26),
A rotational decoupling bearing (28) coupled to the second actuating element (22) via a compensation assembly (30) for common movement in the direction of the axis of movement (A),
Wherein the compensation assembly (30) comprises:
A first ramp element (32) which is axially supported relative to the second operating element (22) in the direction of the displacement axis (A) and which is preloaded by a first preloading device (42) for rotation about the displacement axis (A) relative to the second operating element (22), said first ramp element having a first ramp formation (36),
-A second ramp element (34) which is movable together with the rotational decoupling bearing (28) in the direction of the displacement axis (a), wherein the second ramp element (34) has a second ramp formation (38) and is supported by means of the second ramp formation (38) at the first ramp formation (36) in the direction of the displacement axis (a), wherein the second ramp element (34) is not rotatable relative to the second operating element (22) about the displacement axis (a), and wherein the axial structural length of the compensation assembly (30) is reduced in the event of a rotation of the first ramp element (32) relative to the second ramp element (34) about the displacement axis (a) by means of the first pretensioning device (42),
-A release/blocking assembly (50) adjustable between a blocking position and a release position, having a counter-blocking formation (62) in blocking engagement with a blocking formation (64) at the first operating element (16) in the blocking position, wherein the release/blocking assembly (50) has a detection region (71) which interacts with the first operating element (16) for adjusting the release/blocking assembly (50) from the blocking position into the release position, characterized in that the first pretensioning device (42) comprises a first pretensioning spring (44) extending in a circumferential direction about the movement axis (a), wherein the first pretensioning spring (44) is supported with one of its end regions relative to the second operating element (22) and with its other end region relative to the first ramp element (32).
2. Pressure fluid operating device according to claim 1, characterized in that the first operating element (16) is a cylinder and the second operating element (22) is a piston.
3. The pressure fluid operated device of claim 2, wherein the cylinder is an annular cylinder.
4. A pressure fluid operated device according to claim 2 or 3, wherein said piston is an annular piston.
5. A pressure fluid operating device according to any one of claims 1 to 3, characterized in that the first ramp element (32) is annular and has at least one first ramp formation (36) extending in the circumferential direction, and the second ramp element (34) is annular and has at least one second ramp formation (38) extending in the circumferential direction.
6. Pressure fluid operating device according to claim 5, characterized in that the first ramp element (32) has a plurality of first ramp formations (36) extending in the circumferential direction.
7. Pressure fluid operating device according to claim 5, characterized in that the second ramp element (34) has a plurality of second ramp formations (38) extending in the circumferential direction.
8. A pressure fluid operating device according to any one of claims 1 to 3, characterized in that the second ramp element (34) is coupled with the second operating element (22) in a rotationally fixed manner and with respect thereto in the direction of the displacement axis (a).
9. A pressure fluid operating device according to any one of claims 1 to 3, characterized in that the second operating element (22) is preloaded in the operating direction (B) in the direction of the movement axis (a) relative to the first operating element (16) by a second preloading device (46).
10. A pressure fluid operated device according to any one of claims 1 to 3, characterized in that the release/blocking assembly (50) comprises a release/blocking element (52) which is movable at the second operating element (22) substantially in the direction of the movement axis (a) between the blocking position and the release position, wherein the release/blocking element (52) is provided with third pretensioning means (74) for pretensioning the release/blocking element (52) into its blocking position with respect to the second operating element (22).
11. Pressure fluid handling device according to claim 10, characterized in that the release/blocking element (52) has a release/blocking section (60) provided at an axial side (58) of the second handling element (22) facing away from the first handling element (16) and having the mating blocking formation (62) and a detection section (72) of the detection region (71) which extends through the second handling element (22) and protrudes for a detection interaction with the first handling element (16) at an axial side (70) of the second handling element (22) facing towards the first handling element (16).
12. Pressure fluid operating device according to claim 11, characterized in that the third pretensioning device (74) comprises a pretensioning spring (76) which is supported relative to the detection section (72) and the second operating element (22) and is to pretension the detection section (72) in the direction towards the first operating element (16).
