CN201041204Y - Zero collision cog type universal safety clutch - Google Patents

Abstract

The utility model relates to a zero collision jaw type general-purpose security clutch which has a plurality of implementation forms of single or double directions and single or double couplings. The utility model has the characteristics that the security clutch has no overload collision or impact, the working rotating torque is giant, the rotating speed is high, the residual rotating torque is small or near to zero, the volume is small, the utility model is simple and reliable, the manufacture is easy and the service life is long. The utility model is characterized in that an interlocking blocking mechanism which can prevent a steel ball interlocking mechanism to be interlocked under the overload state is installed, and the interlocking blocking mechanism is arranged inside the steel ball interlocking mechanism in the axial direction and arranged inside or outside the steel ball interlocking mechanism in the radial direction; the ascent angel of the blocking working surfaces of the steel ball interlocking mechanism and the interlocking blocking mechanism can guarantee the friction self-locking and the blocking working condition of the contact of the steel ball interlocking mechanism and the interlocking blocking mechanism to be steady, so that the steel ball interlocking mechanism and the interlocking blocking mechanism have the capability of adapting the change of the separation distance automatically and the automatic compensation of abrasion, the rotating mode of the zero collision of all the components is persistently retained under the overload working condition, and the process of the separation block and the interlocking resetting of the interlocking blocking mechanism is absolutely reliable. After the overload is separated, the positive rotation and the reverse rotation can realize the interlocking resetting of the clutch simply, conveniently and automatically.

Description

Zero-collision jaw-type universal safety clutch

Technical Field

The utility model relates to a clutch in the mechanical transmission field, in particular to a jaw type safety clutch with torque limiting function.

Technical Field

Conventional safety clutches (also referred to as torque limiters) are of three types, shear pin, nested and friction. Compared with other two forms, the embedded jaw type safety clutch has the advantages of simple structure, reliable work, high action precision in overload, easy regulation of limited torque, convenient maintenance, no relative slip of the main and driven shafts after connection, no back clearance transmission torque, quick recovery of normal transmission after overload, no possibility of failure due to friction heat and the like. However, in the conventional dog clutch, in the working state after overload, the axial pressure and the working torque of the spring force the dogs of the driving dog and the driven dog rings to generate continuous impact type slipping phenomenon, which causes excessive wear of the dogs and even extreme conditions such as dog breakage, especially the impact generated at the moment when the driving dog and the driven dog rings are disengaged. Therefore, the application range of the conventional dog clutch is greatly limited, and the excellent characteristics of the conventional dog clutch cannot be exerted, and it has been widely considered in the industry that it can be used only in shafting transmission parts with low rotation speed (about 150-200 rpm), low load (about 4-400N · m), and low rotational inertia of the driven part, such as in light industry and food industry (see article "improved design of dog clutch", wanghai, mechanical design, 1998 year 03).

In order to exert the performance advantages of the jaw type safety clutch and overcome the inherent structural defects, the jaw type high-speed safety clutch with the application number of 96213275.6 is improved by the utility model, the slipping phenomenon of the impact type is eliminated by completely removing the elastic embedding force after overload, the abrasion is reduced, the service life is prolonged, and the application range is expanded. However, there is still the disadvantage that, due to structural constraints, the possibility of harmful impacts not being absolutely eliminated, but rather rigid back impacts on the axial support nut; because the key control part cannot be automatically compensated after being worn, the consistency and the reliability of the system are necessarily reduced after a plurality of overload actions; meanwhile, the axial length and the complexity of the torque adjusting mechanism are increased, and the torque adjusting range is narrowed; the original advantage of rapid recovery of transmission after overload is changed, manual recovery and resetting are needed after each overload, time and labor are wasted, the requirement on maintenance space is more directly severe, and a part of application range is reduced virtually.

SUMMERY OF THE UTILITY MODEL

The utility model aims at overcoming the technical prejudice that the industry exists for a long time, provide one kind and eliminated traditional tooth and inlay the general safety clutch of the zero collision tooth that safety clutch inherent shortcoming is strikeed, make it possess not have the overload and strike, no continuous impact wear, long-life, simple structure, low in manufacturing cost resumes swift, convenient and automatic after the overload, does not receive the mounted position restriction, the high rotational speed, the advantage of big torque.

Another object of the present invention is to provide a universal safety clutch with zero-collision jaw-type axial dual clutch, which has the characteristics of doubled transmission torque and smaller residual torque after overload.

Before describing the technical scheme, the related nouns or concepts are explained as follows:

belongs to a main ring: a rotating member rigidly attached by an attached stop ring or an attached stop ring.

Reference ring: a rotating member as a reference object for which the stopper ring is relatively stationary in the fitting operation state; the end face thereof which directly faces the blocker ring in the axial direction is called a reference end face, and the cylindrical face which directly faces the blocker ring in the radial direction is called a reference cylindrical face.

Blocking the working surface: after the axial separation of the block fitting means, the crest portion of the tooth for abutting contact between the radial teeth of both the ring gears constituting the means is represented by λ.

And (3) blocking working conditions: the blocking teeth of the blocking and embedding mechanisms are opposite to each other and contact with each other, so that the working condition of embedding of other axial embedding mechanisms which are axially positioned outside the blocking and embedding mechanisms is prevented.

δ angle and ρ angle: in the blocking working condition, on one hand, the sliding end face or the cylindrical surface of the blocking ring is in contact with the reference end face or the reference cylindrical surface of the reference ring to form a sliding friction pair (in the case of rigid integration of two blocking rings in the duplex safety clutch, the end face sliding friction condition does not exist), on the other hand, the blocking working face of the blocking tooth is in axial contact with the blocking working face of the auxiliary blocking tooth to form a static friction pair, when the circumferential position of the blocking ring relative to the auxiliary blocking ring is limited by only the static friction pair, the static friction pair is required to be self-locked, wherein the minimum lift angle of the blocking working face capable of ensuring self-locking of the static friction pair is defined as delta, and the maximum lift angle is defined as rho.

Limiting the working surface: a limiting surface is given to the circumferential relative position of the blocking ring. For the control embedded mechanism, when lambda is less than delta, the self-locking can not be realized due to the opposite vertex contact between the blocking teeth of the two sides, so that only the side surface of the blocking tooth and the side surface of the limiting bulge in the middle of the tooth top of the blocking tooth are limiting working surfaces; when delta is more than or equal to lambda is less than or equal to rho, all the side faces and the blocking working faces of the blocking teeth are limiting working faces because the abutting contact between the blocking teeth of the two sides can be reliably self-locked.

Full-tooth embedding depth: when the axial fitting mechanism is completely fitted, the axial distance from the highest tooth top point of one fitting tooth to the highest tooth top point of the other fitting tooth is obtained.

Minimum barrier height: the blocking engagement means must be separated by a minimum axial distance necessary to achieve the abutting contact between its blocking working surfaces.

Maximum limit embedding depth: the circumferential constraint action of the limiting embedding mechanism is guaranteed to exist, and the maximum distance which can be separated in the axial direction of the embedding mechanism is blocked. For the control embedding mechanism, the depth is the axial distance between the highest points in the upper boundaries of the limit working surfaces of the two embedding parties in the complete embedding state.

