CN111749994A - Pressure fluid operating device for friction clutch - Google Patents
Pressure fluid operating device for friction clutch Download PDFInfo
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- CN111749994A CN111749994A CN202010235491.3A CN202010235491A CN111749994A CN 111749994 A CN111749994 A CN 111749994A CN 202010235491 A CN202010235491 A CN 202010235491A CN 111749994 A CN111749994 A CN 111749994A
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- 239000012530 fluid Substances 0.000 title claims abstract description 66
- 230000000903 blocking effect Effects 0.000 claims abstract description 149
- 238000001514 detection method Methods 0.000 claims abstract description 35
- 230000015572 biosynthetic process Effects 0.000 claims abstract description 29
- 238000006073 displacement reaction Methods 0.000 claims abstract description 26
- 238000005755 formation reaction Methods 0.000 claims description 27
- 238000000034 method Methods 0.000 claims description 13
- 230000008569 process Effects 0.000 claims description 11
- 230000003993 interaction Effects 0.000 claims description 9
- 230000009471 action Effects 0.000 description 9
- 230000000694 effects Effects 0.000 description 5
- 230000013011 mating Effects 0.000 description 5
- 238000007789 sealing Methods 0.000 description 5
- 230000002093 peripheral effect Effects 0.000 description 4
- 230000004323 axial length Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000012535 impurity Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000008093 supporting effect Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 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
- 230000007423 decrease Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000011017 operating method Methods 0.000 description 1
- 230000002040 relaxant effect Effects 0.000 description 1
Images
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
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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
- F16D25/083—Actuators therefor
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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
- F16D25/12—Details not specific to one of the before-mentioned types
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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
- F16D25/12—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
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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
- 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)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Pressure fluid operated device for a friction clutch having a compensating assembly, comprising: a first ramp element which is axially supported in the direction of the displacement axis relative to the second operating element and is pretensioned by a first pretensioning device for rotation about the displacement axis relative to the second operating element, the first ramp element having a first ramp profile, a second ramp element which, together with a rotational decoupling bearing, is displaceable in the direction of the displacement axis, wherein the second ramp element has a second ramp profile and is supported by means of the second ramp profile in the direction of the displacement axis at the first ramp profile, wherein the second ramp element cannot be rotated about the displacement axis relative to the second operating element, 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 displacement axis by the first pretensioning device, a release/blocking assembly which is adjustable between a blocking position and a release position, which has a counter-blocking formation in blocking engagement with a blocking formation at the first operating element in the blocking position, wherein the release/blocking assembly has a detection region which interacts with the first operating element for adjusting the release/blocking assembly from the blocking position into the release position.
Description
Technical Field
The present invention relates to a pressure fluid operated device, for example for use in a truck, for operating a friction clutch.
Background
Such a pressure fluid-operated device usually comprises a cylinder fixedly positioned relative to the vehicle and a piston defining a pressure fluid chamber with the cylinder and being displaceable in the direction of the displacement axis. The piston can be loaded with a force store, for example a spring tongue of a diaphragm spring, via a rotary decoupling bearing in order to carry out a clutch actuation process in this way and method. The installed position of such a diaphragm spring serving as a force store in the engaged state of the friction clutch changes as a function of the wear occurring in the friction clutch, for example, of the friction linings of the clutch disk, since the diaphragm spring is gradually relaxed when moving into the engaged state as a function of increasing wear compared to a state in which there is no wear.
Disclosure of Invention
The object of the present invention is to provide a pressure fluid actuating device for a friction clutch, which allows adaptation to wear-induced changes in the installation position of the force store of the friction clutch in a simple and reliable manner.
