阅读说明：本技术 具有用于离合器弹簧的定向元件的离合器支承装置 (Clutch support device with orientation element for clutch spring ) 是由 M·圣蒂芙 J-B·马雷斯科 F·阿米奥 J·迈拉尔 于 2018-02-05 设计创作，主要内容包括：本发明涉及一种用于动力闭合地连接和分离驱动总成与辅助总成的机动车离合器(10),所述机动车离合器具有支承装置(20,20a),用于借助接触面(21,21a)将轴向力传递到至少一个盘形弹簧(30)上,以便打开离合器,其中,所述盘形弹簧(30)具有在径向上朝内伸出的弹簧舌片(31),所述弹簧舌片在彼此之间具有槽口(32),其中,所述支承装置(20,20a)为了在径向上不能移动地以及抗扭转地固定所述盘形弹簧(30)而具有榫头(22,22a),所述榫头从所述接触面(21,21a)沿所述机动车离合器(10)的轴向方向延伸并且设置为用于被所述弹簧舌片(31)之间的槽口(32)接收并且与所述槽口处于嵌合中。(The invention relates to a motor vehicle clutch (10) for the dynamic closed connection and disconnection of a drive assembly and an auxiliary assembly, having a bearing device (20, 20a), for transmitting an axial force to the at least one disk spring (30) by means of the contact surfaces (21,21a) in order to open the clutch, wherein the cup spring (30) has spring tongues (31) which project radially inwards and which have notches (32) between one another, wherein the bearing device (20, 20a) has a pin (22, 22a) for the radially immovable and rotationally fixed fixation of the disk spring (30), the pin extends from the contact surface (21,21a) in the axial direction of the motor vehicle clutch (10) and is provided for being received by and in engagement with a notch (32) between the spring tongues (31).)

1. A motor vehicle clutch (10) for the dynamic closed connection and disconnection of a drive assembly and an auxiliary assembly, having a bearing device (20, 20a), for transmitting an axial force to at least one disk spring (30) by means of a contact surface (21,21a) for actuating the clutch, wherein the cup spring (30) has spring tongues (31) which project radially inwards and which have notches (32) between one another, characterized in that the bearing (20, 20a) has a pin (22, 22a) for the radially immovable and rotationally fixed fixation of the disk spring (30), the pin extends from the contact surface (21,21a) in the axial direction of the motor vehicle clutch (10) and is provided for being received by the notch (32) between the spring tongues (31) and in engagement therewith.

2. The motor vehicle clutch (10) according to the preceding claim, wherein the bearing arrangement (20a) has a flange (23a) extending in the axial direction on its inner circumference, which flange extends through an inner opening (34) of the cup spring (30).

3. The motor vehicle clutch (10) according to one of the preceding claims, further having a hub (13), wherein the motor vehicle clutch (10) is configured such that the hub (13) acts as a stop for the bearing arrangement (20, 20a) in order to open the motor vehicle clutch (10) when the bearing arrangement (20, 20a) is moved axially.

4. The motor vehicle clutch (10) according to any one of the preceding claims, wherein the powertrain is an internal combustion engine, wherein the auxiliary assembly is a compressor.

5. A bearing arrangement (20, 20a) for actuating a clutch (10) of a motor vehicle, the bearing (20, 20a) is provided for transmitting an axial force to the at least one cup spring (30) by means of the contact surface (21,21a), wherein the cup spring (30) has spring tongues (31) which project radially inwards and which have notches (32) between one another, characterized in that the bearing (20, 20a) has a pin (22, 22a) for the radially immovable and rotationally fixed fixation of the disk spring (30), the pin extends from the contact surface (21,21a) in the axial direction of the motor vehicle clutch (10) and is provided for being received by the notch (32) between the spring tongues (31) and in engagement therewith.

6. The bearing arrangement (20, 20a) according to the preceding claim, wherein the bearing arrangement (20a) has a flange (23a) extending in the axial direction on its inner circumference, which flange is provided for extending through an inner opening (34) of the cup spring (30).

7. Bearing arrangement (20, 20a) according to claim 5 or 6, wherein the bearing arrangement (20, 20a) is of the ball bearing or roller bearing type.

