Self-centering safety element and coupler comprising a plurality of such safety elements

Abstract

This invention relates to a safety element (5a) with self-returning characteristics for a coupler (1), the coupler comprising two coupler elements (2, 3), wherein, in the coupled state, torque can be transmitted between the two coupler elements (2, 3), and wherein, by means of the safety element, the two coupler elements (2, 3) can switch to the coupled-out state and automatically return to the coupled-in state according to the torque. Furthermore, this invention relates to a coupler comprising at least one safety element (5a) according to the invention.

Description

Technical Field

[0001] This invention relates to a safety element according to claim 1, which is configured for a coupler. It has the characteristic of being coupled out according to torque in the event of a failure due to overload. Furthermore, the safety element can subsequently autonomously return to the coupled state. Furthermore, this invention relates to a coupler comprising a plurality of safety elements according to the invention, particularly a shaft coupler capable of switching according to torque. Background Technology

[0002] The safety element is configured as a coupler, which includes two coupler elements, which can be understood as coupler halves. In the case of a shaft coupler, torque can be transmitted between the two coupler elements in the coupled state, wherein, by means of the safety element, the two coupler elements can autonomously switch to the coupled-out state according to the torque (i.e., when a defined torque is exceeded), provided that the safety element includes: a push rod, which is movable in its axial direction by means of a provided support to provide its coupled-in or coupled-out state in the assembled state of the coupler; a locking element, which abuts against the push rod, such as a ball, wherein, preferably, the locking element abuts against the end face of the push rod; and a spring device, by means of which the spring force can be transmitted to the push rod and further to the locking element, such as a butterfly spring assembly, wherein the push rod has a shoulder element, which protrudes radially at the push rod, preferably a surrounding annular shoulder element, wherein at least one A transmission body, which is in contact with and works in conjunction with the shoulder element and at least one pressure body, wherein the transmission body is, for example, a rolling element, and preferably the pressure body is configured as a surrounding annular pressure body, for which the pressure body has a turning surface, and the shoulder element includes two functional surfaces, namely an inclined surface also pointing in the axial direction and a laterally arranged rest surface, wherein the transmission body contacts the inclined surface of the shoulder element in the coupled state of the coupler in a manner that transmits spring force, and in the coupled state of the coupler (neutral), it rests against the laterally rest surface of the shoulder element. Further, in the assembled state, the push rod and locking element are assigned to the first of the two coupler elements of the coupler, and the other second coupler element is assigned a locking region, for example a conical or spherical opening, which is constructed complementary to the locking element. Here, the locking region practically forms part of or is assigned to the safety element.

[0003] This type of safety element, and the coupler equipped with it, is used in heavy-duty machinery, such as machines in the mining, construction, or conveying technology industries, like cranes, such as container cranes. Container cranes in modern port terminals, for example, have special requirements due to increasing automation.

[0004] Furthermore, safety elements are known that, if they are in the out-of-coupling position and the coupler elements are disengaged after a failure, they cannot autonomously return to the in-coupling state. In this type of safety element, return must be forcibly initiated by manual operation, which is labor-intensive and always requires on-site personnel. US 2010 / 0224713 A1 provides an example of this, proposing a safety element and a coupler equipped with it. Each safety element is arranged on one half of the coupler and includes a pushrod that, in the in-coupling state, can transmit torque to the other half of the coupler in the forward position via spring force. After a failure, the pushrods and locking elements of all safety elements are pushed back to a position where no spring force can be transmitted to the pushrods. The transmission of force from the spring mechanism is interrupted or neutralized. To switch the coupler back to torque-transmitting operation, the transmission of spring force to the pushrods must be restored and the neutralization must be canceled. In the aforementioned prior art, this switching can only be initiated by manual intervention, which can be achieved, for example, by targeted hammering and requires an operator.

[0005] The applicant has proposed a safety element with a self-returning function in DE 10 2019 110 297 B3. Using this safety element or a coupler equipped with it, after a failure, re-coupling can be achieved when the coupler is partially disengaged, without the need for manual operation of each safety element. In this prior art, a mechanism is provided including an operating lever externally disposed on a housing, which is pivotable against a push rod by a spring force to return to the coupled state. This application now seeks an improved solution to this problem. Summary of the Invention

[0006] Based on the objective of this invention, a safety element is provided that is installed in a coupler and can be re-engaged after the coupling and torque transmission have been disconnected for safety reasons, without requiring an operator to manually return each of the many safety element push rods at the operating point of the coupler.

[0007] According to the present invention, this task is solved by further forming the resting surface of the shoulder element of the pushrod into an action surface, which has an angle relative to the axial direction of the pushrod, that is, tilted at an angle α relative to the axial direction of the pushrod.

[0008] Here, the proposed angle of the action surface corresponds to the direction in which the slope of the shoulder element also inclines. The action surface, on the one hand, directs the spring force and on the other hand, causes the transmission of the spring force. This transmission is designed such that a small, defined force component is applied to the tappet only in the axial direction, so that re-coupling in that direction occurs in a way that protects the material.

[0009] The appropriate size of the inclination angle for the working surface can be determined empirically. Practically, the locking element can only be repositioned into the locking area when the rotational speed difference between the coupling halves is small, because in this way, re-coupling can be achieved with a small return force on the pushrod in a way that protects the material.

[0010] If the transmission body is constructed as a rolling element, it does not necessarily perform pure rolling motion; instead, there will be sliding portions with the pushrod or pressure body. Thus, it involves both partial rolling and partial sliding.