According to the invention, said 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 is movable in an operating direction along a movement axis relative to the first operating element 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 rotary decoupling bearing coupled with the second operating element via a compensating assembly for joint movement in the direction of the movement axis,
wherein the compensation assembly includes:
a first ramp element which is axially supported in the direction of the displacement axis relative to the second operating element and is pretensioned by a first pretensioning device for rotation about the displacement axis relative to the second operating element, the first ramp element having a first ramp profile,
a second ramp element which is movable together with the rotary decoupling bearing in the direction of the displacement axis, wherein the second ramp element has a second ramp profile and is supported by means of the second ramp profile in the direction of the displacement axis at the first ramp profile, wherein the second ramp element cannot be rotated relative to the second operating element about the displacement axis, and wherein the axial structural length of the compensating assembly is reduced if a rotation of the first ramp element relative to the second ramp element about the displacement axis is produced by a first prestressing device,
a release/blocking assembly adjustable between a blocking position and a release position, having a counter-blocking formation in blocking engagement with a 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 for adjusting the release/blocking assembly from the blocking position into the release position.
In the arrangement according to the invention of the pressure fluid operated device, an excessive movement of the second operating element relative to the first operating element, caused by wear in the friction clutch, is detected by the interaction of the release/blocking assembly with the first operating element, and the first ramp element is released to perform the readjustment movement only when such an excessive movement is detected. This readjustment movement causes the axial structural length of the compensating assembly comprising the two ramp elements to be reduced and accordingly provides the force store of the friction clutch, i.e. for example a diaphragm spring, with the possibility of further relaxing in the engaged state of the friction clutch to an extent corresponding to the wear occurring. With a pressure fluid actuating device of this type, an improved adjustment and in particular an improved dynamics is achieved during the actuation of the clutch as a function of the minimum dead volume of the pressure fluid chamber.
For uniform operational action it is proposed: 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 annular embodiment of the two actuating elements, it is advantageous if the first ramp element is of annular design and has at least one, preferably a plurality of, first ramp profiles extending in the circumferential direction, and the second ramp element is of annular design and has at least one, preferably a plurality of, second ramp profiles 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 movement axis, wherein the first pretensioning spring is supported with its one end region relative to the second actuating element and with its other end region relative to the first ramp element.
In order to provide a displacement coupling between the second ramp element and the rotary decoupling bearing and at the same time also to 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 to the second operating element in a rotationally fixed manner and in a displaceable manner relative thereto in the direction of the displacement axis.
The second operating element can be pretensioned in the direction of the displacement axis in the operating direction relative to the first operating element by means of a second pretensioning device. The second prestressing device also counteracts the slack force accumulator, so that a force balance is established in the engaged state of the friction clutch.
For a defined interaction between the release/blocking arrangement and the first ramp element, it is proposed that the release/blocking arrangement 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 a third pretensioning device for pretensioning the release/blocking element into its blocking position relative to the second operating element.
The spatial separation of the blocking/releasing function on the one hand and the detection of an excessive movement of the second operating element relative to the first operating element on the other hand can be achieved in that the release/blocking element has a release/blocking section which is arranged at an axial side of the second operating element facing away from the first operating element and has a counter-blocking formation and a detection section of a detection region which extends through the second operating element and which protrudes at an axial side of the second operating element facing the first operating element for the detection interaction with the first operating element.
In order to positively bias the release/blocking element into a position in which it is already present for detecting an excessive movement of the second operating element, it is proposed that the third biasing device comprises a biasing spring which is supported relative to the detection section and the second operating element and biases the detection section in the direction of the first operating element.
In an alternative embodiment, in which the release/blocking arrangement is provided substantially separately from the second operating element, the release/blocking arrangement can comprise a release/blocking element having an annular release/blocking element body, which is arranged at an axial side of the second operating element facing away from the first operating element, wherein the release/blocking element is provided with a third prestressing device for prestressing the release/blocking element body in a release direction opposite to the operating direction toward the second operating element.
For the release/blocking interaction with the first ramp element, a release/blocking region with a counter-blocking formation can be provided at the release/blocking element body. Furthermore, a detection region is provided at the release/blocking element body which is in detection interaction with the first operating element in order to detect an excessive axial movement of the second operating element due to an excessive wear of the friction clutch.
In order to provide a simple design, 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 counter-blocking formation, and that the detection region comprises a detection section which protrudes radially outward from the annular release/blocking element body for the purpose of detecting an interaction with the first operating element.
