Clutch

Abstract

A friction clutch (1) with an inner ring (2) arranged about a rotary axis (d) and an outer ring (3) arranged coaxially in reference thereto, as well as an elastic intermediate ring (3) arranged between these two in a radially limited fashion, with the inner ring (2) and the intermediate ring (4) resting on each other via a ramp arrangement (9) arranged and acting bi-directionally in the circumferential direction. In order to embody the clutch (1) easily and cost-effectively, segments (13) pointing radially outwardly and arranged distributed over the perimeter form in connection with a radial displacement of the intermediate rings (4) relative to the outer ring (3) a positive connection (22) in the circumferential direction with the radial displacement of the intermediate ring (4) being provided with a ramp arrangement (12) effective in the axial direction and switched by an axial displacement of the inner ring (2) in reference to the intermediate ring (4).

Claims

1. A clutch comprising an inner ring arranged about a rotary axis (d) and an outer ring arranged coaxially relative to the inner ring, an elastic intermediate ring arranged between the inner ring and the outer ring and limited therebetween in a radial direction, the inner ring and the intermediate ring rest on each other via a ramp arrangement located bi-directionally effective in a circumferential direction, the intermediate ring including segments pointing outwardly and arranged distributed over a circumference of the intermediate ring to form a positive connection between the intermediate ring and the outer ring, a radial displacement of the intermediate ring being provided via the ramp arrangement by an axial displacement of the inner ring relative to the intermediate ring, the segments include recesses forming the positive connection and the outer ring includes radially inwardly extending cams, and the recesses are complementary to the radially inwardly extending cams.

2. The clutch according to claim 1, wherein the intermediate ring is embodied unilaterally open.

3. The clutch according to claim 1, wherein the segments are separated from each other via radially outer recesses extending radially inwardly.

4. The clutch according to claim 3, wherein the segments are separated from each other via radially inner recesses cut-in radially from an inner side.

5. The clutch according to claim 4, wherein the radially inner recesses and radially outer recesses are arranged on a same circumference.

6. The clutch according to claim 5, wherein a bar embodied between and by the radially inner recesses and radially outer recesses forms an elastic element arranged between the segments.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention is explained in greater detail based on the exemplary embodiment shown in FIGS. 1 and 2. Shown are:

(2) FIG. 1 a view of the clutch arranged about a rotary axis, and

(3) FIG. 2 the top part of the clutch in a cross-section.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

(4) FIG. 1 shows the clutch 1 arranged about the rotary axis b in a front view. The clutch 1 comprises the inner ring 2 and the outer ring 3 as well as the intermediate ring 4 arranged therebetween. The inner ring 2 has at its inner perimeter 5 the inner gears 6 for receiving blades of a wet-running friction clutch. In this regard, the inner ring serves as the blade carrier like the outer blade carrier.

(5) The inner ring 2 comprises at its outer perimeter inclining ramps 7, 8, arranged distributed over the circumference and alternating in both circumferential directions, at which ramps 10, 11 are received, forming the ramp arrangement 9 of the intermediate ring 4 via ramps 7, 8 embodied complementarily thereto. In a manner not shown, additionally a ramp arrangement 12 with axial ramps is arranged, shown in FIG. 2, between the inner ring 2 and the intermediate ring 4.

(6) The intermediate ring 4 has segments 13, arranged widened radially outwardly and distributed over the circumference, which are separated from each other via recesses 14, 15, 16 entered radially from the inside and radially from the outside, and thus allow a radial displacement of the intermediate ring 4 while widening the recesses 14, 15, 16. Here, the bars 19 between the segments 13 serve as elastic elements. Additionally, the intermediate ring 4 is opened unilaterally via the penetration 17. The intermediate ring 4 is received on the inner ring 2, radially pre-stressed. Depending on the switching state of the clutch 1, the segments 13 come into a positive contact with the inner perimeter 18 of the outer ring 3.

(7) The outer ring 3 can be connected in a manner not shown at its outer perimeter to a housing or the like in a form-fitting or friction-fitting fashion, or by material-to-material bonding.

(8) In order to form the active positive connection 22 shown here the cams 20 arranged distributed over the perimeter at the outer ring 3 engage radially the recesses 21 in the segments 13.

(9) FIG. 2 shows the clutch 1 of FIG. 1 in a cross-sectional detail with the inner ring 2, the outer ring 3, and the intermediate ring 4. FIG. 2 illustrates the embodiment of the ramp arrangement 12. The ramps 7, 8 of the inner ring 2 and the ramps 10, 11 of the intermediate ring 4 and/or the segments 13 complementary thereto are embodied as axially inclined ramps. The cams 20 engage the recesses 21 of the segments 13 to generate the positive connection 22.

(10) Based on the combined analysis of FIGS. 1 and 2 the function of the clutch 1 is explained. When the clutch 1 is opened, the intermediate ring 4 is radially pre-stressed on the inner ring 2 without any displacement of the ramps 7, 8, 10, 11 in reference to each other. This way a radial gap forms between the segments 13 and the outer ring 3 and/or the cams 20, so that no moment is transmitted.

(11) In order to actuate the clutch, the inner ring 2 is displaced in reference to the outer ring 3 axially for example via an actuator, a pressure piston, or the like. This way via the ramp arrangement 12, the segments 13 are displaced radially outwardly at the ramps 7, 8, 10, 11 such that the segments 13 engage the cams 20 in a friction-fitting fashion. By the different rotation of the inner ring 2 and the outer ring 3 the intermediate ring 4 is delayed or accelerated in reference to the inner ring causing a relative rotation of the ramp arrangement 9 with the inclines of the ramps 7, 8, 10, 11 arranged in the circumferential direction and thus a relative rotation of the intermediate ring 4 in reference to the inner ring 2. This way, the segments 13 are further distorted in reference to the cams 20 until the cams 20 latch radially pre-stressed in the recesses 21.

(12) In order to again open the clutch 1 the inner ring 2 is displaced in the opposite direction of the axial inclines of the ramps 7, 8, 10, 11. This way, the pre-stressing of the segments 13 is reduced in reference to the cams 20 and the intermediate ring 4 rotates under its pre-stressing force on the inner ring 2 and under releasing of the positive connection 22 between the cams and the recesses 21 into its original position, so that the force-fitting connection of the segments 13 at the outer ring 3 is released again.

LIST OF REFERENCE CHARACTERS

(13) 1 Clutch 2 Inner ring 3 Outer ring 4 Intermediate ring 5 Inner circumference 6 Inner gear 7 Ramp 8 Ramp 9 Ramp arrangement 10 Ramp 11 Ramp 12 Ramp arrangement 13 Segment 14 Recess 15 Recess 16 Recess 17 Penetration 18 Inner circumference 19 Bar 20 Cam 21 Recess 22 Positive connection d rotary axis