[0011] According to this new approach, safety elements can be provided that are designed for different torques and / or graded according to different structural dimensions. Practically, a series of safety element models can be provided. Advantageously, for each safety element in the series, a suitable angle for the inclination of the working surface of the shoulder element for the tappet is defined. For example, this angle can be empirically determined for each size of the corresponding safety element or for each desired torque.

[0012] During the operation of the coupler, both coupler elements (coupler halves) rotate and can transmit a certain maximum torque. The overall performance of the coupler depends on the characteristics and number of safety elements used. This results in a cumulative performance corresponding to the number of existing safety elements in the coupler. When the maximum torque is exceeded, the locking elements of all safety elements and the push rods simultaneously retract from the locking area against the force of the spring device, preventing further torque transmission. Preferably, the transmitting body of the ball no longer rests completely neutrally against the action surface of the push rod. This allows a force component to be introduced into the push rod in the axial direction, causing the push rod to advance in the direction of the locking area.

[0013] In safety elements of US 2010 / 0224713 A1 and DE 10 2019 110 297 B3, a resting surface is provided on the shoulder element of the tappet. If the transmitting body (ball) rests against the resting surface in the coupled state, although the movable pressure body can still push the ball, the ball can no longer transfer force to the tappet through the resting surface. The spring force caused by the spring mechanism is neutralized. As long as the ball remains in contact with the resting surface, the coupler half is separated. Both the safety elements of US2010 / 0224713 A1 and DE 10 2019 110 297 B3 require significant overhead, both in terms of personnel and equipment, to apply force to the tappet from the outside.

[0014] In contrast, the new solution proposed here alters the function of the resting surface by transforming it into an action surface. This action surface is practically inclined at an acute angle relative to the axial direction of the pushrod. When the motion of the transmission ball on the action surface is redirected, a defined transmission ratio is involved due to the angle α of its inclination. The transmission ratio of the action surface can be adjusted by changing the inclination angle α. The desired outcome is to guide a relatively small axial force into the pushrod and allow it to re-advance in the direction of its coupled position. Practically, this transmission ratio is such that the locking element is only allowed to re-enter the locking region when the speed difference between the coupling halves is small. Re-coupling should only be allowed with a significantly reduced return force on the pushrod.

[0015] Thus, the coupler equipped with the safety element according to the invention can now autonomously recouple in the event of a failure leading to an interruption of coupling and torque transmission, simply by slowly restarting the driven coupler element. It is always recommended to eliminate problems leading to torque overload before recoupling. Practically, the coupler is only slowly restarted after this to autonomously recouple. The driven coupler element is slowly placed in rotation such that a small axial return force transmitted to the pushrod is sufficient to advance all the locking elements of one coupler half into the locking area of ​​the other coupler half, thereby restoring torque transmission.

[0016] The transmission ratio, adjusted by the tilt angle of the action surface, is selectively chosen so that successful re-coupling of the locking element can only occur with a limited speed difference. Therefore, it is a protective process. As mentioned, practically, the coupler should first be completely stopped, and the cause of torque overload should be identified and eliminated before restarting and re-coupling.

[0017] Couplers equipped with the proposed safety element can thus be advantageously put back into operation without requiring field operators to manually or externally manipulate each tappet and bring it into its forward position using complex mechanical devices. Practically, the movement is performed slowly, so that the small axial force component for the tappet caused by the transmission is sufficient to move it to its forward coupled position. The coupler can then transmit the torque it is designed to deliver.

[0018] Practically, the angle α of the rest surface of the shoulder element is in the range of 3° to 12°, preferably in the range of 5° to 10°, and particularly preferably in the range of 7° to 8°.

[0019] Advantageously, a first axially movable pressure body and a second pressure body are provided, wherein the second pressure body is fixedly arranged relative to the housing.

[0020] In practice, two pressure bodies are directly or indirectly loaded by a spring, wherein at least one of the two pressure bodies has an inclined turning surface, wherein each of the turning surfaces is in contact with a transmission body, and wherein the turning surface of at least one of the two pressure bodies is arranged at an angle, preferably an acute angle, relative to the radial plane.

[0021] The support portion of the pushrod can be advantageously integrated into the housing, wherein the housing has a fastening device configured for easily mounting the safety element onto the coupler element. If the housing has a cylindrical configuration, then, for example, an external thread on the housing can be provided as a fastening device, which can screw into the complementary internal thread of the coupler element.

[0022] The housing is practically equipped with an adjustment device by means of which its axial position relative to the supporting coupler element is adjustable in its assembled state. It is considered important for the proposed safety element to thus achieve the adjustability of the axial position of the multiple components arranged in series in the assembled state. The relevant components are push rods, locking elements, and locking regions. They should be arranged with as little clearance as possible or with small gaps defined between them. The push rods and locking elements are located in the housing assigned to one coupler element, while the locking regions are assigned to another coupler element. This creates a certain positional tolerance in the axial direction between the components, which can be compensated for by means of the adjustability of the housing.

[0023] The aforementioned measures are not only considered as solutions dependent on the aforementioned basic tasks, but also as solutions to independently invented problems arising from positional tolerances of the components. Therefore, starting from the preamble of claim 1, a safety element is proposed herein, additionally provided with the aforementioned adjustment device for the housing, to adjust its axial position relative to the carrying coupler element and indirectly adjust the axial positions of the component push rod, locking element, and locking area relative to each other.

[0024] The aforementioned independent solution for the adjustability of the component is supplemented by constructing the snap-in area as a replaceable snap-in area element having a fixed positioning aid, wherein the positioning aid, in the assembled state, works in conjunction with the stop device of the relevant coupler element.