A stable blocking action can be achieved in that the blocking formation at the first ramp element comprises a blocking engagement at least partly annularly around the movement axis, axially oriented in a direction away from the first operating element, and the counter-blocking formation at the release/blocking assembly comprises a counter-blocking engagement, axially oriented in a direction towards the first operating element and capable of forming a blocking engagement and a blocking disengagement 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 accumulator which can be loaded by a pressure fluid operating device according to one of the preceding claims for carrying out a clutch operating process.
Drawings
The present invention is described in detail below with reference to the attached drawings. The figures 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-operated device of fig. 1, taken along the line II-II in fig. 1;
figure 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 of a friction clutch with little wear;
FIG. 6 shows the pressure fluid operated device of FIG. 1 in a state of the friction clutch where there is a strong wear to compensate for;
fig. 7 shows a longitudinal section through an alternative embodiment of a pressure fluid actuating device for a friction clutch;
fig. 8 shows a cross-sectional view of the pressure fluid operated device of fig. 7 along the line VIII-VIII in fig. 7;
fig. 9 shows a perspective view of a part of the pressure fluid operated device 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 in accordance with a force accumulator 14 which is provided in this case and is designed, for example, as a diaphragm spring.
The pressure fluid actuating device 10 comprises a first actuating element 16, which is provided as an annular cylinder and which surrounds the displacement axis a annularly by means of its substantially annular configuration. The second operating member 22, which is engaged substantially between the inner peripheral wall portion 18 and the outer peripheral wall portion 20 of the first operating member 16, provides an annular piston annularly about the axis of movement a. The second operating element 22 is movably guided in the direction of the movement axis a in fluid-tight manner relative to the inner and outer circumferential wall portions 18, 20 of the first operating element 16 via a plurality of sealing/guiding elements 24.
A pressure fluid chamber 26, which is closed fluid-tightly by means of different sealing/guiding elements 24, is formed between the first operating element 16 and the second operating element 22. A pressure fluid, for example compressed air, can be introduced into the pressure fluid chamber 26 via a not shown interface, in order to apply or displace a force action to the second operating element 22 in the operating direction B relative to the first operating element 16 by establishing a fluid pressure in the pressure fluid chamber 26. When the second operating element 22 is moved in the displacement direction B, it is loaded via a rotary decoupling bearing 28, which is held, for example, at the second operating element 22, with a spring tongue, which engages radially inside, for example radially inside, a radially inner region of the force accumulator 14, which is embodied, for example, as a diaphragm spring, in order to move or pivot it in order to carry out a disengagement process in the displacement direction B and in this way 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 relative to the rotary decoupling bearing 28 by means of a compensating assembly 30. The compensating assembly 30 comprises a first ramp element 32 annularly about the axis of movement a and a second ramp element 34 connected thereto, also annularly about the axis of movement a. The first ramp element 32 has a first ramp profile 36 with a plurality of ramp surfaces which follow one another in the circumferential direction. Correspondingly, the second ramp element 36 has a second ramp profile 38 with a plurality of ramp surfaces which follow one another in the circumferential direction. The ramp surface of the first ramp formation 36 abuts the ramp surface of the second ramp formation 38. The ramp elements 32, 34, whose ramp surfaces or ramp profiles 36, 38 bear against one another, provide this supporting property of the compensating assembly 30, so that a relative rotation of the two ramp elements 32, 34 relative to one another causes a change in the axial structural length of the compensating assembly 30 as a result of the ramp surfaces of the ramp profiles 36, 38 sliding on one another.
The second operating element 22 is held in a rotationally fixed and axially displaceable manner relative to the second ramp element 34 by means of the rotation-preventing formations 40. The anti-rotation formations 40 comprise, for example, in the second ramp element 34 a groove extending in the direction of the movement axis a and at the second operating element 22 a guide projection engaging into the groove and extending longitudinally in the direction of the movement axis a. 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 brought about.
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 helical 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 so as to rotate relative to the second actuating element 22.