Initial separation height: under the action of the elastic embedding force, the axial embedding mechanism has the minimum axial separation distance which is required by the components of the axial embedding mechanism to realize the relative rotation of the axial embedding mechanism. The distance must be zero in the opposite direction permitted by the design, whereas the distance may be non-zero.

Entrance margin K of the blocking fitting mechanism: when the influence of other embedding mechanisms and the circumferential freedom of the blocking ring are not considered, the maximum circumferential angle of the gear rings forming the blocking embedding mechanism can be continuously staggered from the minimum blocking height on the premise of not influencing the axial embedding of the mechanism.

In the present invention, when the two sides of the assembly of one embedding mechanism respectively use the two sides of the assembly of the other embedding mechanism as the axial supporting base, it is called that the previous embedding mechanism is located inside the latter embedding mechanism in the axial direction, and vice versa. In addition, the utility model discloses the short for of independent barrier ring is "barrier ring".

In order to achieve the above purpose, the utility model discloses a zero collision jaw type universal safety clutch, by the first engaging element, the second engaging element, spring and adjusting nut based on same axial lead constitution, the first engaging element is fixed with the first pivot, the second engaging element can move axially, its part non-gomphosis surface is formed with the characteristic curved surface that can transmit torque, the first engaging element and the second engaging element axially relatively constitute the work gomphosis mechanism that has transmission torque and overload separation dual function, the spring is directly or indirectly installed between second engaging element and adjusting nut, provide axial gomphosis power for the work gomphosis mechanism, and finally form direct or indirect axial restriction and support to the spring by adjusting nut; the method is characterized in that: 1) The blocking embedded mechanism is used for preventing the axial embedding of the working embedded mechanism in an overload separation state, is positioned in the working embedded mechanism in the axial direction, is positioned in or out of the working embedded mechanism in the radial direction, and is formed by axially embedding a blocking ring and an auxiliary blocking ring, and the peripheral directions of the embedded end surfaces of the two rings are provided with the same number of radial blocking teeth with the axial blocking effect; the minimum blocking height of the blocking embedding mechanism is larger than the initial separation height of the working embedding mechanism in two rotation directions and smaller than the full-tooth embedding depth of the working embedding mechanism; the secondary blocker ring being rigid integral with an owner ring, the owner ring being the second engagement element or the first engagement element; the stop ring is supported by the reference ring in a single direction, and the sliding end face of the stop ring and the reference ring form a circumferential free sliding friction pair; the reference ring is a first or second engagement element opposite the owner ring of the auxiliary blocker ring; 2) The limiting embedding mechanism is arranged for limiting the circumferential relative position of a blocking ring in the blocking embedding mechanism and consists of the blocking ring and an auxiliary limiting ring; the auxiliary limiting ring and the auxiliary blocking ring are rigidly integrated into the same ring, the limiting embedding mechanism and the blocking embedding mechanism are superposed to form a control embedding mechanism, in the control embedding mechanism, the blocking teeth are also limiting teeth, the auxiliary blocking teeth are also auxiliary limiting teeth, the blocking working surfaces of the tooth tops of the two are spiral surfaces with the lead angle not more than rho, and a limiting bulge is formed in the middle of at least one of the tooth tops; meanwhile, the maximum limit embedding depth of the limit embedding mechanism is larger than the full-tooth embedding depth of the working embedding mechanism.

Reach the utility model discloses another purpose dual zero collision tooth inlays general safety clutch of formula, its characterized in that: two embedded end faces are fixed on the first rotating shaft in a circumferential direction towards the first joint elements which are opposite to each other, two second joint elements capable of moving axially are fixed with the second rotating shaft in a circumferential direction, part of non-embedded surfaces of the two joint elements are respectively provided with a characteristic curved surface capable of transmitting torque, the two joint elements are respectively and axially embedded with the two first joint elements to form a working embedded mechanism, and the two working embedded mechanisms are synchronously in a separated state or an embedded state. The non-engaging end faces of the two second engagement elements are each acted upon by a spring which provides the two operative engagement means with an axial engagement force and is finally axially restrained and supported by the adjusting nut. In order to prevent the axial embedding of the two working embedding mechanisms in an overload separation state, two blocking embedding mechanisms are arranged, and the two mechanisms respectively form a group of sub-clutch mechanisms with one working embedding mechanism; in each group of sub-clutch mechanisms, the blocking embedding mechanisms are radially positioned inside or outside the working embedding mechanisms and are formed by axially embedding a blocking ring and an auxiliary blocking ring, and the same number of radial blocking teeth with axial blocking effect are arranged on the periphery of the embedding end surfaces of the two rings; the minimum blocking height of the blocking embedding mechanism is greater than the initial separation height of the working embedding mechanism in two rotation directions and less than the full-tooth embedding depth of the working embedding mechanism; the secondary blocker ring is rigidly integral with an owner ring, which is the second or first engagement element. In each group of sub-clutch mechanisms, a limit embedding mechanism for limiting the circumferential relative position of a blocking ring in the blocking embedding mechanism is also arranged and consists of the blocking ring and an auxiliary limit ring; the auxiliary limiting ring and the auxiliary blocking ring are rigidly integrated into the same ring, the limiting embedding mechanism and the blocking embedding mechanism are superposed to form a control embedding mechanism, in the control embedding mechanism, the blocking teeth are also limiting teeth at the same time, the auxiliary blocking teeth are also auxiliary limiting teeth at the same time, the blocking working surfaces of the tooth crests of the two are spiral surfaces with the rising angle not larger than rho, and a limiting bulge is formed in the middle of at least one of the tooth crest surfaces; meanwhile, the maximum limit embedding depth of the limit embedding mechanism is larger than the full-tooth embedding depth of the same working embedding mechanism.

In the duplex safety clutch, two blocking embedding mechanisms are axially and respectively positioned in one group of sub-clutch mechanisms, two independent blocking rings are axially and unidirectionally supported by the reference end surface of a reference ring, and the reference ring is served by a first engaging element or a second engaging element; meanwhile, the two stop rings can realize long-term related linkage of the circumferential positions of the two stop rings by means of an axial embedding mechanism between the two stop rings.

In addition, the blocking teeth of the two blocking rings can be respectively formed on the two end surfaces of the same annular base body and the inner cylindrical surface or the outer cylindrical surface on the same side in a mode that the tooth tops face towards each other, so that the two blocking and embedding mechanisms are axially connected in a mode that the two blocking rings are rigidly integrated and axially supported with each other, are axially and simultaneously positioned in the two working and embedding mechanisms, and use the first connecting element as a reference ring of the blocking ring and use the second connecting element as an auxiliary main ring of the auxiliary blocking ring. Likewise, the object of the two first joining elements being rigidly integral can also be achieved by sharing one annular base body.

In order to make the blocking engagement mechanism work perfectly and reliably, it is preferable to impose a constraint on the blocking ring so as to force it to rest relatively on the reference end face or the reference cylindrical surface of the reference ring in the engaged state.