[0025] Advantageously, in a coupler with multiple safety elements, each of the locking elements (e.g., a ball) can contact a corresponding one of the locking region elements without having to consider the alignment of the two coupler elements, since, for example, only one locking region element is adapted to each locking element.

[0026] Advantageously, a guide bushing is provided, which, in the assembled state, guides the pushrod and / or the locking element, wherein the guide bushing is concentrically assigned to the first coupler element as well as the pushrod.

[0027] Guide bushings can be assigned as separate components or as integrated components to safety elements, such as housing components of safety elements.

[0028] The housing may have a closing element as a housing component, wherein the closing element functions as a corresponding support for the spring device and / or as a guide for the push rod and / or locking element.

[0029] The closure element practically includes a device by means of which its axial position relative to the housing is adjustable. Simply put, the closure element has a guide hole for a pushrod and an edge with external threads. The external threads can be used as a fastening device. Furthermore, the external threads can form the aforementioned device for adjusting the axial position. The external threads of the closure element practically work in conjunction with mating internal threads disposed within the housing, preferably involving fine-pitch threads. Additionally, an integrated stop element, such as an aluminum block, can be provided, embedded in a blind hole arranged transversely to the external threads within the external thread region. The aluminum block extends into the external thread region and only deforms and stops when the external threads are screwed into the internal threads of the housing, similar to the embedded plastic in a DIN 985 self-locking hexagonal nut, which deforms during screwing and acts as a thread stop.

[0030] The spring device may include at least one disc spring, and preferably a group of disc springs consisting of multiple disc springs.

[0031] At least one of the tappet and / or pressure body may have at least one radially extending groove on its steering surface, which functions as a guide for the transmission body in the assembled state.

[0032] The locking element and / or the locking area element are practically made of ceramic material.

[0033] Pressure bodies and / or transmission bodies can be made of ceramic materials.

[0034] Static or stationary pressure bodies, as well as movable pressure bodies, can alternatively be made of metal alloys. Practically, they undergo treatment to provide improved wear resistance. Transmission bodies can also be made of metal alloys and undergo treatment to improve wear resistance. Treatments for these components can be heat treatment, for example, to harden pressure bodies and / or transmission bodies made of steel, or can be in the form of coatings, applying materials that improve wear characteristics, such as chrome plating, especially hard chrome plating.

[0035] Furthermore, practically speaking, the components operate inside the housing in the presence of a suitable lubricant.

[0036] Furthermore, for the tappet, it is proposed that it be assembled in multiple parts from at least one tappet pin and a shoulder element (especially a shoulder ring) to which it can be connected. The shoulder ring may have a tapered working surface, or the tapered working surface may additionally have radial grooves. A suitable connection between the tappet pin and the shoulder ring establishes a defined and fixed fit between the tappet pin and the shoulder ring, especially in the axial direction. The two-piece configuration has the advantage of allowing the shoulder ring to be replaced separately. It is subject to special wear during operation and may need to be replaced when the tappet pin is still usable. Then, the existing tappet pin is simply fitted with a new shoulder ring. In addition, it is feasible to subject the shoulder ring to a treatment specifically designed to improve its wear characteristics, while leaving the tappet pin untreated or subjecting it to another suitable treatment.

[0037] Furthermore, a coupler is proposed comprising two coupler elements rotatable about an axis, the coupler elements being switchable between a coupled-in state and a coupled-out state, wherein torque can be transmitted in the coupled-in state, wherein at least one safety element according to any one of claims 1 to 16 is arranged on a defined diameter and concentrically with the axis of rotation (preferably axial or radial) of the coupler element on one of the coupler elements, and in the case of multiple safety elements, a defined spacing between the safety elements is preferably provided, wherein a corresponding number of engaging region elements are arranged on the same diameter and concentrically with its axis of rotation on the second coupler element, and specifically, at a spacing consistent with the safety elements.

[0038] Advantageously, a circumferential groove is provided on the second coupler element, which, in the coupled state, works in conjunction with the locking element of the safety element. The cross-section of the groove is practically adapted to the cross-section of the locking element, for example, to the cross-section of a spherical locking element. Attached Figure Description

[0039] The invention is illustrated exemplarily in the accompanying drawings, and described in detail with the aid of several drawings. These drawings show: Figure 1 A coupler equipped with six safety elements according to the present invention is provided. Figure 2 A partial cross-sectional view of a safety element according to the prior art, mounted on a coupler and displayed in the coupled state. Figure 3 : Figure 2 A partial cross-sectional view of a known safety element in the fictitious coupling state of the coupler. Figure 4 A partial cross-sectional view of a first embodiment of the safety element according to the invention, mounted on a coupler and displayed in the coupled state. Figure 5 : Figure 4 A partial cross-sectional view of the embodiment in the coupled state in another plane. Figure 6 : Figure 4 and Figure 5 A partial cross-sectional view of the embodiment in the coupled-out state of the coupler. Figure 7 : A perspective view of an alternative strut for a second embodiment of the safety element according to the present invention. Figure 8 : A perspective view of an alternative movable pressure body for a second embodiment of the safety element according to the present invention. Figure 9 : A perspective view of an alternative fixed pressure body for a second embodiment of a safety element according to the present invention. Detailed Implementation

[0040] exist Figure 1 The image illustrates a coupler 1 according to the invention, having two coupler elements 2 and 3 (coupler halves) movable relative to each other, which can switch according to torque. In the current example, coupler elements 2 and 3 are rotatable about the rotation axis 4 of the coupler 1. Therefore, the coupler 1 is a shaft coupler. It is torsional rigid and switchable. It can switch between coupled-in and coupled-out states according to torque.