A second pretensioning device 46 acts between the first actuating element 16 and the second actuating element 22, which provides a force action that pretensions the second actuating element 22 relative to the first actuating element 16 in the actuating direction B against the loading action of the force store 14. The second prestressing spring 48 here 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 member 22 and substantially blocks the first ramp member 32 from rotating relative to the second operating member 22. The release/blocking assembly 50 comprises a release/blocking element 52 shown in fig. 3, which is adjustably guided in the direction of the movement axis a at the second operating element 32. For this purpose, the release/blocking element 52 can comprise a plurality of, for example two, guide projections 56 which are arranged at a distance from one another in the circumferential direction and engage in corresponding guide recesses in the second operating element 22. By means of the guide projection 56 engaging in 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 displacement axis a.
A release/blocking section 60 of the release/blocking element 52 is provided on an axial side 58 of the second operating element 22 facing away from the first operating element 16. In connection with a counter-stop formation 62 provided at the release/blocking section 60, a stop 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 formed completely and around the displacement axis a at the second operating element 22, which is oriented axially in the direction away from the first operating element 16, i.e. has teeth extending in this direction away from the first operating element 16, which have a tooth gap formed between them in the circumferential direction. In a corresponding manner to this blocking engagement 66, a counter-blocking engagement 68 is provided at the release/blocking section 60, which provides the counter-blocking formation 62. The counter-blocking toothing has a plurality of teeth which follow one another in the circumferential direction and extend axially toward the first operating element 16, with tooth gaps formed between them in the circumferential direction. The mating stop engagement portion 68 can be brought into engagement with the stop engagement portion by axial movement onto the stop engagement portion 66. The blocking engagement portion 66 and the mating blocking engagement portion 68 can be disengaged by 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 an axial side of the second operating element 22 facing the first operating element 16 towards 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 from the pressure fluid in 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 prestressing device 74 comprises a third prestressing spring 76 which is formed in the form of a diaphragm spring, surrounds the detection section 72 and is supported relative to said detection section and the second actuating element 22. By means of this third biasing spring, the release/blocking element 52 is biased with its release/blocking section 60 in the direction of the second operating element 22 and simultaneously with its counter-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-operated device 10, in which it is used, for example, in conjunction with a new or non-worn friction clutch 12 and the friction clutch 12 is in an engaged state. This means that the force accumulator 14, via the rotary decoupling bearing 28 and the compensating arrangement 30, displaces or pretensions the second actuating element 22 into a basic position relative to the first actuating element 16, in which the forces between the second pretensioning spring 48 and the force accumulator 14 are balanced and the pressure fluid chamber 26 provides a dead volume which allows a slight movement of the second actuating element 22 beyond the basic position onto the first actuating element 16 in a release direction F opposite the actuating direction B. The second operating element 22 can be moved further beyond the basic positioning in the release direction F onto the first operating element at least as far as the axial engagement depth of the blocking engagement 66 with the counter-blocking engagement 68, which can be in the range of approximately 3 mm.
To carry out the operating process, a pressure fluid, for example compressed air, is introduced into the pressure fluid chamber 26. Due to the resulting fluid pressure, a force is exerted on the second operating element 22, which presses it to the left in the view of fig. 3. Via the compensating assembly 30, the rotary decoupling bearing 28 is moved axially in the operating direction B, so that it acts on a radially inner region of the force store 14, i.e. on the radially inner end of the spring tongue, for example of a diaphragm spring, and thus disengages the friction clutch 12. In order to engage the friction clutch, the fluid pressure in the pressure fluid chamber 26 is released, so that, due to the relaxed force accumulator 14 and the pretensioning action of the second pretensioning spring 48, the second operating element 22 is moved back into its basic position shown in fig. 1 relative to the first operating element 16, in which the already mentioned dead volume is present, i.e. the axial distance between the two operating elements 16, 22 is also present.