13. A pressure fluid operating device according to any one of claims 1 to 3, characterized in that the release/blocking assembly (50) comprises a release/blocking element (52) with an annular release/blocking element body (78) which is arranged at an axial side (58) of the second operating element (22) facing away from the first operating element (16), wherein the release/blocking element (52) is provided with third pretensioning means (74) for pretensioning the release/blocking element body (78) towards the second operating element (22) in a release direction (F) opposite to the operating direction (B).
14. Pressure fluid handling device according to claim 13, characterized in that a release/blocking area (80) with the mating blocking formation (62) and a detection area (71) in detection interaction with the first handling element (16) are provided at the release/blocking element body (78).
15. Pressure fluid handling device according to claim 14, characterized in that the release/blocking area (80) comprises a release/blocking part (82) fixed at the release/blocking element body (78) and having the mating blocking formation (62), and in that the detection area (71) comprises a detection section (72) protruding radially outwards from the annular release/blocking element body (78) for detection interaction with the first handling element (16).
16. A pressure fluid operated device according to any one of claims 1 to 3, characterized in that the blocking formation (64) comprises at the first ramp element (32) a blocking engagement (66) at least partially annularly around the movement axis (a), axially oriented in a direction away from the first operating element (16), and the mating blocking formation (62) comprises at the release/blocking assembly (50) a mating blocking engagement (68) axially oriented in a direction towards the first operating element (16) and capable of forming blocking engagement and disengagement with the blocking engagement (66) by axial displacement of the release/blocking assembly (50) relative to the second operating element (22).
17. Clutch system comprising a friction clutch (12) having a force store (14) loadable by a pressure fluid operating device (10) according to any of the preceding claims to perform a clutch operation procedure.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102019204349.6 | 2019-03-28 | ||
| DE102019204349.6A DE102019204349A1 (en) | 2019-03-28 | 2019-03-28 | Pressurized fluid actuator assembly for a friction clutch |
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| Publication Number | Publication Date |
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| CN111749994A CN111749994A (en) | 2020-10-09 |
| CN111749994B true CN111749994B (en) | 2024-07-05 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202010235491.3A Active CN111749994B (en) | 2019-03-28 | 2020-03-30 | Pressure fluid operation device for friction clutch |
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| DE (1) | DE102019204349A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE102021200710A1 (en) | 2021-01-27 | 2022-07-28 | Zf Friedrichshafen Ag | Central slave cylinder for the pneumatic actuation of a friction clutch |
| DE102021200711A1 (en) | 2021-01-27 | 2022-07-28 | Zf Friedrichshafen Ag | Central slave cylinder for pneumatic actuation of a friction clutch and reset tool |
| DE102021201096A1 (en) | 2021-02-05 | 2022-08-11 | Zf Friedrichshafen Ag | concentric slave cylinder |
| DE102021201897A1 (en) | 2021-03-01 | 2022-09-01 | Zf Friedrichshafen Ag | concentric slave cylinder |
| WO2023073017A1 (en) * | 2021-10-27 | 2023-05-04 | Zf Friedrichshafen Ag | Central clutch release means for the pneumatic actuation of a friction clutch |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017001410A1 (en) * | 2017-02-14 | 2018-08-16 | Wabco Gmbh | Self-adjusting pneumatic clutch actuator |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE10035491B4 (en) * | 2000-07-21 | 2012-06-21 | Zf Sachs Ag | Pressure plate assembly |
| DE102007031740A1 (en) * | 2006-08-05 | 2008-02-07 | Zf Friedrichshafen Ag | Wear compensation arrangement for operating system of friction coupling, has wear detection arrangement for detecting wear in friction coupling and causing relative movement of force receiving arrangement during occurrence of wear |
| CN106164521B (en) * | 2014-03-25 | 2019-07-09 | 舍弗勒技术股份两合公司 | Compensation adjustment device for a friction clutch |
| US10927902B2 (en) * | 2016-05-04 | 2021-02-23 | Kongsberg Automotive As | Pneumatic clutch actuator |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017001410A1 (en) * | 2017-02-14 | 2018-08-16 | Wabco Gmbh | Self-adjusting pneumatic clutch actuator |
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| DE102019204349A1 (en) | 2020-10-01 |
| CN111749994A (en) | 2020-10-09 |
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