Isolated overload clutch with modular structure

Abstract

A form-locking overload clutch that reengages by applying an external force is proposed, which consists of a component flange and a pressure flange, and the pressure flange is rotatably supported relative to the component flange by a bearing. The overload clutch has a stepped hole arranged on the pitch circle of the component flange, and a synchronization opening arranged coaxially with the stepped hole on the pressure flange is opposite to the stepped hole. The stepped hole has a transmission area and a receiving area, wherein a bolt, a support plate, a set of switching segments or switching balls, a pressure plate, a spring element and an adjusting nut are accommodated in at least one stepped hole, wherein at least a pressure piece with a groove is accommodated in the synchronization opening of the pressure flange that is concentrically opposite to the stepped hole, wherein the bolt is pressed into the groove of the pressure piece by the force of the spring element and thereby transmits torque. The invention is characterized in that at least one stepped hole is directly introduced into the component flange and forms an integral geometry with the component flange.

Description

Technical Field

[0001] Mechanical overload clutch has been proved to be a reliable mechanical component for avoiding damage caused by excessive torque in the field of industrial drive technology. In particular, the structural type of the transmission component with a positive locking of the force application is characterized by high accuracy in releasing the torque.

[0002] Depending on the technical requirements, different functional designs can be found in force-exerting, form-locking mechanical overload clutches:

[0003] - Ratchet overload clutch for a simpler drive.

[0004] - Synchronous overload clutch with conformal reengagement.

[0005] - Overload clutch with reengagement by reversal of direction of rotation.

[0006] -Isolated overload clutch with reengagement by application of external force.

[0007] The subject matter of the invention proposed here is a technical improvement of the design of the last-mentioned isolating overload clutch with reengagement by application of external force. Background Art

[0008] From the prior art, isolating overload clutches with reengagement by application of external force are known, in which an isolating component with an associated pressure piece is integrated into a simple structure consisting of two flanges that can rotate relative to each other. This type of isolating component or this type of isolating overload clutch with reengagement by application of external force, which is referred to below as overload clutch, is described in EP 0 156 993 B1 of the applicant.

[0009] The advantage of the overload clutch according to the teaching of EP 0 156 993 B1 is that the insulating component used here can be easily combined with its component housing into existing designs. The disadvantage is that it is expensive and usually requires a large installation space, because the function of the clutch is divided into two areas: a first area consisting of flanges supported relative to each other and a second area consisting of the insulating component and the pressure piece arranged on the pitch circle and preferably screwed on. Summary of the invention

[0010] The invention is therefore based on the object of providing an overload clutch of as modular a design as possible, which allows a compact design with a high power density and can be manufactured inexpensively.

[0011] In order to achieve this object, it is proposed to construct an overload clutch consisting of a component flange and a pressure flange which is arranged coaxially with the component flange and is rotatably mounted.

[0012] The component housing of the release component from the prior art is integrated into the component flange of the clutch. For this purpose, the internal geometry of the previous component housing is introduced into the component flange in the form of an axially or radially oriented stepped hole. The functional component of the overload clutch that transmits the torque is built into the stepped hole of the component flange, which is formed by a bolt, a pressure plate, a support plate, a plurality of switching segments or balls, a spring element and an adjustment ring. The spring element can consist of one or more helical springs arranged concentrically with the bolt or a group of layered disc springs. The synchronization opening is introduced into the pressure flange coaxially with the stepped hole of the component flange, and a pressure piece is installed in the synchronization opening.

[0013] The stepped bore and the synchronization opening can advantageously be arranged at the same angular spacing on the pitch circle.

[0014] In order to adapt the overload clutch to the torque to be transmitted, only some of the stepped holes and the synchronization openings can be equipped with screws or pressure pieces and the stepped holes that are not required can be closed, for example, with covers.