The first ramp element 32 is pretensioned by its associated first pretensioning device 42 to rotate in the circumferential direction relative to the second operating element 22. Because the mating blocking engagement portion 68 of the release/blocking member 52 is brought into engagement with the blocking engagement portion 66 at the first ramp member 32, the first ramp member 32 cannot rotate relative to the second operating member. Furthermore, the slope of the two ramp profiles 36, 38 is set such that they are self-locking and the axial forces acting when performing the operating process do not lead to a forced rotation of the two ramp elements 32, 34 relative to one another either. The self-locking effect can also be intensified in that impurities can enter the spatial region which contains the two ramp profiles 36, 38, which can also place the impurities between the ramp surfaces which bear against one another, and can thus cause intensified friction.
If wear occurs in the friction clutch 12, this causes the force accumulator 14 to relax further during engagement than if there was 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 therefore the second operating element 22 moves closer beyond the base position toward the first operating element 16. This is basically possible because the above-mentioned dead volume of the pressure fluid chamber 26 is provided in the basic position of the second operating element 22. 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 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 release/blocking element 52, despite being axially displaced relative to the second operating element 22, also comes into engagement with the counterpart blocking engagement 68 with the blocking engagement 66. 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 carried out 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 is relaxed to such an extent that it moves the second operating element 22 still further axially beyond the basic position via the rotary decoupling bearing 28 and the compensating assembly 30 when the friction clutch 12 is engaged. This state is shown in fig. 6. The detection section 72 in turn abuts against the first operating element 16 and, by excessive axial displacement of the second operating element 22 in the release direction F beyond the basic position, the mating blocking engagement 68 is no longer in engagement with the blocking engagement 66. From now on, the pretension generated by the first pretension spring 44 is sufficient to rotate the first ramp element 32 relative to the second operating element 22 about the movement axis a. As the ramp profiles 36, 38 bear against one another and slide relative to one another in this rotational movement, the axial overall length of the compensating assembly 30 is reduced in this rotational movement of the first ramp element 32.
Since the second ramp element 34 is held in a defined axial position by the force store 14, the second operating element 32 is moved axially away from the first operating element under the pretensioning action of the second pretensioning spring 48 when the axial structural length of the compensating assembly 30 is reduced. The first ramp element 32, which is under axial load of the second operating element 22, is rotated until the blocking engagement 66 and the counter-blocking engagement 68 again come into engagement with one another as the axial structural length of the compensating assembly 30 decreases. This can be the case, for example, when the teeth of the blocking engagement 66 and the counter-blocking engagement 68 have rotated by one tooth relative to one another in the course of the rotational movement of the first ramp element 32. In the case of a subsequent engagement of the blocking engagement 66 and the counter-blocking engagement 68 with one another, a force equilibrium is established again between the pretensioning force of the relaxed force accumulator 14 acting essentially in the release direction F in the engaged state of the friction clutch 12 and the pretensioning force of the second pretensioning spring 48 acting in the operating direction B. The second control element 22, in turn, essentially executes the wear compensation process in the manner and method described above again in its basic position relative to the first control element 16, in which case the operating process can then be executed again taking into account the dead volume of the pressure fluid chamber 26 that is present for the subsequently compensated state, and then, when such wear occurs again in the friction clutch 12, the second control element 22 reaches the state shown in fig. 6 in the engaged state of the friction clutch 12.
If, for example, a completely worn clutch disk is replaced in the friction clutch 12 or a new friction clutch is inserted into the vehicle, the hydraulic fluid actuating device 10 is again brought into a state which is associated with the new state of the friction clutch. For this purpose, after the blocking action of the release/blocking arrangement 50 has been released, the first ramp element 32 must be rotated back against the biasing action of the first biasing spring 44 in order to thereby increase the axial overall length of the compensating arrangement 30 again and to make it possible for the friction clutch to be operated subsequently, that is to say that a rotation of the first ramp element 32 can occur again to a degree corresponding to wear and with this a reduction in the axial overall length of the compensating arrangement 30 can occur.
