Clutch arrangement for transmitting torque between two shafts

Abstract

This invention relates to a clutch arrangement for transmitting torque between two shafts (3, 4), characterized in that: to achieve torque transmission, two one-way clutches (1, 2) with opposite torque transmission directions (A, B) are respectively arranged in the force flow between the two shafts (3, 4), and in their respective torque transmission directions (A, B), the torque transmission is limited to a predetermined maximum transmittable torque (M). max ).

Description

Technical Field

[0001] The present invention relates to a clutch arrangement for transmitting torque between two shafts. Background Technology

[0002] An overload clutch between a drive shaft and an output shaft is known from EP 1 106 854 B1, wherein a drive gear is provided relative to the drive side, and an overload protection component with an integrated spring element is provided axially rearward of the drive gear and engages with a toothed element fixedly connected to the output shaft. Summary of the Invention

[0003] Therefore, the objective of this invention is to provide a clutch arrangement of the above type that is simple in structure, low in cost, saves installation space, and avoids overload during torque transmission.

[0004] The task is accomplished by the features of claim 1. Other advantageous and claimed embodiments can be derived from their respective dependent claims, description, and drawings.

[0005] Therefore, a clutch arrangement for transmitting torque between two shafts is proposed, wherein, in order to achieve torque transmission, two one-way clutches with opposite torque transmission directions are respectively provided in the force flow between the two shafts, and in their respective torque transmission directions, the torque transmission is limited to a predetermined maximum transmittable torque.

[0006] By arranging two one-way clutches in opposite directions, a simple and space-saving torque transmission arrangement can be achieved in both rotational directions of the two shafts. In each rotational direction, the maximum transmittable torque can be limited by the respective one-way clutch, thus reliably preventing overload. Furthermore, the one-way clutches can be manufactured easily and at low cost from mass-produced components.

[0007] With the proposed clutch arrangement, short-term torque peaks that occur in transmission applications, such as when a vehicle is driving over uneven roads, can be reliably absorbed, preventing damage to the one-way clutch and the transmission. Simultaneously, it enables trouble-free continued operation.

[0008] To limit the maximum transmittable torque, preferably, each one-way clutch can be switched to a slipping condition when the maximum transmittable torque in its respective torque transmission direction is reached. This allows for the limitation of torque transmission in a particularly simple and reliable manner with the proposed clutch arrangement.

[0009] In a preferred, particularly space-saving, arrangement, the one-way clutches are arranged coaxially in sequence along the axial direction, and are respectively arranged coaxially between the inner diameter of the first shaft, which is at least partially constructed as a hollow shaft, and the outer diameter of the second shaft.

[0010] One embodiment of the present invention, which is particularly simplified in structure, saves more installation space and achieves lightweighting, is as follows: the one-way clutches are respectively rotatably and fixedly connected to the inner diameter of the hollow shaft section of the first shaft through the outer diameter of their respective outer rings, and the clamping body is movably disposed in the clamping gap formed by the coaxiality of the outer rings and the outer diameter of the second shaft.

[0011] Alternatively, the one-way clutches can also be rotatably and fixedly connected to the outer diameter of the second shaft by the inner diameter of their respective inner rings, and the clamping bodies are movably disposed in the clamping gap formed by the inner diameters of the corresponding inner rings and the hollow shaft section of the first shaft being coaxial.

[0012] Preferably, the clamping bodies are movably guided on clamping ramps formed in their respective clamping gaps, and in the event of overload, they can move from the working area for transmitting force in the torque transmission direction to an overload area on the clamping ramp. The overload area is configured such that the clamping bodies slip on their respective clamping ramps, thereby limiting force transmission to the maximum transmittable torque.

[0013] The one-way clutches preferably employ the same structure. Alternatively, they may be configured differently, for example, in terms of the configuration of the clamping ramp, so that different transmittable torque limits can be set, especially in different directions of rotation.

[0014] In another particularly preferred embodiment of the invention, the clamping bodies are clamping rollers. Therefore, line contact can be achieved between the clamping ramp and the clamping bodies, and between the clamping bodies and the second shaft, thereby reducing the load at the clamping contacts during operation. Alternatively, balls can also be used as clamping bodies.

[0015] In an advantageous improvement of the invention, the outer rings of the one-way clutches are each made of sheet metal sleeves. This allows for manufacturing, in a particularly lightweight, simple, and low-cost manner, without cutting, by sheet metal processing methods, especially by stamping and deep drawing. Preferably, the clamping ramps are formed without cutting at the inner diameter of each outer ring by deep drawing. Thus, the outer rings and clamping ramps can be manufactured together in a single step without cutting.