[0041] Coupler 1 is used, for example, in the drive system of machines, such as those in mining, construction, or conveying technology equipment (e.g., cranes). It is particularly used in applications involving container cranes. Sudden overloads can occur in such machines, endangering machine components (e.g., motors, gearboxes, etc.). To protect these components, the proposed coupler 1 disconnects the power transmission between the two coupler elements 2 and 3, thereby isolating the overload from the machine components and protecting them. Therefore, coupler 1 can be referred to as a safety coupler or an overload coupler.

[0042] In order for the coupler 1 to meet the safety function according to torque, it is equipped with six safety elements 5a according to the invention. Each safety element 5a has a certain performance for transmitting torque. In this example, the total torque that the coupler 1 can transmit is based on the six safety elements 5a, so the coupler 1 has, in principle, six times the performance of a single safety element 5a.

[0043] Safety element 5a is subject to wear. Specific components of safety element 5a that are critical to operational safety are typically inspected periodically and replaced when necessary.

[0044] In order to improve the lifespan of the safety elements 5a according to the invention, they are provided with devices for reducing wear, as described below.

[0045] Coupler element 2 carries six safety elements 5a. For this purpose, the coupler element is constructed in a flange shape. The safety elements 5a are positioned on the coupler element 2 on a circle (pitch circle) coaxial with the rotation axis 4 of the coupler 1. Each safety element 5a is constructed to be rotationally symmetric and has a central axis 6a. Using the central axis 6a, it is positioned on the pitch circle of the coupler element 2. In this example, the central axis 6a of the safety element 5a is arranged parallel to the rotation axis 4 of the coupler 1 or the coupler element 2. Alternatively, the safety elements 5a can also be arranged radially aligned on the coupler element, for example, to obtain a coupler that functions in the axial direction.

[0046] Figure 2 and Figure 3 A safety element 5b, belonging to the prior art, is shown mounted on a coupler element 2 constructed in a flange shape. The coupler element 2 has a mounting plane 7 orthogonal to the axis of rotation 4, and the safety element 5b also has a defined mounting plane 8. In the illustrated assembly state, the mounting plane 8 of the safety element 5b contacts the mounting plane 7 of the coupler element 2. Thus, in this prior art, the relative positions of the coupler element 2 and the safety element 5b are fixed in the axial direction. The safety element 5b includes a push rod 9 within a housing 10, wherein the housing edge 10a defines the mounting plane 8 of the safety element 5b. The push rod 9 is indirectly spring-loaded and presses against a locking ball 11. Figure 2The locking ball 11 engages in the engagement region 12, which is located on the opposing coupler element 3 and can be axially adjusted by means of the adjusting screw 13. The push rod 9 has a pin with a shoulder element 14 in its circumferential direction. The shoulder element 14 is in contact with the ball, which serves as the transmission element 15. Figure 3 The diagram shows the safety element 5b in its out-of-coupling state, in which the cylindrical rest surface 16, which is part of the shoulder element 14, is in contact with the transmission body 15. In this position, the transmission of the spring preload to the push rod 9 is neutralized. To switch from the out-of-coupling state back to the in-coupling state, the push rod 9 must be advanced from the outside, accompanied by the locking ball 11 being pressed into the locking region 12.

[0047] Figure 4 A first embodiment of the safety element 5a according to the invention is shown, which has a self-returning function. By virtue of this function, it can autonomously switch from a coupled-out state to a coupled-in state. For a coupler equipped with this safety element, this means that it can automatically switch from a disconnected state to a coupled-in state of the coupler half. For comparable features, the same reference numerals as previously described are used for simplicity.

[0048] Figure 4 Specifically, it is shown that the safety element 5a is assembled on the coupler element 2 in a manner different from the prior art. The proposed safety element 5a includes a rotationally symmetric pushrod 9 modified relative to the prior art, on which the cylindrical rest surface is replaced with a frustoconical action surface having an angle relative to the axial direction of the pushrod, here 7.5° relative to the central axis of the pushrod 9. Figure 4 The front end 17 of the push rod presses against the spherical locking element (locking ball 11), wherein the push rod 9 is arranged in the housing 10, which has a support for the push rod 9 and allows its axial mobility. The internal structure within the housing 10 of the safety element 5a is at least largely consistent with that according to Figure 2 and Figure 3 The construction is consistent with that of known safety elements. Unlike this prior art, this safety element omits the use of housing edges as mounting planes for fixed positioning on the relevant coupler element 2, and further differs in that the push rod 9 has the aforementioned inclined action surface 49.

[0049] For assembly onto the coupler element 2, the housing 10 is provided with a combined fastening and adjusting device 18, by means of which its axial position relative to the carrying coupler element 2 can be adjusted. The housing 10 is arranged coaxially with the pushrod 9 around the pushrod and has two end sides 10b and 10c. End sides 10b and 10c form supports with support openings L1 or L2, which function as guide supports for the axial movement of the pushrod 9. Seals S1 or S2 are arranged in each support opening. Simply put, the fastening and adjusting device 18 is an external thread 19 provided on the exterior of the cylindrical sidewall 20 of the housing 10. The external thread 19 is practically constructed as a fine-pitch thread. Correspondingly, the coupler element 2 has a complementary internal thread 21 into which the external thread 19 of the housing 10 can be screwed. The threaded connection consisting of the external thread 19 and the internal thread 21 has a dual function: it serves for assembly and fastening on one hand, and for the aforementioned axial adjustability on the other. The axial position of the housing 10 determines the axial position of the push rod 9, which is connected in series with the locking ball 11 and with an associated locking area 12, which is located on another coupler element 3. During assembly, the appropriate screw-in depth of the housing 10 is determined. This is intended to create a gapless fit between the push rod 9 and the locking ball 11, and subsequently between the locking ball 11 and the locking area 12.