In order to ensure that the pressure fluid actuating device 10 can be operated in emergency operation and the friction clutch 12 can be operated as before in the event of a failure of the compensating arrangement 30, for example in the event of complete collapse of the axially mutually supporting ramp elements 32, 34, the second operating element 22 can be maximally displaced at the inner and outer circumferential wall 18, 20 of the first operating element 16 to such an extent that complete disengagement of the friction clutch 16 is ensured in this case.
With reference to fig. 7 to 9, an alternative embodiment of the pressure fluid actuating device 10 is described below. This embodiment corresponds in a basic aspect to the previously described configuration, in particular also in terms of the transmission of the operating force via the two ramp elements 32, 34 which bear against one another by means of the respective ramp profiles 36, 38, so that reference can be made to the above-described embodiment for this purpose.
The basic structural difference is that the release/blocking assembly 50 is structurally decoupled from the second operating element 22. The release/blocking assembly 50 includes a release/blocking element 52 formed by an annular release/blocking element body 78. The release/blocking element body 78 surrounds the displacement axis a in a ring-like manner and is also situated substantially radially outside the ramp elements 32, 34 or outside the ramp profiles 36, 38 thereof or radially inside the outer circumferential wall 20 of the first operating element 16. The detection region 71 is integrally provided at the release/blocking element body 78 and is provided by a flange-shaped detection section 72 which projects radially outward and which preferably radially overlaps an axial end of the outer circumferential wall 20 of the first operating element 16 over the entire circumference about the movement axis a. By means of a third prestressing spring 76 of the third prestressing device 74, which is embodied, for example, as a helical compression spring, and which surrounds the displacement axis a, the release/blocking element body 78 is prestressed in the release direction F in the direction of the first ramp element 32, the second operating element 22 or also the first operating element 16. In this case, the third pretensioned spring 76 is supported, for example, on the second ramp element 34. By this pretensioning effect, the detection section 72 is essentially pretensioned against the outer circumferential wall 20 of the first operating element 16.
A release/blocking region 80 is provided in the circumferential region at the region of the radially inward engagement 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 fixed by riveting at the release/blocking element body 78. At this release/blocking part 82 the counter-blocking formations 62 with their counter-blocking engagement 68 are formed.
At least in the circumferential region of the first ramp element 32 which interacts with the release/blocking region 80, the blocking formation 64 is provided with its blocking engagement 66. In this embodiment too, the blocking toothing 66 is formed into a counter-blocking toothing 68 with teeth projecting in the axial direction, so that said 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, in the engaged friction clutch 12, for example, in which there is no wear, the second operating element 22 is in its basic position relative to the first operating element 16. The second pretensioning spring 48 of the second pretensioning device 46, which is embodied in this embodiment as a wave spring or the like, for example, holds the second operating element 22 at a distance from the first operating element 16, so that the second operating element 22 can be moved substantially in the release direction F beyond the base position toward the first operating element 16. By the pretensioning action of the second pretensioning device 46 and the other of the third pretensioning devices 74, the blocking engagement 66 is held in engagement with the counter-blocking engagement 68, so that the first ramp element 32, which is under the pretensioning of the first pretensioning device 42, cannot rotate, and therefore a defined axial relative positioning of the first actuating element 22 with respect to the rotationally decoupled bearing 28 is predetermined and the friction clutch 12 can be actuated in a correspondingly defined manner by introducing pressure fluid into the pressure fluid chamber 26.
If wear occurs in the friction clutch 12, this causes the force accumulator 14 to be able to relax further when it is engaged, so that its radially inner region moves further in the release direction F toward the first operating element 16. By the force action of the force accumulator 14, the second actuating element 23 and the release/blocking element 52 pretensioned by the third pretensioning device 74 are displaced in the release direction F until the detection section comes into contact with the outer circumferential wall 20 when the base position 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 in the direction of the first actuating element 16 beyond the basic position against the biasing effect of the second biasing means 46. The release/blocking element 52 cannot follow this movement. Due to 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 for rotation about the rotational axis a and rotates relative to the second ramp element 34 under the pretensioning effect of the first pretensioning device 42. Here, the axial length of the compensating assembly 30 comprising the two ramp elements 32, 34 is reduced. The second actuating element 22, which is acted upon by the second prestressing 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 in engagement with one another, so that after wear compensation the two ramp elements 32, 34 are again secured against relative rotation by the release/blocking assembly 50 and can again perform the operating procedure with a reduction in the axial length of the compensating assembly 30.