[0015] Another possibility for adapting the overload clutch to the torque to be transmitted is to change the preload of the spring element. For this purpose, the adjusting ring can be designed as an adjusting nut with an external thread, whose axial position in a stepped bore with a corresponding internal thread can be changed by rotation. The adjusting nut can be locked against unintentional rotation by means of a friction-locking or form-locking component.

[0016] The overload clutch transmits the torque from the component flange to the pressure flange by pressing the bolts of the spring flange through the spring element via the pressure plate, the support plate and the switching segment or ball into the preferably conical groove of the pressure piece embedded in the synchronization opening of the pressure flange. When the overload clutch is disengaged, the circumferential force acting on the bolts and the pressure piece by the torque exceeds the level defined by the pretension of the spring element. As a result, the bolt moves out of the groove of the pressure piece in the axial direction and releases the rotation between the component flange and the pressure flange. Due to the special geometric design and arrangement of the bolts, the pressure plate, the support plate, the switching segment or ball and the spring element, the bolt is held in its position outside the engagement with the pressure piece and the overload clutch can be stopped without further contact between the bolt and the pressure piece.

[0017] The disengaged or engaged state of the overload clutch can be detected by a sensor, which detects the position of the bolts in the component flange. If the bolts are equipped with a common switching disk, the axial position of which relative to the component flange is then queried, this detection can be further improved.

[0018] To reengage the overload clutch, the component flange and the pressure flange are rotated relative to each other with the drive stationary in such a way that the center axes of the bolt and the pressure piece are aligned. The bolt can then be brought into positive engagement with the recess of the pressure piece again by applying an external force in the direction of the pressure piece. To facilitate the alignment of the center axes of the bolt and the pressure piece, clearly visible indexing holes or other markings can be provided on the outer circumference of the component flange and the pressure flange.

[0019] By means of the construction and functions briefly described here, an overload clutch can be provided which can transmit high torques in a compact construction. Furthermore, by integrating the stepped bore in the component flange, a high modularity and adaptability of the overload clutch to the required torque can be achieved. In addition, the overload clutch according to the invention allows simple and reliable detection of the operating state and can be manufactured very cost-effectively. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Other features and advantageous details of the overload clutch according to the invention are apparent from the description of the preferred embodiment shown below. Here, components that correspond in their function are provided with the same reference numerals in all the figures.

[0021] It goes without saying that the present invention is not limited to the feature combinations in the claims or the description. For a technician, other meaningful combinations of the claims and / or other meaningful combinations of features from the claims and / or the description and / or from the features in the drawings will be apparent from the formulation of the task.

[0022] Figure 1 A longitudinal section AA and a cross section BB are shown through an axial overload clutch according to the invention as a flange embodiment with an axially oriented stepped bore in the engaged state.

[0023] Figure 2 Shown from Figure 1 Detail C and detail D as half-section views of an axial overload clutch according to the invention with an axially oriented stepped bore.

[0024] Figure 3 A longitudinal section CC through a second axial overload clutch according to the invention with an axially oriented stepped bore in combination with an elastomeric clutch is shown in the disengaged state.

[0025] Figure 4 Shown from Figure 3 Detail E of an axial overload clutch according to the invention with an axially oriented stepped bore and detail F derived from detail E by projection.

[0026] Figure 5 A longitudinal section DD is shown through a third axial overload clutch according to the invention as an embodiment for a hollow-shaft electric motor in the engaged state with an axially oriented stepped bore.

[0027] Figure 6 A longitudinal section EE through a fourth radial overload clutch according to the invention with an axially oriented stepped bore in combination with a rotationally fixed all-steel clutch in the engaged state is shown. DETAILED DESCRIPTION