When the bidirectional blocking mechanism has a bidirectional blocking function, the initial separation height of the working embedding mechanism in two rotation directions is zero, the blocking working surfaces are respectively and correspondingly formed on two sides of each tooth crest surface in the blocking tooth mechanism, and the entrance margin K of the blocking embedding mechanism conforms to the inequality K & gttheta _c +θ _f + η. The relevant parameters are defined as follows:

θ _c : the circumferential included angle corresponding to the top surface of the working tooth on the first jointing element,

θ _f : the circumferential included angle corresponding to the top surface of the working tooth on the second jointing element,

eta: due to the lead angle and the circumferential clearance of the working embedding mechanism.

More simply, the side surface of the limit bulge in the control embedding mechanism on the same side with the blocking working surface is preferably made into a spiral surface with the lead angle of beta, and the lead angle is more than or equal to delta and less than 180 degrees. When the | delta | is less than or equal to beta and less than 90 degrees to phi, if an embedding type limiting mechanism which can forcibly limit the blocking ring at a specific circumferential position relative to the reference ring, namely a blocking ring rotation stopping mechanism, is arranged between the reference ring and the blocking ring, and when the mechanism is embedded, the blocking ring loses axial blocking capability, then the aim of forced embedding can be easily realized. Here, Φ is a friction angle of a friction pair formed between a side surface of the stopper protrusion and the blocking tooth or the subsidiary blocking tooth. The blocking ring rotation stopping mechanism may be a pin-slot type embedding mechanism comprising axial or radial through holes on the reference ring reference end surface or the reference cylindrical surface, corresponding grooves or split ring gaps on the corresponding friction surfaces of the blocking ring, and a rotation stopping pin.

In addition, the safety clutch can also be integrally packaged in a shell, the shell consists of a shaft sleeve, a transmission ring, an annular end cover and a threaded end cover replacing an adjusting nut, a characteristic curved surface capable of transmitting torque is formed on the inner hole surface of the shaft sleeve, the outer cylindrical surface of the shaft sleeve is circumferentially fixed or directly and rigidly integrated with the inner hole surface of the first joint element, a characteristic curved surface capable of transmitting torque is formed on the outer surface of the transmission ring of the annular sleeve, the inner hole surface of the transmission ring is circumferentially fixed with the outer cylindrical surface of the second joint element in a spline connection mode, the annular end cover is sleeved on the shaft sleeve in a supporting spring mode and is fixedly connected to one end surface of the transmission ring, and the threaded end cover is sleeved on the shaft sleeve from the other end and is connected with threads on the inner ring surface of the corresponding end of the transmission ring in a threaded connection mode.

The utility model discloses in, through adding the blocking mosaic mechanism that plays the axial and stop the effect in to work mosaic mechanism to and stop ring spline mechanism, realized well the utility model discloses a purpose. Namely, when the rising angle lambda of the blocking working face is less than delta, the limit bulge in the blocking embedding mechanism is utilized, or when the rising angle lambda of the blocking working face meets the relation delta which is less than or equal to lambda which is less than or equal to rho, the self friction self-locking characteristic of the blocking working face is utilized, or the comprehensive utilization is carried out, and the circumferential relative position in the blocking embedding mechanism under the blocking working condition is well maintained, so that the purposes of maintaining the blocking relation, preventing the embedding resetting of the working embedding mechanism in the overrunning state and eliminating the impact or collision are achieved; the blocking capacity is forcibly released by means of reverse rotation or a blocking ring rotation stopping mechanism, so that the aims of quick, convenient or automatic recovery of embedding after overload, no limitation of an installation position and long service life are well fulfilled. Meanwhile, the inherent properties of high rotating speed and large torque are naturally released. And only a simple stop ring is added, and the clutch structure still has the characteristics of simplicity and low manufacturing cost. In addition, through the duplex two-jaw universal safety clutch and the mode of making the two stop rings into a whole in rigidity to thoroughly eliminate the end face sliding friction resistance, the purpose of another utility model which has double transmission torque and smaller residual torque after overload is well achieved.

In the aspect of torque transmission ability, operating speed, overload frequency, continuous overload time, residual torque coefficient, life-span and range of application, the utility model discloses friction formula or spring steel ball formula safety clutch for prior art has the advantage that the unit is comparable.

Drawings

Fig. 1 is an axial cross-sectional view of a first embodiment of the present invention.

Fig. 2 is a schematic view of the second engaging element in fig. 1, (a) is an axial half sectional view of a right side view of (b), (b) is a front view, and (c) is an enlarged view of a radial projection of a partial tooth profile in the T direction in (b).

Fig. 3 is a schematic view of the blocker ring of fig. 1, (a) is a front view, (b) is a left side view, and (c) is an enlarged expanded schematic view of a partial radial projection of the T direction in (a).

Fig. 4 is a partial development view of radial projections of the tooth profiles of the respective interlocking mechanisms in fig. 1 on the same outer cylindrical surface under different working conditions, (a) is a tooth profile relationship diagram of the working interlocking mechanism in an interlocking state, (b) is a tooth profile relationship diagram of the control interlocking mechanism corresponding to (a), (c) is a tooth profile relationship diagram of the working interlocking mechanism under a blocking working condition, (d) is a tooth profile relationship diagram of the control interlocking mechanism corresponding to (c), (e) is a tooth profile relationship diagram of the one-way control interlocking mechanism corresponding to (c), and (f) is a partial enlargement diagram of (a), and an arrow represents a relative overload rotation direction.

FIG. 5 is a schematic view of all possible abutting contact relationships of the blocking and embedding mechanism with various tooth shapes in the blocking working condition, which are shown in the form of a radial projection expansion diagram, wherein the left side contour lines in all the figures belong to the blocking rings, and the right side contour lines in all the figures belong to the auxiliary blocking rings; (a) The control fitting mechanisms are variously described in (a) to (c) which show three specific tooth profiles, (d) to (i) which show all tooth profiles when | δ | < λ ≦ ρ, and (e) to (i) which show coplanar specific tooth profiles when β = λ; (j) The tooth profile is suitable for a radial type position-restricting fitting mechanism.

Fig. 6 is an axial half-sectional view of the second embodiment of the present invention.

Fig. 7 (a) is an axial sectional view of a third embodiment of the present invention, and (b) is an axial half-sectional view of the second engaging element in (a).

Fig. 8 (a) is an axial sectional view of a fourth embodiment of the present invention, and (b) is a schematic view of a fitting end surface of the first engaging element in (a).

Fig. 9 is an axial sectional view of the simplest embodiment of the present invention.

Fig. 10 is an axial cross-section of a sixth embodiment of the invention in the form of a package.

Fig. 11 is an axial cross-sectional view of a seventh embodiment of the present invention, which is sealed and forcibly fitted.

Fig. 12 is an axial cross-sectional view of an eighth embodiment of the invention in another package form.

Fig. 13 is an axial cross-sectional view of a specific application of the present invention to a coupling.

Fig. 14 (a) is an axial sectional view of a ninth embodiment of the present invention, (b) is an axial sectional view of a middle stopper ring in (a), and (c) is a simplified sectional view of an axial symmetric plane T-T in (b).

Fig. 15 is an axial cross-sectional view of a tenth embodiment of the invention in packaged form.

Fig. 16 (a) is an axial sectional view of an eleventh embodiment of the present invention, (b) is an axial sectional view of the left blocker ring in (a), (c) is an axial sectional view of the right blocker ring in (a), and (d) is a simplified left side view of (c).