[0050] Here, the push rod 9 is also indirectly under a preload, which is generated by a spring device 22 arranged in the housing 10. For this purpose, the spring device 22 includes a butterfly spring assembly 23, which is coaxially arranged around the push rod 9.

[0051] Alternatively, the screw-in depth of housing 10 can be selected such that a slight gap is created between the pushrod / locking ball / clamping area during assembly, for example, so that no gap is achieved only when the machine is preheated and reaches a preset operating state. A specific degree of thermal expansion of the components involved can reduce or eliminate the gap by a defined dimension. During assembly, housing 10 can be screwed in, for example, with a defined torque so that housing 10 is subsequently reversed in the opposite direction at a defined angle, thereby creating a defined gap.

[0052] The final screw-in depth of the housing 10 in the coupler element 2 is practically stopped. A suitable device 24 is provided for stopping this action, such as in... Figure 4In the example, a threaded pin 25 is arranged in the hole 26 of the coupler element 2. When screwed in, the threaded pin 25 presses radially against the external thread 19 of the housing 10 to fix its position relative to the coupler element 2. To protect the external thread 19, an intermediate piece 27 made of aluminum (as a soft metal) is provided in front of the tip of the threaded pin 25. This intermediate piece is pressed against the external thread 19 of the housing 10 without damaging it. The intermediate piece 27 deforms and thus achieves a stopping effect, similar to the plastic of a DIN 985 self-locking hexagonal nut, which deforms during screwing and resists loosening of the threaded connection.

[0053] The locking region 12 of the locking ball 11 for each safety element 5a is arranged on another coupler element 3. In this example, the locking region 12 is configured as a replaceable locking region element 28. The locking region element 28 has an external thread that screws into the internal thread of the coupler element 3. Each locking region element 28 has a locking recess 29, which is a recess with a tapered inner surface 30. In addition, each locking region element has a fixed positioning aid, which in this example includes a radially projecting flange 31. The projecting flange 31 works in conjunction with the radial surface of the coupler element 3 in the assembled state, which acts as a stop device. For the locking region element 28, the correct axial position is always defined. This eliminates the need to place the two coupler elements in a specific rotational position relative to each other before coupling, as is the case in the prior art. The proposed locking region element 28 is manufactured with good enough quality and dimensional accuracy to allow the locking ball 11 of each safety element 5a of the coupler to freely work with each assembled locking region element 28. In this way, the proposed safety element 5a is generally conducive to coupling.

[0054] Figure 5 as well as Figure 6 and Figure 4 Similarly, the first embodiment involves a safety element. It differs from the prior art in that the pushrod 9 has a modified second functional surface of its shoulder element 14 forming an action surface 49, which has an angle relative to the axial direction of the pushrod 9. In this example, the action surface is inclined at an angle α of 7.5° relative to the axial direction of the pushrod 9. In this example, the action surface 49 is arranged circumferentially on the shoulder ring 14a. This results in a frustoconical configuration of the action surface 49.

[0055] and Figure 4 compared to, Figure 5 and Figure 6 The first embodiment is shown in another cross-section, wherein, Figure 5 This involves coupled states, and Figure 6 The display shows the coupler out of service, with pushrod 9 and locking ball 11 in the retracted position; the coupler is disengaged. The locking ball has retracted from the engaged area. Figure 6In the diagram, the locking region element 28 is simplified to be shown aligned with the pushrod and locking ball. However, in practice, the locking region element 28 continues to rotate at this point; during this continued rotation, the locking depth 29 has pushed the locking ball 11 backward until... Figure 6 The location shown. In this regard, Figure 6 It is a simplified theoretical representation of the coupled state, which shows the stuck region (simplifiedly) at the wrong rotational position.

[0056] In addition, Figure 5 The cross-section shows another threaded pin 32 in another pin hole 33 within the coupler element 2, because this cross-section is located at the same level as the other threaded pin 32 in the other threaded pin hole 33 within the coupler element 2. Figure 4 In different cross-sectional planes, the threaded pin 32 has a tapered tip. It is used for the assembly and positioning of the guide bushing 34, which has a V-shaped groove on its outer surface. The tip of the threaded pin 32 is screwed into the V-shaped groove and thereby fixes the position of the guide bushing 34, which guides the locking ball 11 and the front cylindrical end (front end 17) of the push rod 9. For this purpose, the guide bushing 34 has a first cylindrical inner surface 35, which forms a guide for the locking ball 11. A second cylindrical inner surface 36 forms a guide for the front end 17 of the push rod 9. In this example, the locking ball 11 has a larger diameter than the front end 17 of the push rod 9. The two cylindrical inner surfaces 35 and 36 of the guide bushing 34 are adapted to these two mentioned diameters. Between the cylindrical inner surfaces 35 and 36, the guide bushing 34 has a tapered inner surface 37, which acts as a stop to limit the movement of the locking ball 11.

[0057] Coupler element 2 has a larger diameter than coupler element 3, and it houses a shaft seal ring 38 (dust ring) including a sealing lip 39 that abuts against coupler element 3. The shaft seal ring 38 is arranged to prevent contaminants from entering the guide bushing 34 and the engagement area 12.