[0028] from Figure 1 The basic structure of the first axial overload clutch K1 according to the invention can be seen in FIG. Here, the component flange 1 is connected to the pressure flange 2 via a bearing 3 and is supported rotatably relative to the pressure flange 2 about the rotation axis R. A plurality of axially directed stepped holes 5 are preferably introduced at equal angular intervals on a pitch circle of the component flange 1 that is concentric with the rotation axis R. On the pressure flange 2, a corresponding synchronization opening 22 is located opposite the stepped hole 5, in which a pressure piece 23 with a preferably conical groove 24 is accommodated, wherein the center axes of the stepped hole 5 and the groove 24 are aligned with each other. Here, the pressure piece 23 is fixed in the synchronization opening 22 of the pressure flange 2 by means of a fixing screw 25. In this example, only two of the four stepped holes 5 are used for transmitting torque, and the other two stepped holes 5 are closed with a closure cap 27. The stepped hole 5 of the component flange 1 consists of a transmission area 6 and a receiving area 7, wherein the receiving area 7 has a larger diameter than the transmission area 6.

[0029] from Figure 1 and especially from the one with detail D Figure 2 1, it can be seen how the bolt 9 equipped with the transmission ball 13, the support plate 14, the switching segment 16, the pressure plate 15, the spring element 18 in the form of a leaf spring assembly and the adjusting nut 19 are arranged in the stepped bore 5 in the stated order, starting from the pressure piece 23. As an alternative to the two-part design of the bolt 9 equipped with the transmission ball 13, the bolt 9 can also be provided with a screwed-on ball geometry or a cone at its end in one piece.

[0030] The torque of the clutch is transmitted from the component flange 1 to the pressure flange 2. To ensure this, the spring element 18 is prestressed axially by means of the adjusting nut 19 and transmits its force to the pressure plate 15. The switching segment 16 is thus clamped axially between the pressure plate 15, which is provided with an inner cone, and the support plate 14, which also has an inner cone, and exerts a force directed radially toward the bolt 9 via these inner cone surfaces. In this case, the switching segment 16 rests on the cone surface on the outer circumference of the bolt 9 and, together with the transmission balls 13 embedded in the hole of the bolt 9, pushes the bolt in the direction of the pressure piece 23. In this case, the axial force generated between the component flange 1 and the pressure flange 2 and acting on the bearing 3 is absorbed by the bearing cover 4, which is screwed to the pressure flange 2.

[0031] The adjusting nut 19 is locked against unintentional rotation by means of a locking plate 20, wherein the locking plate 20 engages the hexagon of the adjusting nut 19 in a form-fitting manner by means of a hexagon shown in detail C, and wherein the locking plate 20 is simultaneously fixed to the outer circumference of the component flange 1 by means of locking screws 21. This allows for a delicate adjustment and locking of the adjusting nut 19 in steps of 30 degrees.

[0032] In order to prevent lubricant from escaping into the environment and to prevent dirt from entering the axial overload clutch K1, an outer seal 28 is arranged between the component flange 1 and the pressure flange 2, and an inner seal 29 is arranged between the bearing cover 4 and the component flange 1. For lubrication, the screw 9 has a lubrication channel 10, which can be supplied with lubricant starting from the outer circumference of the component flange 1 via a lubrication connection 12 and a lubrication hole 11.

[0033] If the torque transmitted between the component flange 1 and the pressure flange 2 exceeds the value defined by the force of the spring element 18, the component flange 1 and the pressure flange 2 begin to rotate relative to each other about the rotation axis R. In this case, the bolt 9 equipped with the transmission balls 13 moves in the direction of the bolt disengagement direction D1, and the switching segment 16 slides from the cone surface of the bolt 9 to its outer circumferential surface, which contacts the transmission area 6 of the stepped hole 5. The axial overload clutch K1 is now in the separated state, which is in the state of Figure 3 in and Figure 4 , shown in detail E and detail F.

[0034] exist Figure 3 The axial overload clutch K1 in detail E and detail F is functionally identical to that in detail E. Figure 2 The axial overload clutch in corresponds to that in , but is equipped for transmitting torque between two shafts, which additionally have a clutch hub K3 on the component flange 1 and a form-locking elastomeric clutch K2 on the pressure flange 2 .