Fig. 17 is an axial sectional view of a twelfth embodiment of the present invention having tension springs.

Fig. 18 is an axial cross-sectional view of a thirteen embodiment of the present invention in an encapsulated form.

Fig. 19 (a) is an axial sectional view of a fourteenth embodiment of the present invention, (b) is a front view of the second engaging element in (a), and (c) is a sectional view of a T-T section in (b).

Fig. 20 (a) is an axial cross-sectional view of a fifteenth embodiment of the present invention, (b) is a simplified front view of the left blocker ring in (a), (c) is an axial half-sectional view of the left view of (b), and (d) is an axial half-sectional view of the right blocker ring in (a).

Fig. 21 is an axial cross-sectional view of a sixteenth embodiment of the present invention.

Fig. 22 is an axial sectional view of a seventeenth embodiment of the present invention.

Fig. 23 (a) is an axial sectional view of an eighteenth embodiment of the present invention, (b) is a front view of a middle stopper ring in (a), (c) is an axial sectional view of a middle link ring in (a), and (d) is a front view of (c).

Detailed Description

The essential description is as follows: in the text of the present description and in all the figures, identical or similar components and features thereof are provided with the same reference signs, so that the present description is given in detail only when they appear for the first time and will not be given repeated detailed description when it appears again thereafter.

Fig. 1 to 4 show a first embodiment of the invention, a two-way safety clutch in the form of a shaft-to-shaft transmission. As shown in fig. 1, the first engagement element 50 is a reference ring of the blocker ring 100 and the second engagement element 80 is a primary ring of the secondary blocker ring. The first engaging element 50 and the second engaging element 80 constitute a working fitting mechanism. The first and second rotary shafts are fixed (not shown) to the first and second coupling members 50 and 206, respectively, by flat keys. The second engagement element 80 is sleeved over the second hub 206 with spline teeth circumferentially fixed therebetween. The fitting spring 160 is mounted between the non-fitting end surface of the second engaging element 80 and the spring seat 162, and the adjustment nut 164 is screw-coupled to the outer end side of the second boss 206, is indirectly coupled in the axial direction with the first engaging element 50, and performs axial support and adjustment of the fitting spring 160 via the spring seat 162. The blocking ring 100 is located radially inside the working engagement means, and with the secondary blocking ring forms a blocking engagement means, the sliding end face 124 of which faces the reference end face 70 of the first coupling element 50. The restraining spring 120 is interposed between the blocker ring 100 and the end face of the external spline teeth of the second hub 206. The anti-rotation pin linkage ring 180 is fitted over the cylindrical surface of the first engagement element 50 outside the non-engagement end, axially spaced by a return spring 186 and axially restrained by a snap ring 210. Three axial rotation stop pins 182 are uniformly distributed at one end of the rotation stop pin linkage ring 180, the three rotation stop pins 182 are respectively embedded in three rotation stop pin mounting holes 188 on the first joint element 50, and the top surface of the rotation stop pin linkage ring is close to but not contacted with the stop ring 100.

Fig. 2 shows a specific structure of the second engaging element 80. The second working teeth 82 are radial teeth having a trapezoidal cross section, which are uniformly distributed on the outer ring side of the fitting end surface thereof, and the auxiliary blocking teeth 142 are uniformly distributed on the inner ring side of the fitting end surface thereof. The auxiliary blocking tooth 142 is radially connected with the second working tooth 82 into a whole, the tooth crest 144 of the auxiliary blocking tooth is higher than the tooth crest 84 of the second working tooth, the blocking working surface 148 of the auxiliary blocking tooth is a spiral surface with the lead angle of lambda, and the lead angle is more than delta and less than lambda and less than rho. To simplify construction and ease of manufacture, the secondary blocker tooth flank 150 and the tooth flank 146 are completely coplanar with the second working tooth flank 88 and the tooth flank 86, respectively, and the secondary blocker tooth 142 is therefore divided into two parts, the part of the intermediate tooth flank corresponding to the tooth flank 144 of the second working tooth gullet being no longer present. The layout and profile of the mating end face of the first engagement element 50 is identical to that of the second engagement element 80, except that there is no secondary blocking tooth, and the working tooth top face has a curvature.

As shown in fig. 3, a spring-loaded shoulder 128 is formed within the annular base 112. The blocking teeth 102 of the blocking ring 100 are uniformly distributed on the outer ring side of the ring-shaped base body 112, and a limit protrusion 114 is formed in the middle of the tooth top thereof. Each blocking tooth 102 is symmetrically provided with two spiral blocking working surfaces 108 with the lead angle of lambda, two tooth side surfaces 110, two limiting convex spiral side surfaces 118 with the lead angle of beta, | delta | is more than or equal to beta and less than 180 degrees, and a limiting convex top surface 116. The end with the stop face 108 is the engaging end face of the stop ring, the other end is the circumferential sliding end face 124 of the stop ring, and the upper rotation stop groove 126 is the stop tooth groove. Determining the circumferential position, circumferential width, and circumferential width of the rotation stop stud mounting hole 188 with such an effect that the rotation stop stud 182 is fitted into the rotation stop groove 126, the position at which the stopper ring 100 stays must result in the stopper fitting mechanism failing to successfully block the axial fitting of the working fitting mechanism.

As shown in fig. 4 (a), (b) and (f), the first engaging element 50 and the second engaging element 80 constitute a two-way working fitting mechanism, and the barrier ring 100 and the subsidiary barrier ring constitute a control fitting mechanism which is both a barrier fitting mechanism and a limit fitting mechanism. The entrance margin K of the fitting means is controlled to be (the relevant symbol represents the circumferential angle between the corresponding points)

Here, K > θ _c +θ _f + eta; axial separation distance greater thanThe circumferential degree of freedom of the positive locking engagement defined by the blocking running surface 108 is then naturally greater than K. In the state of being embedded with the other end of the body,wherein D is _t Representing the initial separation height of the working engaging mechanism in the non-designed overload direction, in this case a bidirectional overload, D in both directions _t Are all constantly zero; d _c Representing the full-tooth engagement depth of the working engagement mechanism,

represents the minimum blocking height of the blocking and fitting mechanism (the horizontal line symbol represents the axial distance, the same applies below),

representing the maximum limit embedding depth of the limit embedding mechanism. Fig. 4 (c) and (d) show the tooth profile relationship of the fitting mechanisms in an overload condition, and fig. 4 (e) shows the tooth profile relationship of the one-way control fitting mechanism corresponding to fig. 4 (c).

It will be understood that in this embodiment, the rotation stop pins 182 and their mounting holes 188 are circumferentially distributed in three, the blocker ring 100 and the secondary blocker ring each have three uniformly distributed identical radial teeth, the secondary blocker tooth 142 circumferentially extends exactly radially of the second working tooth 82, and the arrangement of the blocking tooth gullet as the rotation stop recess 126 is not essential, but is purely for the sake of simplicity of construction and process. In the case of a special case where the auxiliary barrier ring cannot be formed integrally with the main ring, the auxiliary barrier ring can be handled by a method of manufacturing it separately in advance and then rigidly combining it with the main ring by welding or interference fit or the like. Similarly, the restraining spring 120 and the return spring 186 are wave springs, but may be any other type of elastic body.