[0016] In another alternative embodiment, preferably, the clamping ramp is formed in sheet metal at the outer diameter of the inner ring of the respective one-way clutch.

[0017] It is also advantageous if the outer ring of the one-way clutch has radially inwardly projecting flanges at both axial ends for axial guidance of the clamping body. Each flange can be easily manufactured in sheet metal forming by deep drawing or flange stretching.

[0018] In a further improvement of the invention, the second shaft is configured to form a step radially inward at its end via a journal, thereby being inserted radially into a second hollow shaft segment on the first shaft that also forms a step radially inward. This achieves radial support for both shafts in a very compact and space-saving arrangement in a simple and cost-effective manner. Consequently, the one-way clutch can be arranged with virtually no radial load, thus reliably preventing damage caused by impacts during operation.

[0019] Preferably, a rolling bearing as a radial support is provided between the journal and the second hollow shaft segment. However, it is also conceivable to use a sliding bearing, especially by providing a finely ground transition fit or clearance fit between the journal and the second hollow shaft segment.

[0020] Preferably, the outer diameter of the outer ring of the rolling bearing is rotatably and fixedly connected to the inner diameter of the second hollow shaft section.

[0021] Preferably, the rolling bearing is configured as a needle roller bearing with a small radial mounting height and high load-bearing capacity. Preferably, the needle rollers are guided by rolling contact on both the inner diameter of the bearing outer ring and the outer diameter of the journal. Attached Figure Description

[0022] Other claimed features of the invention will become apparent from the following description and the accompanying drawings, which further illustrate the invention. The drawings show: Figure 1 is a cross-sectional view of a clutch arrangement of the present invention for transmitting torque between two shafts. Figure 2. A side view of the first one-way clutch of the clutch arrangement, partially sectioned along tangent A-A. Figure 3 Figure 2 A magnified partial image, Figure 4. A side view of the second one-way clutch of the clutch arrangement, partially sectioned along tangent B-B. Figure 5 Figure 4 A magnified partial view. Detailed Implementation

[0023] In the accompanying drawings, different views of the clutch arrangement of the present invention for transmitting torque between two shafts are shown by way of example.

[0024] Figure 1The clutch arrangement shown has two separate, preferably identical, one-way clutches 1 and 2, which are arranged coaxially in sequence and located in the force flow between two parallel shafts 3 and 4, respectively. The one-way clutches 1 and 2 are arranged with opposite torque transmission directions A and B, as shown... Figure 3 and Figure 5 As shown, they can only transmit torque in their respective rotational directions A and B; they idle in their respective other rotational directions A and B. By arranging the one-way clutches 1 and 2 in opposite directions, it can be ensured that torque can be transmitted in both rotational directions A and B of shafts 3 and 4, and that only one one-way clutch 1 or 2 is engaged at any given time, while the other is unloaded.

[0025] The shafts 3 and 4 are arranged coaxially in sequence. Here, the first shaft 3 has a first hollow shaft section 8 that expands at its end, which surrounds the free end of the second shaft 4. The first shaft 3 constitutes, for example, an input shaft, and the second shaft 4 constitutes an output shaft.

[0026] The one-way clutches 1 and 2 are radially disposed between the inner diameter of the first hollow shaft section 8 of the first shaft 3 and the outer diameter of the second shaft 4. The first one-way clutch 1 is rotatably fixedly connected to the inner diameter of the first hollow shaft section 8 via the outer diameters of its outer rings 6 and 7. In this hollow shaft section 8, the one-way clutches 1 and 2 are preferably directly adjacent to each other by means of their respective outer rings 6 and 7 in a press-fit manner. They are coaxially arranged relative to the second shaft 4 and surround it at the outer diameter of the second shaft 4. The rotation axes 5 of the shafts 3 and 4 simultaneously constitute the central axes of the one-way clutches 1 and 2, respectively.

[0027] A clamping body 10, consisting of clamping rollers, is provided in the radial clamping gap 9 formed by the coaxiality of the inner diameters of the outer rings 6 and 7 and the outer diameter of the second shaft 4. Figures 2 to 5 The clamping bodies 10 are guided by a rolling contact manner on the clamping ramps 11 formed in their respective clamping gaps 9 and on the outer diameter of the second shaft 4. Therefore, one clamping body 10 is guided on each clamping ramp 11. The clamping ramps 11 are formed at the inner diameter of the outer rings 6 and 7, respectively.