[0035] In addition, Figure 3 Neutral Figure 4 The axial overload clutch K1 shown in FIG. 1 has an annular switching component 30, which is composed of a switching ring 31 and a web 32 and is fixed to the bolt 9 by means of a web screw 33. When the axial overload clutch K1 is disengaged, the bolt 9 performs an axial lifting movement in the bolt disengagement direction D1 together with the switching component 30, wherein the position of the switching component 30 is detected by a sensor 44 and transmitted to the controller. This signal can, for example, stop the drive after the axial overload clutch K1 is disengaged. The sensor 44 can be designed in the form of a mechanical or contactless switch.

[0036] After the drive has been switched off, the now stationary axial overload clutch K1 can be reengaged. For this purpose, the component flange 1 and the pressure flange 2 are rotated relative to one another to such an extent that the indexing holes 26 and therefore the bolts 9 and the pressure piece 23 face one another in alignment. In this position, the bolts 9 are moved at their ends facing the switching element 30 by hammering or axial pressure in the bolt engagement direction D2 toward the pressure piece 23 until they engage again there or until the switching segment 16 again rests on the outer cone surface of the bolt 9 and exerts a defined force on the bolt in the direction of the pressure piece 23. The engagement of the bolts 9 can be carried out individually or in groups with the aid of a special engagement device, wherein the switching element 30 is designed in such a way that it can elastically absorb the deformation of the switching ring 31 and the web 32 that occurs during this period. In this case, the engagement of the bolts 9 can be carried out by manual auxiliary actions or by an automated device.

[0037] exist Figure 5The axial hollow shaft overload clutch K4 according to the invention shown in FIG. 1 , which is designed in particular for mining applications, corresponds to the previous exemplary embodiment in terms of its function. However, the design of the bearing is reversed compared to the previous exemplary embodiment, wherein the bearing 3 is supported with its inner ring on the tubular extension of the component flange 1 and the pressure flange 2 with the pressure piece 23 is rotatably supported above it. The axial forces acting on the bearing 3 are also absorbed here by the bearing cover 4. The pressure flange 2 of the axial hollow shaft overload clutch K4 is connected to the hollow shaft 34 of the drive, preferably of the electric motor, via a cone flange 35. Here, the cone flange 35 equipped with an outer cone 36 is clamped in a friction-locking manner on the cylindrical circumferential surface of the hollow shaft 34 by a clamping ring 37 equipped with an inner cone 38 and to which a clamping screw 39 is applied. Alternatively, the circumferential surface of the hollow shaft 34 can also be formed by external teeth, wherein the cone flange 35 has corresponding internal teeth in this case and can also be fixed to the hollow shaft 34 without play by means of a clamping ring 37. Instead of a clamping ring connection, the torque transmission between the hollow shaft 34 and the cone flange 35 can also be realized by a parallel key connection, a clamping hub or a clamping ring hub or a hydraulic hollow sleeve-clamping sleeve. The component flange 1 has axial teeth on its inner diameter, which are in a form-locking connection with the gear shaft 40, wherein the gear shaft 40 is located radially inside the hollow shaft 34 with its shaft body and axially passes through the hollow shaft. The gear shaft 40 is connected to the retaining flange 41 by means of a pull-out screw 43 and is locked against axial movement, wherein the retaining flange 41 is fixed in the component flange by means of a retaining screw 42. The torque transmission when the drive is activated starts from the hollow shaft 34 of the drive and extends via the cone flange 35, the pressure flange 2, the pressure piece 23, the transmission balls 13, the screws 9, the transmission area 6 of the stepped bore 5 and the component flange 1 to the gear shaft 40, which transmits the torque through the hollow shaft 34 to the output on the other side of the hollow shaft 34. The output can be formed, for example, by a transmission, preferably a planetary transmission.

[0038] With the help of Figure 5 The advantage of the described axial hollow shaft overload clutch K4 is that it is located at the free end of the hollow shaft 34 and is therefore easily accessible for maintenance work and can be easily replaced during regular repair work.