The present embodiment is further described with reference to fig. 1 and 4 in conjunction with the working process.

In the engaged state, the operating torque is transmitted to the second engagement element 80 via the first engagement element 50 and then to the second sleeve 206 via splines, completing the transmission of torque within the clutch, although the transmission paths may be reversed. In the case of overload in any direction, i.e., when the transmitted torque generates an axial reaction force on the contact surface of the first working tooth 52 and the second working tooth 82 which is greater than the fitting pressure provided by the spring 160, as shown in fig. 4 (a) or 4 (f), the second working tooth 82 is inevitably separated axially against the elastic pressure, and is withdrawn from the fitting position, so that the fitting relationship of the entire working fitting mechanism is not present, and the internal torque transmission path between the two engaging elements is disconnected.

After the overload separation begins, the overload separation is carried out due to parameters

When the axial separation distance of the second engaging element 80 with respect to the first engaging element 50 reaches D _c At this time, the lowest point a of the upper dependent blocking tooth blocking face 148 has already axially passed the lowest point G of the blocking tooth blocking face 108, as shown in fig. 4. And since the blocking ring 100 is constrained by the spring 120 to rest on the first coupling element 50Thus, as long as the entrance margin K blocking the engagement mechanism is not far from its lower limit, the process of disengagement in rotation is sufficient to ensure that D is achieved in the first synchronization controlling the axial disengagement distance of the engagement mechanism _c The auxiliary blocking tooth blocking working surface 148 reliably jumps over the blocking tooth blocking working surface 108, and the interference and stable self-locking static friction relationship are established, so as to drive the blocking ring 100 to circumferentially slide on the reference end surface 70 of the first engaging element 50, thereby stopping the axial separation process between the two engaging elements at the maximum separation distance. Therefore, the axial distance between the second engaging element 80 and the first engaging element 50 is constant at zero, and both are in a zero-contact overrunning sliding friction condition without any impact and magnetic collision, particularly at the moment of separation. This will significantly reduce the wear rate of the two, eliminate noise, and prolong life. In addition, the top surfaces of the first working teeth or the second working teeth can be made into a step shape with a high inner end, so that the average sliding friction radius and the residual torque under the overload working condition are obviously reduced. The residual torque coefficient will be much smaller than the sliding friction coefficient.

Since the bidirectional barrier fitting mechanism is used, the security clutch of the present embodiment has the characteristics of no impact and no collision in both directions. It should be emphasized that the helicoidal characteristic of the blocking face in the control fitting mechanism is a prerequisite for ensuring zero collision of the working teeth in the blocking condition, i.e. λ > 0 must be required. And the lambda is more than or equal to the delta is a necessary condition for blocking friction self-locking between working surfaces in a blocking working condition, and is also a necessary condition for blocking the embedding mechanism to have the capability of self-adapting to the axial separation distance and the capability of automatically compensating abrasion of various shafts in a certain range, so that the overall performance, the reliability and the service life of the safety clutch are obviously improved, and the compensation amount can be given as required during manufacturing. Particularly, when delta is more than 0 and lambda is more than 0 and less than delta, the auxiliary blocking tooth 142 can slide and climb relatively because the two blocking working surfaces which are contacted with each other in an opposite mode cannot be self-locked, and the axial separation distance of the blocking embedding mechanism is larger than D _c Until encountering the stop lug 114. That is, with proper design, we can getSo as to lead the two working teeth to have no contact with each other. In addition, the self-locking relationship between the blocking working faces only exists in the corresponding overload rotation, that is, the relative rotation in which the lift angle of the blocking working face in the opposite contact is made positive, but never exists in the relative rotation in which the lift angle is made negative, because the lift angle λ ' = - λ < - δ |, λ ' in the latter rotation completely falls outside the lower limit of the self-locking requirement λ ' ≧ δ. Thus, by changing the relative rotational direction of the two engagement elements in the blocking condition, the original self-locking relationship between the blocking faces will be immediately lost, and the blocking ring 100 will no longer follow the integral rotation of the secondary blocking tooth 142, but will rest on the reference ring base face 70.

Therefore, for the fitting reset of the safety clutch, one method of the present embodiment is a reverse method, and the prerequisite for implementation is that K > θ _c +θ _f + η. At this time, no matter what extreme situation occurs,at most, if the driving element of the safety clutch rotates reversely by one tooth, that is, the first engaging element 50 rotates relatively to the second engaging element 80 opposite to the overload relative rotation and rotates by one tooth, the auxiliary blocking tooth 142 can slide off the blocking working face 108 of the blocking tooth 102 and synchronously engage and reset with the second working tooth 82, and the reverse separation blocking situation can not occur, especially when a one-way blocking engagement mechanism is used, the blocking tooth notch rotates synchronously with the auxiliary blocking tooth 142, as shown in fig. 4 (e). Another method of the fitting reduction in the present embodiment is a rotation stop method. That is, while maintaining the overload rotation condition, the lock pin coupling ring 180 is axially pressed to overcome the axial reaction force of the spring 186, and then the lock pin 182 is axially pressed into the lock recess 126 on the sliding end face 124 of the blocking ring, and the blocking ring 100 is circumferentially stopped at a specific relative position where it loses the axial blocking ability, so that the auxiliary blocking tooth 142 is forced to slide and climb relative to the blocking tooth 102, and after passing over the limit projection 114 at the middle thereof, it is inserted into the next tooth groove of the blocking ring 100, thereby achieving the purpose of the controllable engaging and returning of the clutch.

Obviously, the utility model discloses a safety clutch's gomphosis resets, and the mechanism is simple, and the process is reliable, easily realizes automation and remote control through reversal or electricity, liquid, and the performance that will make tooth-embedded safety clutch obtains strideing across type promotion, increases its operating speed, torque and adaptable overload frequency by a wide margin to and the space that the mountable was arranged. The application field and range of the clutch are remarkably expanded, and the clutch becomes a universal safety clutch.

It should be noted that the stop ring detent mechanism and the detent method of controlled engagement reset are optional structures or methods. If this construction and method is used, the angle of rise β of the flank 118 of the stop lobe at the tip center of the blocking tooth must satisfy the inequality: | δ | ≦ β < 90 ° - φ, and is best with the side 118 coplanar with the barrier working surface 108, i.e., β = λ. Alternatively, the rotation stop mechanism may be of a radial type or the like, and the embodiment shown in fig. 14 may be referred to for the related description.

If the present embodiment is a pure one-way safety clutch, a blocking fitting mechanism having only a one-way blocking function may be employed, as shown in fig. 4 (e), in which case the circumferential degree of freedom of the fitting mechanism may be zero. In addition, the constraint of the blocker ring 100 is not necessary in this embodiment, but is done for the sole purpose of absolutely ensuring that the blocking engagement mechanism is able to establish an axial blocking relationship within the first time. The restricting manner is not limited to a spring compression manner, and may also be a manner of making all or part of the first engaging element 50 or the blocking ring 100 by using a magnetic material to cause magnetic attraction therebetween, or a manner of making the blocking ring 100 into an elastic opening ring with a shoulder, or an elastic opening ring with a conical revolution surface, or a manner of applying a radial elastic force to a partial conical revolution surface of the blocking ring 100, such as a radial pressing manner of a spring ball, an elastic snap ring, or the like. The blocking ring 100, its restraining method, the blocking engagement mechanism, the limiting engagement mechanism, their relationships with other members, and the descriptions regarding δ and ρ are described in more detail in the invention patents "basic dog self-locking differential" and "pressing dog single-and two-way overrunning clutch" proposed by the applicant, which are incorporated by reference in their entirety, and will not be described in detail herein.