The dead volume reserved in the pressure fluid actuating device of the pressure fluid chamber, which is formed according to the invention, for carrying out the compensation process is relatively small and does not substantially impair the accuracy of the 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 behavior can be ensured even over the operating life.
List of reference numerals
10 pressure fluid operation device
12 friction clutch
14-force accumulator
16 first operating element
18 inner peripheral wall portion
20 outer peripheral wall portion
22 second operating element
24 sealing/guiding element
26 pressure fluid chamber
28 rotating decoupling bearing
30 compensating assembly
32 first ramp element
34 second ramp element
36 first slope forming part
38 second ramp forming portion
40 anti-rotation forming part
42 first pretensioning device
44 first pre-tightening spring
46 second pretensioning device
48 second pre-tightening spring
50 Release/stop Assembly
56 Release/blocking element
58 axial side
60 Release/Barrier section
62 mating stop formations
64 stop forming part
66 stop engagement
68 mate stop engagement
70 axial side
71 detection area
72 detection section
73 opening
74 third pretensioning device
75 sealing element
76 third preloaded spring
78 Release/blocking element body
80 release/blocking area
82 Release/blocking Member
Axis of movement A
B direction of operation
Direction of C release
Claims (14)
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 along a movement axis (A) in an operating direction (B) relative to the first operating element (16) by introducing a pressure fluid into the pressure fluid chamber (26),
-a rotational decoupling bearing (28) coupled with the second operating element (22) via a compensating assembly (30) for joint movement in the direction of the movement axis (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 movement axis (A) and is pretensioned by a first pretensioning device (42) for rotation about the movement axis (A) relative to the second operating element (22), the first ramp element having a first ramp profile (36),
-a second ramp element (34) which, together with the rotational decoupling bearing (28), is movable in the direction of the movement axis (A), wherein the second ramp element (34) has a second ramp profile (38) and is supported by means of the second ramp profile (38) in the direction of the movement axis (A) at the first ramp profile (36), wherein the second ramp element (34) cannot be rotated relative to the second operating element (22) about the movement 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 movement 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.
2. A pressure fluid operating device according to claim 1, characterized in that the first operating element (16) is a cylinder, preferably an annular cylinder, and the second operating element (22) is a piston, preferably an annular piston.
3. A pressure fluid operating device according to claim 1 or 2, characterized in that the first ramp element (32) is ring-shaped and has at least one, preferably a plurality of first ramp formations (36) extending in the circumferential direction, and the second ramp element (34) is ring-shaped and has at least one, preferably a plurality of second ramp formations (38) extending in the circumferential direction.
4. A pressure fluid operating device according to any one of the preceding claims, characterized in that the first pretensioning means (42) comprises a first pretensioning spring (44) extending in a circumferential direction around 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).
5. A pressure fluid operating device according to any one of the preceding claims, characterized in that the second ramp element (34) is coupled non-rotatably and relative movably to the second operating element (22) in the direction of the movement axis (a).
6. A pressure fluid operating device according to any one of the preceding claims, characterized in that the second operating element (22) is pretensioned in the operating direction (B) in the direction of the movement axis (a) relative to the first operating element (16) by means of a second pretensioning device (46).
7. A pressure fluid operating device according to any one of the preceding claims, 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 a third pretensioning means (74) for pretensioning the release/blocking element (52) into its blocking position relative to the second operating element (22).
8. A pressure fluid operating device according to claim 7, characterized in that the release/blocking element (52) has a release/blocking section (60) which is provided at an axial side (58) of the second operating element (22) facing away from the first operating element (16) and which has the counter-blocking formation (62) and a detection section (72) of the detection region (71), which extends through the second operating element (22) and which protrudes at an axial side (70) of the second operating element (22) facing toward the first operating element (16) for a detection interaction with the first operating element (16).