8. Disc spring (30) for use in a motor vehicle clutch (10), wherein the disc spring (30) has spring tongues (31) which project radially inward and which have notches (32) between one another, characterized in that the notches (32) are provided for engagement with a pin (22, 22a) of a bearing device (20, 20a) which extends in the axial direction of the motor vehicle clutch (10) in such a way that the disc spring (30) is fixed radially immovably and rotationally fixed relative to the bearing device (20, 20 a).

Technical Field

The invention relates to a clutch bearing arrangement having an alignment element for a clutch spring, which is embodied as a disk spring, and to a clutch for a motor vehicle auxiliary assembly having such a clutch bearing arrangement. Such a clutch is referred to below as a motor vehicle clutch.

Background

Clutches are provided in motor vehicles for closing and separating the power between the drive train and the transmission when required. In addition, clutches in motor vehicles are also provided for closing and separating the power between the drive assembly and the auxiliary assembly when required. Such an auxiliary assembly can be, for example, an air compressor or compressor. In particular commercial vehicles such as trucks or buses are often equipped with pneumatic brake systems which require compressed air for their operation. Such vehicles have a pressure accumulator in addition to the compressor. If such a pneumatic accumulator is charged with compressed air during operation of the vehicle and a predetermined nominal internal pressure exists, the compressor is no longer temporarily required to be driven by the drive assembly until the target internal pressure is again undershot as a result of the operation of the air consumer. Rather, driving the compressor at this point in time is even undesirable, since energy is additionally consumed by the unnecessary drive.

Such a clutch arranged between the drive train and the compressor is typically embodied as a plate clutch and has a plurality of friction plates. The friction disks are pressed against one another by means of one or more disk springs in order to achieve the closed (power-closed) clutch state. To open the clutch, a counter force is built up on the disk spring by means of a pneumatic actuator, so that the friction disk is relieved of the spring force of the disk spring.

The technical problem here is that the position of the cup spring within the clutch must be fixed in order to reduce wear between the cup spring and the component which is in contact with the cup spring. Rather, the position of the cup spring relative to the rest of the clutch structure, in particular relative to the clutch hub, must be fixed. The cup spring is thus not rotatable and not radially displaceable relative to the clutch hub in the mounted state.

In EP 1995482 a1, a rotationally fixed connection between the clutch hub and the disk spring is thus achieved: the clutch hub has slits in the axial direction at a plurality of locations, and the disc spring is fitted into the slits. Furthermore, the disk spring is centered on its outer diameter radially on the hub securing device, so that a movement of the disk spring in the radial direction of the hub is not possible. In this design, high tolerance values must be provided for radial centering of the disk springs, since the centering is not performed directly on the hub, but rather on the hub safeguard (or on the clutch housing). As a result, the position of the individual springs relative to one another and relative to the bearing device cannot be determined precisely, so that increased wear occurs on the finger and on the springs. A further disadvantage of this design is that during actuation of the clutch, relative movements between the bearing and the spring can occur, which also lead to wear.

In EP 2123929B 1, only one cup spring is used in order to avoid wear which would otherwise occur between the several cup springs relative to one another. In order to achieve a rotationally fixed centering between the output element 32 and the disk spring, the output element 32 has three slotted recesses 114, in each of which a spring tongue 112 (see fig. 4 of EP 2123929B 1) is inserted, which is longer in the radial direction than the remaining spring tongues. The centering or fixing of the cup spring in the radial direction is effected on its outer circumference. In this design, the spring is centered on the hub and therefore with a small tolerance value. However, here too, a relative movement between the bearing device and the spring can occur during actuation of the clutch, which increases the wear.

Disclosure of Invention

At least one of the above problems is solved by a motor vehicle clutch, a bearing arrangement and a cup spring according to the appended claims. Advantageous embodiments are the subject matter of the dependent claims.

By configuring the motor vehicle clutch, the bearing device and the disk spring according to the invention, an orientation/centering of the disk spring within the motor vehicle clutch is achieved, by means of which an improved wear behavior of the disk spring itself and of parts in contact with the disk spring can be achieved. Due to the configuration according to the invention, the disk springs can rotate neither relative to each other nor relative to the bearing about the clutch axis. As a result, the wear-sensitive spring tongues of the disk spring, in particular, are not damaged. In particular, wear of the spring tongue and the contact surface between the spring tongue and the bearing is reduced, since the possibility of movement between the spring tongue and the bearing is minimized. Furthermore, wear between the radially outer region of the belleville spring and the hub is minimized.