[0058] exist Figure 5 The cross-sectional view shows two transfer balls 15, each in contact with a stationary pressure body configured annularly as a pressure ring 40. Additionally, an axially movable pressure body is provided, configured as a movable pressure ring 41. Finally, the pushrod 9 has a shoulder element 14, configured annularly as a shoulder ring. This shoulder ring includes two functional surfaces. The first functional surface 42 is an inclined plane configured as a surrounding concave groove 42a. This concave groove is configured such that its cross-section conforms to the configuration or radius of the transfer balls 15. The second functional surface 16a of the shoulder element 14 is formed by a cylindrical rest surface 16, which, in this example, is arranged parallel to the axial direction of the pushrod 9, as in the prior art.

[0059] also Figure 5A spring assembly 22 is shown, comprising six disc springs assembled into a disc spring group 23. In the coupled state shown, the disc spring group 23 is in a slightly preloaded state. At the end side 10c of the housing 10, a housing opening is provided with a closure element 43, which serves as a corresponding support for the disc spring group 23 and includes one of the support openings with a seal S2 for the pushrod. The closure element 43 is designed to adjust or release the preload of the disc spring group 23. For this purpose, the cylindrical inner wall 44 of the housing 10 is provided with an internal thread 45, and the closure element 43 has an external thread 46 that works in conjunction with it. This allows the closure element 43 to be screwed into the housing 10 and press more or less against the disc spring group 23 for preload, or to be left slack. To secure the desired adjustment, the cylindrical surface of the closure element 43 with the external thread 46 is provided with a pocket (simply a radial blind hole 47) containing a soft material, such as an embedded aluminum intermediate 48. The soft material does not have threads, but it comes into contact with and deforms upon the internal thread 45 of the housing 10 during assembly. The deformed intermediate piece 48 serves as a stop for adjusting the position of the closing element 43. The deformed intermediate piece 48 achieves a stopping action, much like the embedded plastic of a DIN 985 self-locking hexagonal nut.

[0060] The spring force of the disc spring assembly 23 acts on the transmission ball 15 through two steering members, namely the static pressure ring 40 and the movable pressure ring 41. The latter then redirects a component of the spring force to the annular shoulder element 14 of the tappet 9. The tappet 9 is thus subjected to a force component that preloads it toward the engagement region 12.

[0061] The safety element is shown to be in the disconnected state of the coupler. Figure 6 In the middle, the pushrod 9 has retracted from the engagement area 12, thereby causing the transfer ball 15 to move radially outward until it goes beyond the first functional surface 42. Now the transfer ball 15a rests against the second functional surface, that is, against the action surface 49 which is inclined at an angle α of 7.5° relative to the central axis of the pushrod 9.

[0062] The spring force emanating from the disc spring assembly 23 continues to press against the movable pressure ring 41, which acts on the transfer balls 15a and imparts a radially inward motion component to them. The transfer balls 15a then turn towards the push rod via the inclined action surface, imparting an axial motion component to the push rod in the forward direction, thereby pushing the locking ball 11 towards the locking region 12.

[0063] Unlike existing technologies, in the coupled state, the inclined action surface 49 immediately transfers the force component and generates forward motion within the pushrod 9 through the transfer ball 15a.

[0064] Due to the gentle inclination angle (acute angle α) of the action surface 49, a spring force is transmitted on the action surface. This transmission is chosen to limit the force component that propels the push rod 9 forward in its axial direction. This is intended to allow the process of the locking ball 11 engaging into the locking region 12 to proceed in a material-protective manner. This force component is arranged so small that it is preferably coupled only at small speed differences. At larger speed differences, a greater forward force is required in the push rod 9, but this would be accompanied by higher material wear, which the present invention aims to prevent. The small forward axial force reduces wear immediately after a failure occurs, when the coupler elements 2 and 3 are still in the process of gradually calming rotation and are subject to frictional contact of the abrasive material due to the remaining speed difference. On the other hand, subsequent commissioning can also be carried out in a material-protective manner.

[0065] In the first scenario, when coupler 1 is coupled out under torque during full-load operation, coupler elements 2 and 3 are initially still rotating, where a certain speed difference quickly emerges. At this time, the locking ball 11 and the engagement area 12 overtake each other, and since they move at different speeds, this specific frictional contact causes material wear. However, because a limited forward axial force component is applied to the pushrod 9 and locking ball 11 according to the invention, wear during this operating phase can be kept at a low level.

[0066] During restart, it is recommended to start from a stationary state with both coupler elements 2 and 3, and slowly restart only the driven coupler element 2 or 3. This allows the limited forward force reaching the push rod 9 to gently press the locking ball 11 into the engagement area 12 of the coupler element 3. Conversely, if the driven coupler element accelerates too abruptly, coupling will fail, and therefore will not occur in practice. The only effective coupling method is to use the proposed safety element to forcibly protect the material.

[0067] Figure 7 An alternative configuration of the grooved push rod 9b is shown, which can replace the push rod 9 of the first illustrated embodiment, thereby producing another embodiment of the safety element 5a according to the invention. The grooved push rod 9b has a cylindrical pin and an annular shoulder element (shoulder ring 14b), which has a design based on Figure 5 and Figure 6 The first embodiment has two functional surfaces. Its push rod 9 has a shoulder element 14 with two functional surfaces. The first functional surface is an inclined surface constructed as a surrounding concave groove 42a. The second functional surface is an action surface 49 having an angle of inclination relative to the axial direction (central axis) of the push rod 9. Also as in the first embodiment, the safety element 5a with the grooved push rod 9b has a self-returning function. Based on self-returning, if the grooved push rod 9b enters the disengaged state, it will be subjected to an axial force that causes it to... Figure 5 It moves in the direction of its coupled state position.