Fig. 5 shows all possible abutting contact situations of the blocking engagement with various tooth profiles in the blocking operating mode. In FIGS. 5 (d) - (i), | δ | < λ ≦ ρ, all tooth profiles of the fitting control mechanism are shown that can achieve zero contact friction at the tooth tip of the separation tooth and have a wear compensation function. Fig. 5 (d) shows a case where β ≠ λ; fig. 5 (e) - (i) show the special case where all are β = λ and the tooth flank 118 of the stop tooth crest middle limit projection is coplanar with the stop running surface 108, which is advantageous for manufacturing. Fig. 5 (a), 5 (b) and 5 (j) correspond to various tooth relationships with impact wear after overload separation.

It should be noted that, since the operation principle, relationship and process of the block fitting mechanism and the like are completely the same, the following embodiments will not be repeated, and only the specific structure will be explained as necessary.

Fig. 6 shows an embodiment in which the blocking engagement means are situated radially outside the working engagement means. Wherein the blocker ring 100 is fitted over the outer cylindrical surface of the first coupling member 50 and constrained against the reference end surface 70 by the spring 120 and the retaining ring 122. The present embodiment has a large residual torque compared to the above embodiment.

Fig. 7 shows an arrangement in which the blocking ring 100 is moved axially. Here, the second engagement element 80 is a reference ring of the blocker ring 100 and the first engagement element 50 is an owner ring of the secondary blocker ring. The relationship and arrangement of the secondary blocker tooth 142 and the first working tooth 52 is exactly the same as that shown in FIG. 2. The blocking ring 100 is seated in an annular recess of the inner ring-side end face of the second working tooth 82, the side end face of which is the reference end face 70. The outer end of the barrier ring 100 is sequentially provided with a wave spring 120 and a restraining snap ring 122, and the snap ring 122 is embedded in a snap ring groove 212 on the outer cylindrical surface at the opening of the annular groove. To complete the necessary restraint of the team blocker ring 100. The anti-rotation pin ring 182 in this example is mounted in a corresponding axial through hole 188 in the second engagement element 80 and is restrained in axial opposition by a return spring 186 therebetween. The operation of the anti-rotation pin linkage ring 180 is performed by means of an intermediate ring 190, both rings having the same structure. In addition, the fitting spring 160 is served by four disc springs, the radial position of which is defined by a positioning ring 166 having a cross-sectional shape of "T". The blocking ring 100 can also be placed on a cylindrical surface outside the second working tooth 82, but is obviously not a good layout.

Fig. 8 shows an embodiment of the present invention having in-situ fitting capability. This embodiment is in the form of a wheel-axle transmission, and the layout of the two engagement mechanisms is completely as shown in fig. 1. The entire clutch is axially confined between the shoulder of the second bushing 206 and the adjustment nut 164 coupled thereto. Between said shoulder and the first coupling element 50a washer 214 is arranged, the adjusting nut 164 compressing the engagement spring 160 via the compression sleeve 168 and being notably axially associated with the first coupling element 50 via the second sleeve 206. The only complete circumferential engagement of the operative engagement means is achieved by the arrangement of a pair of shorter length teeth and grooves. That is, the inner end of one of the working teeth slot 56 of the first engaging element 50 is blocked by the slot stopper 68 and differentiated into the short slot 66, and the length of one of the second working teeth 82 is shortened to differentiate it into the corresponding short working tooth 94. The tooth slot stop 68 is coplanar with the top land 54 of the first working tooth 52. The spline stop 68 may be integrally formed with the first engagement member 50 or may be formed and then rigidly connected thereto by welding or pin-and-hole interference fit. Of course, completely sealing the tooth grooves 66 and providing circumferentially non-equidistant working rings may also be the purpose of achieving a circumferentially unique engagement.

Several embodiments with independent modalities are shown in fig. 9-12. The layout of both fitting mechanisms is completely as shown in fig. 1, and the stop rings 100 are split elastic rings having split cross sections 130 and have conical outer surfaces of revolution, which rest against the reference end surface 70 by their elastic reaction with the reference cylindrical surface. Fig. 9 has its simplest form, the first engagement member 50 being rigidly integral with the first hub 204, and the adjustment nut 164 directly coupling the first engagement member 50 with the spring 160, all except for the formation of the externally splined teeth 98 for circumferential fixation integrally on the outer cylindrical surface of the second engagement member 80, as shown in fig. 2. Fig. 10 is added to fig. 9 with a packaging shell consisting of a bowl-shaped shell 226 and an annular end cap 230, which are secured therebetween by screws 234. The bowl-shaped housing 226 is circumferentially fixed with the second engagement element 80 by spline teeth 228 of its inner bore face, enabling torque transmission thereof with the first hub 204. The force-transmitting ring gear is fixed thereto by a flat key or screw (not shown). The adjustment nut 164 resides outside the enclosure and axially supports and adjusts the engagement spring 160 via an intermediate ring 190. A seal ring 222 is mounted between the package housing and the first sleeve 204 and a seal ring (not shown) is mounted between the annular end cap 230 and the axial stud of the intermediate ring 190. Fig. 11 is a modification of fig. 10. The spring 160 is mounted indirectly between the second engagement member 80 and the end cap adjustment nut 232, which gives indirect axial support and adjustment to the spring 160. The packaging shell is composed of an end cover type adjusting nut 232, a cylindrical shell gear ring 224 and an annular end cover 230. The end cap type adjustment nut 232 is threadedly coupled into the inner bore of the barrel housing ring gear 224 and is pressed against the non-engaging end face of the first engagement element 50 by the washer 214 to effect axial support and adjustment of the engaging spring 160. The end cap-type adjustment nut 232 receives rotational torque through the force application pocket 238 thereon. The anti-rotation stud link ring 180 is mounted in an annular groove between the end cap adjustment nut 232 and the first bushing 204 and is sealed by a sealing ring (not shown). In fig. 12, the second hub 206 and the first coupling element 50 are both part of the package housing. The equivalent component of the adjusting nut, the bowl-shaped housing 226, is directly associated in screw thread with the outer cylindrical surface of the first engagement element 50, thus achieving the axial support and adjustment of the chimeric spring 160.

Fig. 13 shows an embodiment of a pin-type safety coupling. Wherein the pin 242 is closed on both sides by retaining rings 244. In the present embodiment, the second bushing 206 is a preferred form as the driving shaft.