[0039] Figure 6As a final embodiment, a radial overload clutch K5 is shown, which consists of a component flange 1 and a pressure flange 2, wherein the component flange 1 is arranged radially outside the pressure flange 2 concentrically with the latter and is fixed rotatably relative to the pressure flange by means of a bearing 3. The radially inner pressure flange 2 has a hole 45 concentric with the axis of rotation R for direct fixing to the drive shaft. In contrast to the previous example, the stepped bore 5 is arranged radially in the component flange 1 and the bolt 9 is connected in a form-fitting manner to the pressure piece 23 radially inside the synchronization opening 22 of the pressure flange 2. In this case, the bolt 9 has an integral ball-shaped or conical geometry, by which the bolt is in contact with the pressure piece 23. In this example, the bolt 9 is pressed into the groove 24 of the pressure piece 23 by means of a spring element 18, a pressure plate 15, a switching ball 17 and a support plate 14, wherein the pretension of the spring element 18 can be applied and varied by means of an adjusting nut 19. In this example, the adjusting nut 19 is of two-part design and is clamped in a frictionally locking manner in the internal thread 8 of the stepped bore 5 by axially spreading the two disk-shaped halves apart.

[0040] The radial overload clutch K5 shown is used to transmit torque between two shafts, wherein the component flange 1 is connected to a torsionally rigid elastic all-steel clutch K6 for this purpose. The particular advantages of the radial overload clutch K5 are the small axial structural length and the avoidance of forces acting on the bearing 3, since the forces acting between the bolt 9 and the pressure piece 23 cancel each other out on the circumference of the radial overload clutch K5. As a result, smaller bearings 3 with lower rated loads can be used, thereby achieving a more compact design and thus further reducing costs. Further advantageous features of the invention are derived from the following independent and dependent claims.

[0041] List of reference numerals:

[0042] 1 Component flange

[0043] 2 Pressure flange

[0044] 3 Bearings

[0045] 4 Bearing cap

[0046] 5 Stepped Hole

[0047] 6 Transfer Area

[0048] 7 Receiving area

[0049] 8 Internal thread

[0050] 9 Bolts

[0051] 10 Lubrication channel

[0052] 11 Lubrication hole

[0053] 12 Grease fitting

[0054] 13 Transfer ball

[0055] 14 Support plate

[0056] 15 Pressure plate

[0057] 16 Switching segment

[0058] 17 Switching ball

[0059] 18 Spring element

[0060] 19 Adjusting nut

[0061] 20 Locking plate

[0062] 21 Locking screw

[0063] 22 Synchronous opening

[0064] 23 Pressure piece

[0065] 24 Groove for pressure piece

[0066] 25 Fixing screw for pressure piece

[0067] 26 Indexing holes

[0068] 27 Closure cover

[0069] 28 Outer sealing ring

[0070] 29 Inner seal ring

[0071] 30 Switching Widgets

[0072] 31 Switching ring

[0073] 32 splice

[0074] 33 Tab screw

[0075] 34 Hollow shaft

[0076] 35 Cone Flange

[0077] 36 outer cone

[0078] 37 Clamping ring

[0079] 38 inner cone

[0080] 39 Clamping screw

[0081] 40 Gear shaft

[0082] 41 Retaining flange

[0083] 42 Retaining screw

[0084] 43 Pull out the screw

[0085] 44 Sensors

[0086] 45 holes

[0087] D1 Bolt release direction

[0088] D2 Bolt joint direction

[0089] K1 axial overload clutch

[0090] K2 Elastomer Clutch

[0091] K3 Clutch Hub

[0092] K4 Axial hollow shaft overload clutch

[0093] K5 Radial Overload Clutch

[0094] K6 All-steel clutch

[0095] R Rotation axis

Claims

1. An overload clutch with a positive lock that reengages by applying an external force, comprising a component flange (1) and a pressure flange (2), the pressure flange (2) being supported rotatably relative to the component flange (1) by means of a bearing (3), wherein: The overload clutch has a stepped hole (5) arranged on the pitch circle of the component flange (1), a synchronization opening (22) arranged coaxially with the stepped hole on the pressure flange (2) is located opposite the stepped hole, wherein the stepped hole (5) has a transmission area (6) and a receiving area (7), A bolt (9) is accommodated in at least one stepped hole (5), and a support plate (14), a set of switching segments (16) or switching balls (17), a pressure plate (15), a spring component (18) and an adjusting nut (19) are sequentially mounted on the outer circumference of the bolt (9). The spring element (18) is pretensioned axially by means of an adjusting nut (19) and transmits the pretension to the pressure plate (15), the switching segment (16) or the switching ball (17) is clamped axially between the support plate (14) and the pressure plate (15), A pressure piece (23) having a groove (24) is accommodated at least in a synchronization opening (22) which is concentrically opposite to the stepped hole (5). In this case, at least one bolt (9) is pressed into a groove (24) of at least one pressure piece (23) by the force of a spring element (18) and thereby transmits a torque. It is characterized in that At least one stepped hole (5) is introduced directly into the component flange (1) and forms a one-piece geometry with the component flange (1); and The pressure flange (2) is connected to the hollow shaft (34) of the drive in a torque-transmitting manner via a cone flange (35), wherein the component flange (1) is connected to a gear shaft (40) in a torque-transmitting manner via its axial internal teeth, which transmits the torque through the hollow shaft (34) to the side of the hollow shaft (34) facing away from the overload clutch and thus to the output end.

2. The overload clutch according to claim 1, characterized in that: At least one stepped hole (5) on a component flange (1) is arranged on a pitch circle, wherein a center axis of the at least one stepped hole (5) forms an angle of zero with the axis of rotation (R).

3. The overload clutch according to claim 1, characterized in that: At least one stepped hole (5) on the component flange (1) is arranged on a pitch circle, wherein a center axis of the at least one stepped hole (5) forms an angle of 90 degrees with the axis of rotation (R).

4. The overload clutch according to claim 1, characterized in that: At least one stepped hole (5) on the component flange (1) is arranged on a pitch circle, wherein a center axis of the at least one stepped hole (5) forms an angle between zero and 90 degrees with the axis of rotation (R).

5. The overload clutch according to claim 1, characterized in that: At least one screw (9) is equipped with a transmission ball (13) at its end facing the pressure piece (23).

6. The overload clutch according to claim 1, characterized in that: At least one screw (9) is integrally equipped with a ball-shaped or conical transmission geometry at its end facing the pressure piece (23).

7. The overload clutch according to claim 1, characterized in that: The overload clutch has at least two screws (9), and the screws (9) are connected at their ends facing away from the pressure piece (23) to an annular switching element (30), which consists of a switching ring (31) and a web (32) and whose axial position can be queried by a sensor (44).

8. The overload clutch according to claim 1, characterized in that: The pretension of the spring element (18) can be varied by means of an adjusting nut (19) which is adjustably arranged in the internal thread (8) of the stepped bore (5).

9. The overload clutch according to claim 1, characterized in that: The adjusting nut (19) is locked on the component flange (1) by friction locking or secured by means of a locking plate (20) and a locking screw (21) to prevent unintentional rotation.

10. The overload clutch according to claim 1, characterized in that: Only a portion of the stepped holes (5) in the component flange (1) is fitted with a torque transmission component, and the other portion of the stepped holes (5) is closed by a closing cover (27).

11. The overload clutch according to claim 1, characterized in that: The pressure flange (2) is connected to the hollow shaft (34) of the drive without play via a conical flange (35), wherein the conical flange (35) with an outer cone (36) is operatively connected to a clamping ring (37) with an inner cone (38) and is clamped on the hollow shaft (34) via clamping screws (39).

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