[0068] according to Figure 7 Additional radial grooves 53 are provided, extending on two functional surfaces, with the second functional surface arranged in the region of the working surface 49 (the outer edge of the cone). Since only the grooves 53 interact with the transfer body, in this example, the groove surface of each groove 53 serves as a substitute for the truncated cone working surface 49. Advantageously, the grooves 53 have a... Figure 5 The cone-shaped outer surface of the working surface 49 has the same inclination angle. In the assembled state, Figure 7 The radial groove 53 in the groove acts as a guide for the corresponding transfer element 15 (preferably a rolling element). In this example, the proposed transfer ball 15a is configured as the transfer element. The cross-section of the radial groove 53 is adapted to the configuration of the transfer ball 15a, similar to the raceway of a rolling bearing.

[0069] Another important aspect of this embodiment is reducing the surface pressure between the groove 53 of the transmission body 15 and the shoulder ring 14b. This is achieved by adapting the cross-section of the radial groove 53, as described above, to the cross-section of the transmission body 15 (such as the transmission ball 15a presented herein). The groove 53 forms a device that reduces wear, which has a beneficial effect on the lifespan of the safety element.

[0070] Another advantage is evident here when the safety element 5a switches between coupled-in and coupled-out states. In the first embodiment, this results in adjacent transfer balls 15a changing their distance from each other. Generally, the distance between the transfer balls 15a is greatest in the coupled-out state in all embodiments. Without the lateral guidance via the groove 53, the transfer balls 15a might, and disadvantageously, move closer or further apart in the circumferential direction. By means of... Figure 7 The proposed radial groove 53 guides this situation.

[0071] according to Figure 8 Another measure is proposed, which involves modifying the axially movable pressure body and contributing to a means of reducing wear. The movable pressure body can replace the movable pressure body 41 of the first illustrated embodiment, or it can be used, for example, in conjunction with the grooved push rod 9a in the safety element 5a. The axially movable pressure body is annularly constructed as a pressure ring 41a and has radial grooves 51 for reducing wear, the cross-section of which is also adapted to the configuration of the transmission body 15 (here, the transmission ball 15a). The surface pressure relative to the transmission body 15 is further reduced in the grooves 51, thereby providing a means of reducing wear. To enable the pressure ring 41a to be combined with the grooved push rod 9b, the pressure ring has congruently arranged radial grooves 51 so that the corresponding grooves 53 of the grooved push rod 9b and the grooves 51 of the pressure ring can function as a common guide for the transmission body 15 in pairs.

[0072] With the help of Figure 9 Another measure is proposed, which involves modifying the static pressure body. This static pressure body can replace the static pressure body 40 of the first embodiment, or can be used in conjunction with... Figure 7 The grooved tappet 9b and / or according to Figure 8 The movable pressure ring 41a is used in conjunction with the safety element 5a. Figure 9 The static pressure body is annularly constructed as a pressure ring 40a and has a radial groove 52, the cross-section of which is also adapted to the configuration of the transmission body 15 (here again, the transmission ball 15a). This is for use with the grooved pushrod 9b and / or with... Figure 8 The pressure rings 41a and 40a are combined, and the pressure rings 40a also have radially arranged grooves 52. Thus, each groove 53 of the grooved push rod 9b and / or each groove 51 of the movable pressure ring can work in pairs with each groove 52 of the static pressure ring 40a, creating a common guide for the transmission body 15.

[0073] List of reference numerals 1 Coupler 2 Coupler Components 3 Coupler Components 4. Rotation axis 5a Safety Components 5b Safety Components 6a Central axis 7 Assembly plane 8 Assembly plane 9 tappets 9b Groove Taper 10. Shell 10a Shell edge 10b end side 10c End side (with housing opening) 11. Lock ball 12. Card-in area 13 Adjusting screws 14 Shoulder components 14a Shoulder ring 14b shoulder ring 15. Transmitter 15a Passing the ball 16 cylindrical rest surfaces 16a Second Functional Surface 17. Pin end (taper) 18 Fastening and adjusting devices 19 External thread 20. Columnar sidewalls (shell) 21 Internal thread 22 Spring device 23 Disc spring elements 24 devices 25 threaded pins 26 holes 27 Middleware 28. Components in the insertion area 29. Stuck into the deep excavation section 30 inside 31. Protruding flange 32 threaded pin 33 pin holes 34 Guide bushing 35. Inner surface of the column 36. Inner surface of the column 37. Conical inner surface 38 Shaft sealing ring 39 Sealing Lip 40 Pressure Ring (Static) 40a Pressure Ring (Static) 41. Pressure ring (movable) 41a Pressure ring (movable) 42 First Functional Surface 42a Concave groove (Hohlkehle) 43 Closing element 44. Columnar inner wall 45 Internal thread (housing 10) 46 External thread (closing element) 47 Blind Hole 48. Intermediate components (aluminum) 49. Surface of Action 51 Groove 52 Grooves 53 Grooves L1 support opening L2 support opening S1 sealing ring S2 sealing ring