Fig. 14 shows an embodiment of a one-way security clutch in the form of a duplex. The first coupling element 50 is a reference ring of the blocking ring 100, the inner bore surface of which is the reference cylinder 72, and the second coupling element 80 is an auxiliary ring of the auxiliary blocking ring. Both end faces of the first engagement element 50 and of the blocking ring 100 have a perfectly symmetrical uniform distribution of radial teeth. The two second engagement elements 80 are circumferentially fixed to the second hub 206 by spline teeth, and constitute working engagement mechanisms with the first engagement elements 50, respectively. The two sets of fitting springs 160 are pressed by both ends against the second engaging element 80, respectively, and are supported and adjusted by a shoulder at one end of the second bushing 206 and an adjusting nut 164 at the other end. The blocking ring 100 is located radially within the working engagement means and axially between the two second engagement elements 80, and forms a blocking engagement means with the secondary blocking ring, respectively. The two working embedding mechanisms and the two blocking embedding mechanisms are synchronously in an embedding state or an overload separating state. The bolt hole 74 in the first coupling element 50 is used for fixing the force-transmitting ring gear. The inner bore shoulder 128 of the blocking ring 100 serves to ensure the coaxiality of the first coupling element 50 in the event of an overload, and also serves to heighten the projection 114 on the blocking ring 100 so that it always fits into the inner bore of the second coupling element 80. The pawl lever 136 and the pawl return spring 138 are disposed in radial holes on the axially symmetrical plane of the reference cylindrical surface 72. A circle of ratchets 134 are arranged in a central groove of the outer cylindrical surface of the blocking ring 100, and pawl rods 136 embedded between the ratchets constrain the blocking ring 100 on the reference cylindrical surface 72 and drive the blocking ring 100 to rotate integrally in a relative rotation direction opposite to the overload relative rotation. The number of teeth and the circumferential position of the ratchet teeth 134 are determined in such a way that the blocking ring 100 stays at a position where the engagement mechanism can be engaged and reset when the blocking ring is stopped by the detent lever 136. The optimal positioning is that the peripheral direction of the auxiliary blocking teeth is centered in the tooth grooves of the blocking teeth after the tabling, and the same number of teeth as the number of the working teeth and the uniform distribution are a good choice.

It is noted that the second engagement element 80 is entirely as shown in fig. 2, except that the splined tooth portion is axially biased toward the engagement end. Although the blocker ring 100 has no support for the reference end face, the blocker ring 100 still has a stable axial position because the axial forces acting on the two sub-clutches are necessarily present in pairs due to the synchronicity of the actions of the two sub-clutches. Therefore, in this embodiment, the axial and circumferential geometrical relationships between the working engaging mechanism and the blocking engaging mechanism of the two sub-clutch mechanisms are completely the same as those of the embodiment shown in fig. 1, and therefore, the description thereof is not repeated here. It must be emphasized, however, that δ and ρ in this embodiment are numerically smaller than δ and ρ in the embodiment of fig. 1, due to the absence of frictional resistance from the reference end face.

The operation and overload disconnection process in this embodiment is identical to that of the embodiment of fig. 1, and will not be repeated here. It should be noted that, in the process of the reverse-method tabling reset after overload, the self-locking relation of the working face is forcedly destroyed by using the unidirectional of the ratchet mechanism instead of using the change of the lift angle. Naturally, the engagement reset process of the clutch may also be artificially controlled using the rotation stop method in the present embodiment as in the embodiment of fig. 1. That is, the radially outer end of the rotation-stopping stud 182 is spring-loaded and slidably fitted in the radial through-hole between the bolt holes 74 of the first engaging element 50 with its top pin surface close to but not abutting against the stopper ring 100. A rotation stop recess 126 is provided at a corresponding position on the outer cylindrical surface of the blocking ring 100, and a rotation stop stud coupling ring 180 is disposed on the corresponding outer cylindrical surface of the first engagement element 50, the inner cylindrical surface of the ring being a recess-type cam surface which engages with the outer end of the rotation stop stud 182 and is axially retained by the stud, so that when the rotation stop stud coupling ring 180 is circumferentially stopped, i.e. the cam is rotated relative to the first engagement element 50, the rotation stop stud 182 is radially pressed into the rotation stop recess 126 of the blocking ring 100, thereby circumferentially stopping the blocking ring 100 at a relative position where it loses its axial blocking capability. Upon withdrawal of the circumferential detent, centrifugal force and radial spring force will force the anti-rotation stud 182 back again to the maximum outer diameter of the cam surface, thereby causing its pin ejection out of the anti-rotation recess 126. To improve reliability, the blocker ring 100 may be made in the form of a resilient opening to create self-restraint. Obviously, after the rotation stopping method is adopted, the blocking and embedding mechanism of the embodiment can have bidirectional blocking capability.

The working mechanism of the anti-rotation method, the circumferential position relation of the radial through hole and the anti-rotation groove 126, and the range of the lift angle β of the tooth flank 118 of the stop protrusion at the middle of the tooth crest are completely the same as those described in the embodiment of fig. 1, and will not be repeated here.

It is apparent that the operating torque of this embodiment has doubled compared to the single-clutch safety clutch shown in fig. 1. In addition, because the friction resistance torque of the end face sliding is not available, only the friction resistance torque of the ratchet mechanism is available, and the residual torque after overload is very small. If the blocker ring 100 is self-constrained in the form of a split elastic ring and the engagement reset again uses a detent method, the residual torque coefficient will be more nearly zero, no shutdown may be necessary after overload, and the operating speed will be almost solely dependent on the strength of the material. This characteristic is very important for a transmission shaft system which needs to transmit high rotating speed and high torque without stopping, such as wind power generation. Moreover, due to the trapezoid cross section of the working teeth, even if a form and position error exists between the units in the circumferential direction, a slight separation exists in the axial direction of one sub-clutch mechanism in a power transmission state, the torque borne by the two sub-clutch mechanisms is not strictly equal, for example, 49.9% to 50.1%, and the overall working performance, effect and reliability are hardly affected.

Fig. 15 shows the package form of fig. 14. Wherein the first engagement element 50 is given a radial positioning by the outer circumferential surface of the shoulder of the second bushing 206 and the outer circumferential surface of the end cap type adjustment nut 232 at the other end. The flat key slot thereon can be translated to leave a radial detent engagement mechanism in place for the blocker ring 100.

Fig. 16 shows a variant embodiment of fig. 14. The difference is that the first engaging member 50 has a reference end surface 70 formed in the inner bore thereof, and the two stop rings 100a and 100b are independent of each other and are restrained by a tightening snap ring 216 to the respective reference end surfaces 70. The tightening snap ring 216 is a snap ring having an outer circular surface formed with a "V" shaped circumferential groove, the "V" shaped conical surface of which presses against the conical surface 132 in the inner bores of the two stop rings 100a and 100b, and the radial elastic expansion force of which urges the two against the reference end surface 70. The two stop rings 100a and 100b form a circumferential linkage mechanism through axial engagement between the tooth protrusions 139 on the respective sliding end surfaces 124. The circumferential freedom degree of the linkage mechanism is that after the blocking embedding mechanism at one end is embedded and reset, the blocking embedding mechanism at the other end cannot be in a blocking state, and only the minimum clearance amount in the embedding process or the completed embedding process is taken as an upper limit. The circumferential degree of freedom of the linkage mechanism is preferably zero, and when not zero, the linkage mechanism and the two blocking embedding mechanisms are preferably simultaneously positioned at respective central embedding positions.