According to an advantageous embodiment, the stroke of the bearing device for opening the motor vehicle clutch is achieved by direct contact (axial stop) between the bearing device (in particular the pin of the bearing device) and the axially immovable hub, thereby limiting the maximum axial spring stroke of the disk spring. Therefore, the disc spring is not damaged. Furthermore, the control of the actuation of the clutch is simplified thereby.

According to an advantageous embodiment, the bearing device has a flange extending in the axial direction of the clutch, which flange is arranged radially between the hub and the disk spring. This prevents frictional contact between the radially inner edge of the disk spring and the hub, thereby reducing wear.

Drawings

A number of configurations of the present invention are set forth below with reference to the accompanying drawings.

Figure 1 shows a motor vehicle clutch according to the invention in three sectional views in the closed clutch state,

figure 2 shows the motor vehicle clutch according to the invention in three sectional views in the open clutch state,

figure 3 shows a motor vehicle clutch according to the invention in a cut-away detail view,

figure 4 shows several embodiments of the inventive support device with the inventive cup spring,

figure 5a shows an isometric view of a support device of the invention,

figure 5b shows an isometric view of a support device of the invention with lugs,

fig. 5c shows a belleville spring of the present invention.

Detailed Description

Fig. 1 shows three sectional views of a motor vehicle clutch 10 according to the invention for the power-closed connection of a main assembly to a compressor. The motor vehicle clutch 10 is shown in the closed clutch state. The closed clutch state means that at this point in time a power-closed connection is established between the main assembly and the compressor via the vehicle clutch. In this case, the friction disk pack 17 of the motor vehicle clutch 10 is pushed together, and the individual friction disks move as a unit. The sections a-a and C-C shown below are indicated in the sectional view B-B shown above. Fig. 1 shows an assembled state of a motor vehicle clutch 10, wherein three cup springs 30 and a bearing arrangement 20 are shown in the assembled state. A belleville spring 30 having a circular outer circumference is shown in cross-section B-B. The cup spring 30 has spring tongues 31 arranged symmetrically on its inner circumference. A distance is formed between the individual spring tongues 31. This distance is formed either by the intermediate spaces 33 between the spring tongues 31 or by the notches 32 between the spring tongues 31. The geometry of the slot 32 is matched to the geometry of the pin 22 of the bearing mechanism 20. Between the sides of each slot 32, one of the tenons 22 is in engagement with the disc spring 30. The contact surface 21 of the support device 10, which is partially concealed by the cup spring 30, can be seen through the intermediate space 33. Further, the hub 13 is shown in the center of the sectional view B-B.

The principle functional mode of the motor vehicle clutch 10 is shown in the sectional views C-C. The section C-C extends through the two spring tongues 31. The spring force exerted by the cup spring 30 on the bearing means 20 is via a surface contact between the radially inner region of the cup spring 30 (more precisely the radially inner region of the spring tongue 31) and the contact surface 21 of the bearing means 20. Furthermore, the cup spring 30 exerts a spring force on the hub 13 via surface contact between its radially outer regions. These spring forces in this case cause the closed clutch state, since the cup spring 30 exerts a spring force on the separating ring 16, which is fixedly connected to the axially movable clutch housing 15, in the region between its radially outer region and its radially inner region. The outer friction plates of the clutch, which are part of the friction plate pack 17, are fixed to the axially displaceable clutch housing 15. The spring force of the cup spring 30 presses the release ring 16 together with the clutch housing 15 (with respect to the sectional view a-a) to the right, whereby the friction plate pack 17 is also pressed to the right against the axially immovable hub 13. Thus, the motor vehicle clutch 10 is in the closed clutch state.

The cup spring 30 is centered on the bearing means 20 by arranging more than two pins 22, in the embodiment shown here four pins 22, on the bearing means 20. Thus, the section B-B shows the centering of the cup spring 30 on the bearing 20, wherein the section C-C shows the pretension between the bearing 20, the hub 13 and the separating ring 16 caused by the spring force.