9. A pressure fluid operating device according to claim 8, characterized in that the third pretensioning means (74) comprises a pretension 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 of the first operating element (16).
10. A pressure fluid operating device according to any one of claims 1 to 6, characterized in that the release/blocking assembly (50) comprises a release/blocking element (52) having 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 a third pretensioning device (74) for pretensioning the release/blocking element body (80) towards the second operating element (22) in a release direction (F) opposite to the operating direction (B).
11. A pressure fluid operating device according to claim 10, characterized in that a release/blocking area (80) with the counter-blocking formation (62) and a detection area (71) in detecting interaction with the first operating element (16) are provided at the release/blocking element body (78).
12. A pressure fluid operating device according to claim 10, 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 counter-blocking formation (62), and 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 operating element (16).
13. A pressure fluid operating device according to any one of the preceding claims, wherein the blocking formation (64) comprises, at the first ramp element (32), a blocking engagement portion (66) at least partly annularly about the movement axis (a) oriented axially in a direction away from the first operating element (16), and the counter-blocking formation (62) comprises, at the release/blocking assembly (50), a counter-blocking engagement portion (68) oriented axially in a direction towards the first operating element (16) and capable of coming into and out of blocking engagement with the blocking engagement portion (66) by axial displacement of the release/blocking assembly (50) relative to the second operating element (22).
14. A clutch system comprising a friction clutch (12) having a force accumulator (14) which can be loaded by a pressure fluid operating device (10) according to one of the preceding claims for carrying out a clutch operating process.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102019204349.6A DE102019204349A1 (en) | 2019-03-28 | 2019-03-28 | Pressurized fluid actuator assembly for a friction clutch |
| DE102019204349.6 | 2019-03-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111749994A true CN111749994A (en) | 2020-10-09 |
| CN111749994B CN111749994B (en) | 2024-07-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010235491.3A Active CN111749994B (en) | 2019-03-28 | 2020-03-30 | Pressure fluid operation device for friction clutch |
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| Country | Link |
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| CN (1) | CN111749994B (en) |
| DE (1) | DE102019204349A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102021200711A1 (en) | 2021-01-27 | 2022-07-28 | Zf Friedrichshafen Ag | Central slave cylinder for pneumatic actuation of a friction clutch and reset tool |
| DE102021200710A1 (en) | 2021-01-27 | 2022-07-28 | Zf Friedrichshafen Ag | Central slave cylinder for the pneumatic actuation of a friction clutch |
| 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 (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| DE10035491B4 (en) * | 2000-07-21 | 2012-06-21 | Zf Sachs Ag | Pressure plate assembly |
| CN106164521A (en) * | 2014-03-25 | 2016-11-23 | 舍弗勒技术股份两合公司 | Compensation adjustment device for a friction clutch |
| WO2017191506A2 (en) * | 2016-05-04 | 2017-11-09 | Kongsberg Automotive As | Pneumatic clutch actuator |
| DE102017001410A1 (en) * | 2017-02-14 | 2018-08-16 | Wabco Gmbh | Self-adjusting pneumatic clutch actuator |
-
2019
- 2019-03-28 DE DE102019204349.6A patent/DE102019204349A1/en active Pending
-
2020
- 2020-03-30 CN CN202010235491.3A patent/CN111749994B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN106164521A (en) * | 2014-03-25 | 2016-11-23 | 舍弗勒技术股份两合公司 | Compensation adjustment device for a friction clutch |
| WO2017191506A2 (en) * | 2016-05-04 | 2017-11-09 | Kongsberg Automotive As | Pneumatic clutch actuator |
| DE102017001410A1 (en) * | 2017-02-14 | 2018-08-16 | Wabco Gmbh | Self-adjusting pneumatic clutch actuator |
| WO2018149616A1 (en) * | 2017-02-14 | 2018-08-23 | Wabco Europe Bvba | Self-adjusting pneumatic clutch actuator |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102019204349A1 (en) | 2020-10-01 |
| CN111749994B (en) | 2024-07-05 |
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