[0028] The one-way clutches 1 and 2 each have a working or clamping region 13 for transmitting force and torque in their respective rotational directions A and B, and an overload region 14, on the clamping ramp 11. The working or clamping regions 13 are each defined by an arc segment 15 in their respective torque transmission directions A and B, while the overload region 14 is defined by a bend point 16 in the direction opposite to their respective torque transmission directions A and B. Along the direction opposite to their respective torque transmission directions A and B, the clamping ramp 11 rises slightly towards the overload region 14, thereby narrowing the radial clamping gap 9 formed with the second shaft 4. Here, at the bend point 16, i.e., at the contact or climbing point of the clamping body 10 in the respective overload region 14, the direction of the clamping ramp 11 is formed by a tangent line tangent to the outer diameter of the clamping body 10.

[0029] For each clamping body 4, a spring element 17 is provided in the clamping gap, which acts as a compression spring to apply a preload force to each clamping body 10 relative to the respective torque transmission directions A and B of the one-way clutches 1 and 2.

[0030] When the respective one-way clutches 1 and 2 are in a stationary or idling condition, i.e., when no torque is applied in their respective torque transmission directions A and B, each clamping body 10 is in its initial position and rolled into the area of ​​the section 15 within the working or clamping region 13 of the clamping ramp 11. Here, the clamping body 10 is clamped in the clamping gap 9, thereby transmitting a force from the outer rings 6 and 7 of the respective one-way clutches 1 and 2 to the second shaft 4 via the clamping body 4 rolling on the outer diameter of the second shaft 4, or vice versa, through frictional engagement at the clamping contact point between the clamping body 10 and the clamping ramp 11 under static friction conditions.

[0031] When torque is applied in their respective torque transmission directions A and B, a normal force is generated at the clamping contact point between the clamping body 10 and the clamping ramp 11, causing the outer rings 6 and 7 to expand. At this time, the first shaft 3 can elastically flex at the first hollow shaft section 8. This causes the clamping gap 9 to expand, and the clamping body 10 to move along the clamping ramp 11 toward the overload area 14.

[0032] When a predetermined maximum transmittable torque M is reached at each of the one-way clutches 1 and 2 max When overloaded, such as Figure 3 and Figure 5As shown, the clamping body 4 will contact or climb at the second inflection point 16 in the overload region 14. During this process, the clamping conditions at the clamping contact point between the clamping body 10 and the clamping ramp 11 change. The mounting angle or clamping angle α at the clamping contact point increases until tan α > µ, where µ represents the static friction coefficient of the friction pair at the clamping contact point. Under this clamping condition, the frictional engagement clamping at the clamping contact point is released, causing the clamping body 10 to slip on the clamping ramp. Therefore, torque buildup at the respective one-way clutches 1 and 2 is stopped, and torque transmission is limited to the maximum transmittable torque M. max .

[0033] The mounting angle or clamping angle α at the clamping contact is formed between the force F to be transmitted and the normal N at the clamping contact, such as... Figure 3 The example is shown below.

[0034] By limiting the torque, peak loads can be automatically absorbed, allowing continued operation under non-overload conditions without interfering with continued operation, and especially without reducing torque transmission to zero. This load limitation particularly allows for the smaller size design of the one-way clutches 1 and 2.

[0035] When the load on each of the one-way clutches 1 and 2 decreases again during operation, each clamping body 10 returns to the working or clamping area 13 along its respective clamping ramp 11, and torque transmission is restored. In the working or clamping area 13, the clamping angle α at the clamping contact decreases again, causing tan α to... µ, and achieves frictional bonding based on static friction at the clamping contact. Thus, a force can be transmitted again at the clamping contact.

[0036] During operation, when torque is applied to the first shaft 3, one of the one-way clutches 1 and 2 will bear the torque in their respective torque transmission directions A and B. The torque is transmitted to the second shaft 3 through their respective outer rings 6 and 7 and through the clamping body 10. The other one-way clutch 1 and 2 is in an idling state and unloaded at this point. In the changed torque transmission directions A and B, torque transmission is achieved through the latter, while the aforementioned one-way clutches 1 and 2 are in an idling state and unloaded.

[0037] In this way, torque transmission is achieved in two rotational directions A and B through the oppositely arranged one-way clutches 1 and 2, while simultaneously achieving the corresponding torque limiting as described above. Correspondingly, torque can also be transmitted in the opposite direction, i.e., from the second shaft 4 to the first shaft 3 via the one-way clutches 1 and 2.

[0038] according to Figure 1 The outer rings 6 and 7 of the one-way clutches 1 and 2 respectively have annular flanges 18 and 19 protruding radially inward at both ends of the axial direction, and the clamping body 4 is axially guided thereon.

[0039] Preferably, the outer rings 6 and 7 are respectively made into sleeves, and are preferably manufactured from sheet metal by stamping and deep drawing without cutting. The clamping ramps 11 are preferably manufactured at the inner diameter of their respective outer rings by deep drawing without cutting. The flanges 18 and 19 can be simply manufactured as flanges by deep drawing or flanging stretching.