Claims

1. A safety element (5a) with self-centering properties for a coupling (1) comprising two coupling elements (2, 3), wherein, In the coupled-in state, torque can be transmitted between the two coupler elements (2, 3), wherein, by means of the safety element, the two coupler elements (2, 3) can switch to the coupled-out state and automatically return to the coupled-in state according to the torque, provided that the self-returning safety element (5a) comprises: - A push rod (9, 9b), which is movable in its axial direction by means of a provided support (L1, L2) to provide its coupled-in or coupled-out state in the assembled state of the coupler (1). - A locking element (11) that rests against the push rod (9, 9b). - A spring device (23) by means of which the spring force can be transmitted to the push rod (9, 9b) and further to the locking element (11). - Wherein, the push rod (9, 9b) is provided with a shoulder element (14), the shoulder element protruding radially at the push rod (9, 9b). - Wherein, at least one transmission body (15, 15a) is provided, which works in conjunction with the shoulder element (14) and also in conjunction with at least one pressure body (40, 41, 40a, 41a). - For this purpose, the pressure body (40, 41, 40a, 41a) has a turning surface, and the shoulder element (14) includes two functional surfaces (16a, 42), namely an inclined surface (42a) and a laterally arranged resting surface (16). - Wherein, the transmission body (15, 15a) contacts the inclined surface (42a) of the shoulder element (14) in the coupled state of the coupler (1) in order to transmit the spring force, and the transmission body abuts against the transverse rest surface (16) of the shoulder element (14) in the coupled state of the coupler (1), further provided that, in the assembled state, the push rod (9, 9b) and the locking element (11) are assigned to the first coupler element (2) of the two coupler elements of the coupler (1), and the other second coupler element (3) is assigned to a locking region (12), the locking region being complementary to the locking element (11). - Characterized in that the resting surface (16) of the shoulder element (14) of the push rod (9, 9b) is further formed as an action surface (49), the action surface having an angle relative to the axial direction of the push rod (9, 9b), that is, tilted by an angle (α) relative to the axial direction of the push rod (9, 9b).

2. The safety element (5a) according to claim 1, characterized in that, The angle (α) of the rest surface (16) of the shoulder element (14) is in the range of 3° to 12°, preferably in the range of 5° to 10°, and particularly preferably in the range of 7° to 8°.

3. The safety element (5a) according to claim 1 or 2, characterized in that, The housing (10) is provided with a first axially movable pressure body (41, 41a) and a second pressure body (40, 40a), and the second pressure body (40, 40a) is fixedly arranged relative to the housing (10).

4. The safety element (5a) according to claim 3, characterized in that, Both pressure bodies (40, 41, 40a, 41a) are spring-loaded, at least one of the two pressure bodies (40, 41, 40a, 41a) has an inclined turning surface, each of the turning surfaces is in contact with the transmission body (15, 15a), and the turning surface of at least one of the two pressure bodies (41, 41a) is arranged at an angle relative to the radial plane.

5. The safety element (5a) according to any one of claims 1 to 4, characterized in that, The support portions (L1, L2) of the push rods (9, 9b) are integrated into the housing (10), and the housing (10) has a fastening device (18) configured to simply assemble the safety element (5a) onto the coupler element (2).

6. The safety element (5a) according to any one of claims 1 to 5, characterized in that, The housing (10) is provided with an adjustment device (18) by means of which its axial position relative to the coupler element (2) that bears the load can be adjusted in the assembled state.

7. The safety element (5a) according to any one of claims 1 to 6, characterized in that, The snap-in area (12) is constructed as a replaceable snap-in area element (28), which has a fixed positioning aid (31) that works in conjunction with the stop device of the associated coupler element (3) in the assembled state.

8. The safety element (5a) according to any one of claims 1 to 7, characterized in that, A guide bushing (34) is provided, which in the assembled state is used to guide the push rods (9, 9b) and / or to guide the locking element (11), wherein the guide bushing (34) is also concentrically provided to the first coupler element (2) along with the push rods (9, 9b).

9. The safety element (5a) according to claim 8, characterized in that, The guide bushing (34) is assigned as a separate component or as an integrated component of the safety element (5a), for example, assigned to the housing component (10).

10. The safety element (5a) according to any one of claims 5 to 9, characterized in that, The housing (10) has a closing element (43) as a housing component, which functions as a corresponding support for the spring device (23) and / or as a guide for the push rod (9, 9b) and / or the locking element (11).

11. The safety element (5a) according to claims 5 to 10, characterized in that, The closing element (43) includes a device by means of which the axial position of the closing element relative to the housing (10) can be adjusted.

12. The safety element (5a) according to any one of claims 1 to 11, characterized in that, The spring device includes at least one disc spring, preferably a butterfly spring assembly (23) consisting of multiple disc springs.

13. The safety element (5a) according to any one of claims 1 to 12, characterized in that, The push rod (9, 9b) and / or at least one of the pressure bodies have at least one radially extending groove (51, 52) on their turning surface, the groove serving as a guide for the transmission body (15, 15a) in the assembled state.

14. The safety element (5a) according to any one of claims 1 to 13, characterized in that, The locking element (11) and / or the locking area element (28) are made of ceramic material.

15. The safety element (5a) according to any one of claims 1 to 14, characterized in that, The pressure bodies (40, 41, 40a, 41a) and / or the transmission bodies (15, 15a) are made of ceramic material.

16. The safety element (5a) according to any one of claims 1 to 15, characterized in that, The push rod (9, 9b) is assembled from a push rod pin and a shoulder element that can be connected to it.

17. A coupler (1) comprising two coupler elements (2, 3) rotatable about an axis (4), the coupler elements being switchable between a coupled-in state and a coupled-out state, wherein, Torque can be transmitted in the coupled state, wherein a plurality of safety elements (5a) according to any one of claims 1 to 16 are arranged on a defined diameter and concentrically with the rotation axis (4) of the coupler elements (2, 3) on one of the coupler elements (2, 3), wherein a corresponding number of snap-in area elements (28) are arranged on the same diameter and concentrically with its rotation axis (4) on the second coupler element (2), i.e. at a spacing consistent with that of the safety elements (5a).

18. The coupler (1) according to claim 17, characterized in that, A surrounding groove is provided on the second coupler element (3), which works in conjunction with the locking element (11) of the safety element (5a) in the coupled state.

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