The section a-a extends through both tenons 22. In this case, the radially inner region of the disk spring 30 does not touch the outer circumferential surface of the pin 22. Furthermore, a pretensioning spring 14 arranged inside the pressure chamber 11 is shown in the section plane a-a. In order to move the bearing mechanism 20, i.e. to actuate the clutch, the pressure chamber 11 is charged with compressed air. The fluid pressure inside the pressure chamber 11 acts here on the piston 12, which is located in a force-acting chain with the bearing 20. In order to be able to achieve the desired pretensioning even in the absence of overpressure inside the force application chain inside the pressure chamber 11, a pretensioning spring 14 is arranged inside the pressure chamber 11. In the state shown in fig. 1, either no overpressure or only a small overpressure exists inside the pressure chamber 11, which overpressure either does not deform the cup spring 30 or only deforms it very little. The volume of the pressure chamber 11 in this state is defined as the minimum volume.

In a further embodiment, not shown, a pretensioning spring 14 for pretensioning the force application chain is not present inside the motor vehicle clutch.

Fig. 2 shows the clutch device 10 from fig. 1 in the same section. Only the differences from the schematic diagram of fig. 1 are explained. However, another state is shown, namely a state with an open clutch. The description of section B-B is not discussed in detail since the variations from section B-B of fig. 1 cannot be seen in this view. For actuating the clutch, in this case for opening the motor vehicle clutch 10, the pressure chamber 11 is charged with compressed air from the state of fig. 1, as a result of which the piston 12 is moved to the left (with respect to the sectional view a-a) together with the bearing 20 until it is stopped axially on the hub 13. Thereby, the disc spring 30 is reversed. More precisely, the radially inner region of the cup spring 30 (with respect to the sectional view a-a) is moved to the left, wherein the radially outer region of the cup spring 30 is maintained at the position of the axially immovable hub 13. Thereby, the contact point between the disc spring 30 and the release ring 16 is also moved leftward, whereby the clutch housing 15 is moved leftward. Thus, the friction plate set 17 is unloaded, and therefore the inner and outer friction plates can rotate independently of each other in the state shown in fig. 2, and the clutch is open.

Fig. 3 shows section B-B of fig. 1 and 2 in detail, wherein sections a-a and C-C, although indicated at another location, still represent a section through the tenon 22, while section C-C represents a section through the spring tongue 31.

Fig. 4 shows the sections C-C and a-a of fig. 3. Here, the sections C-C and a-a on the right side of fig. 4 show an embodiment of the support device 20 of the previous figures, but only the component support device 20 and the cup spring 30 are shown. In section C-C (upper right) a cut is made through the spring tongue 31. These spring tongues bear axially against the contact surfaces 21 of the bearing means 20. In this case, the support device 20 does not extend into the radially inner region of the disk spring 30 or of the spring tongues 31.

The sections C-C and a-a on the left side of fig. 4 show an alternative embodiment of the support means 20, namely the support means 20 a. This bearing 20a is identical to the bearing 20 described above, but in the bearing 20a cylindrical collar 23a extends in the axial direction from the contact surface 21a (which corresponds to the contact surface 21 of the previous exemplary embodiment) and in this case extends into the radially inner region of the disk spring 30 or spring tongue 31. The cylindrical collar 23a (viewed in the vertical or radial direction) therefore extends between a radially inner region of the disk spring 30 (more precisely the spring tongue 31) and the hub 13, not shown.

Fig. 5a, 5b and 5c show isometric views of one of bearing 20 (fig. 5a), bearing 20a (fig. 5b) and belleville spring 30. In fig. 5, four pins 22 are shown, which extend in the axial direction from the contact surface 21. Fig. 5a shows an alternative embodiment of the support device 20, namely a support device 20 a. On the pin 22a of the bearing device or on a radially inner region of the pin 22a, the lug 23a extends in a cylindrical configuration. Fig. 5c shows one of the disk springs 30 with its spring tongues 31, notches 32 (between the spring tongues) for receiving the pins 22, 22a, and an intermediate space 33 (between the spring tongues) that is smaller than the notches 32, wherein the geometry of the notches 32 and the geometry of the pins 22, 22a match one another, and the geometry of the intermediate space 33 and the geometry of the pins 22, 22a do not match one another.

The pins 22, 22a correspond to the alignment elements for aligning and centering the disk spring 30 on the bearing 20, 20a, respectively.

List of reference numerals

10 motor vehicle clutch

11 pressure chamber

12 piston

13 hub

14 pre-tightening spring

15 Clutch case

16 separating ring

17 friction plate group

20, 20a support device

21,21a contact surface

22, 22a tenons (on the contact surface of the support means); orientation element

23a flange

30 disc spring

31 spring tongue

32 notches (between spring tongues)

33 intermediate space (between spring tongues)