[0040] The second shaft 4 has a step formed radially inward at the end near the clutch side with a journal 20, and is thereby inserted radially into the second hollow shaft section 21 on the first shaft 3, which also has a step formed radially inward.

[0041] As a radial support, a rolling bearing 22 and its outer ring 23 are provided. The outer diameter of the outer ring 23 is rotatably and fixedly connected to the inner diameter of the second hollow shaft section 21. The rolling bearing 22 is preferably constructed as a needle roller bearing, including needle rollers 24, which are guided by rolling contact on both the inner diameter of the outer ring 23 and the outer diameter of the journal 20. Through the rolling bearing 22, the radial load between the two shafts is supported, so that the one-way clutches 1 and 2 are arranged essentially without radial load.

[0042] Explanation of reference numerals in the attached figures 1. One-way clutch 2 One-way clutch 3-axis 4-axis 5. Rotation axis, central axis 6 Outer ring 7 Outer ring 8 First hollow shaft section 9 Clamping gap 10 Clamping body, clamping roller 11. Clamp the slope 13. Working area for force transmission, clamping area 14 Overload Area 15 paragraphs 16 inflection points 17. Spring elements, compression springs 18. Flanged edge, raised flange 19. Flanged edge, raised edge 20 journals 21 Second hollow shaft section 22 Rolling bearings, needle roller bearings 23 Bearing outer ring 24 needle rollers A. Torque transmission direction, rotation direction B. Torque transmission direction, rotation direction α Angle of clamping F force N normal

Claims

1. A clutch arrangement for transmitting torque between two shafts (3, 4), characterized in that: To achieve torque transmission, two one-way clutches (1, 2) with opposite torque transmission directions (A, B) are respectively installed in the force flow between the two shafts (3, 4), and in their respective torque transmission directions (A, B), the torque transmission is limited to a predetermined maximum transmittable torque (M). max ).

2. The clutch arrangement according to claim 1, characterized in that, To limit the maximum transmittable torque (M) max Each one-way clutch (1, 2) reaches the maximum transmittable torque (M) max When ), it can be switched to slipping mode.

3. The clutch arrangement according to claim 1 or 2, characterized in that, Two one-way clutches (1, 2) are arranged coaxially in sequence along the axial direction, and are respectively arranged coaxially between the inner diameter of the first shaft (3) which is at least partially constructed as a hollow shaft and the outer diameter of the second shaft (4).

4. The clutch arrangement according to any one of claims 1 to 3, characterized in that, Two one-way clutches (1, 2) are rotatably and fixedly connected to the inner diameter of the hollow shaft section (8) of the first shaft (3) by the outer diameter of their respective outer rings (6, 7), and the clamping body (10) is movably disposed in the clamping gap (9) formed by the inner diameter of the corresponding outer ring (6, 7) and the outer diameter of the second shaft (4) being coaxial.

5. The clutch arrangement according to claim 4, characterized in that, The clamping bodies (10) are movably guided on clamping ramps (11) formed in their respective clamping gaps (9), and in case of overload, they can move from the working area (13) for force transmission to the overload area (14) on the clamping ramp (11), wherein the overload area (14) is configured to cause the clamping bodies (10) to slip on the respective clamping ramps (11), thereby limiting the force transmission to the maximum transmittable torque (M). max ).

6. The clutch arrangement according to claim 4 or 5, characterized in that, The clamping bodies (10) are clamping rollers.

7. The clutch arrangement according to any one of claims 3 to 5, characterized in that, The outer rings (6, 7) of the one-way clutches (1, 2) are respectively made into sheet metal sleeves.

8. The clutch arrangement according to any one of claims 4 to 6, characterized in that, The outer rings (6, 7) of the one-way clutches (1, 2) are respectively formed with flanges (18, 19) protruding radially inward at both ends of the axial direction, which are used to guide the clamping body (10) axially.

9. The clutch arrangement according to any one of claims 1 to 8, characterized in that, At the end of the second shaft (4), the journal (20) forms a step in the radial direction, thereby cooperating with the second hollow shaft segment (21) of the first shaft (3) which forms a step in the radial direction in a radially supported manner.

10. The clutch arrangement according to claim 9, characterized in that, The radial support is a needle roller bearing (22) with an outer ring (23). The outer diameter of the outer ring (23) is rotatably and fixedly connected to the inner diameter of the second hollow shaft section (21). The needle rollers (24) are guided by rolling contact on the inner diameter of the outer ring (23) and on the outer diameter of the journal (20) on the other hand.

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