In comparison with fig. 14, the present embodiment can conveniently realize bidirectional operation by simply making bidirectional blocking working surfaces 108 on the blocking rings 100a and 100 b.

Fig. 17 shows the only embodiment of the present invention having tension springs. The layout of the two engaging mechanisms is completely as shown in fig. 16, the two blocking rings 100 are open elastic rings, the revolving friction surfaces formed between the two blocking rings 100 and the respective reference cylindrical surfaces 72 are both conical, and the guiding action of the conical surfaces restrains the two blocking rings 100 to the respective reference end surfaces 70. The engagement spring 160 is mounted in an annular region formed radially between the stop ring 100 and the second engagement element 80, and has two threaded ends extending from respective axial holes of the second engagement elements 80 to be respectively coupled to the two adjustment nuts 164. It is contemplated that spring 160 may be replaced by a plurality of small diameter tension springs arranged circumferentially. In addition, eliminating the second bushing 206 simplifies the structure.

Fig. 18 shows a fourteenth embodiment of the present invention. Corresponding to the results of radially interchanging the component positions in fig. 15. The packaging form is completely the same as that shown in fig. 11, and only one sub-clutch mechanism is added. As with fig. 14-16, as the end cap type adjustment nut 232 is rotated, the axial position of the tubular housing ring gear 224 relative to the first engagement element 50 or the first bushing 204 will vary slightly, unless a symmetrical adjustment is employed as shown in fig. 20. This amount of change is equivalent to half the total compression of the spring 160, but its effect is not difficult to eliminate.

Fig. 19 shows a fifteenth embodiment of the invention, in the form of a tooth coupling, which is a variation of fig. 18. The entire clutch is mounted on the first rotating shaft 200, and only the second sleeve 206, which is the other half of the coupling, is mounted on the second rotating shaft 202. The essential change with respect to fig. 18 is that, although still taking the first coupling element 50 as a reference ring, the blocking engagement means are radially inside the two working engagement means and, correspondingly, the secondary blocking ring is radially inside the second working tooth 82, as shown in fig. 19 (b) and (c). It can be seen that the secondary blocking tooth 142 is a projection on the inner bore face of the second coupling element 80, the crest 144 of which is coplanar with the root face 86 of the second working tooth 82. The two stop rings 100 in this embodiment cannot realize rigid integration and circumferential linkage, so that the reliability is relatively reduced.

Fig. 20 shows a sixteenth embodiment of the present invention, which is a modification of fig. 14. One of the deformations is that the pressure of the spring 160 can be adjusted bilaterally simultaneously to maintain the axial position of the first engagement element 50 stable. The second variant is that the primary ring of the secondary blocker ring is exchanged for the first coupling element 50 and the reference ring for the second coupling element 80, the blocker rings 100a and 100b being moved rapidly in the axial direction together with the reference ring. Therefore, it is necessary to provide a constraining snap ring 122 by which to press the annular base 112 of the blocker rings 100a and 100b to axially fix the latter two against the outer cylindrical surface of the spline teeth of the second coupling member 80 and always abut against the reference end face 70. Between the two stop rings 100a and 100b, there is a circumferential linkage mechanism, which is composed of a groove 137 and a protrusion 139 formed on the middle limit protrusion 114 of the two stop teeth, and the full-tooth engaging depth is larger than the sum of the full-tooth engaging depths of the two working engaging mechanisms, and the circumferential freedom is described in the embodiment shown in fig. 16 and will not be repeated here. Specific structures of the bicyclic rings are shown in FIGS. 20 (b) to (d).

It is understood from fig. 19 and 21 that if the second sleeve 206 is split into two parts, i.e., left and right, to connect two output shafts, respectively, and the circumferential linkage mechanism of the two-sided blocking rings is eliminated, then the two-sided single-connection safety clutches are simply connected in a duplex manner without any relation, and the purpose of respectively protecting the two output shafts can be achieved.

In the seventeenth embodiment shown in fig. 21, the first coupling element 50 is a reference ring of the stop ring 100 and the second coupling element 80 is a secondary ring of the secondary stop ring, the stop-and-snap ring means being located radially and axially within the working engagement means. The first engagement element 50 is no longer a rigid entity but two completely independent bodies 50a and 50b. The two independent bodies 50a and 50b are circumferentially fixed to the first sleeve 204 by flat keys 208, respectively, in a manner that the engaging surfaces thereof are opposed to each other, and are axially limited by the latter end shoulder and the other end adjusting nut 164. The two second engaging elements 80 are circumferentially fixed to the cylindrical housing ring gear 224 by spline teeth on respective inner and outer cylindrical surfaces, and form a working engagement mechanism with the two first engaging elements 50a or 50b from inside to outside, respectively. The fitting spring 160 is centered while pressing on the non-fitting end surfaces of the two second engagement elements 80. The stopper rings 100a and 100b are configured as shown in fig. 20 (b) to (d), and as described above, the two rings are pressed against the reference end surface 70 by the same restraining spring 120. The satellite blocker ring 80 is shown in fig. 19 (b) and (c). The ring-shaped end caps 230a and 230b are fixed to both end faces of the cylindrical case ring gear 224 by screws 234, and are supported radially to be integrated as a sealed case. Wherein an annular end cap 230a is inserted in a clearance fit between the adjustment nut 164 and the first engagement element 50a to axially define the entire package housing. Accordingly, a circular boss is formed on the non-fitting end surface of the first engaging element 50 a.

Fig. 22 shows yet another tooth coupling. The layout form of the sub-clutch mechanism is basically as shown in figure 21. The difference is that the two stop rings are rigidly connected into a whole by a radial base body, so that the two first joint elements 50 cannot be pressed to adjust the embedded elastic force and are limited only by the two snap rings 210; a form of unidirectional drive unidirectional constraint ratchet mechanism is employed as shown in fig. 14. The ratchet mechanism is arranged radially between the reference cylindrical surface 72 of the right-hand first coupling element 50 and the blocker ring 100, constraining the blocker ring 100 only in the circumferential direction. Wherein the pawl lever 136 and the pawl return spring 138 are arranged in a radial through hole in the reference cylindrical surface 72 and the ratchet 134 is integrally formed on a corresponding inner shoulder of the inner bore surface of the blocking ring 100. It is noted that, due to the rigidity of the blocker ring 100, there is no end-face friction with the first engagement element 50, and the residual torque after overload is only a slight frictional resistance torque from the ratchet mechanism, as in the case of fig. 14. Of course, the ratchet mechanism may also be arranged in an axial manner in a corresponding annular revolution region between the blocking ring 100 and the first engagement element 50. Further, the magnitude of the fitting elastic force can be adjusted by adding or subtracting a washer or the like between the two second engaging elements 80 and the fitting spring 160 in the axial direction.

Fig. 23 shows yet another encapsulated two-up embodiment. Corresponding to the results of radially interchanging the component positions in fig. 21. The stop ring 100 is still based on the first engagement element 50, and the secondary stop ring is still based on the second engagement element 80, and is located radially outside the second working teeth 82, that is, the stop caulking ring mechanism is located axially inside the working caulking mechanism, and is located radially outside the working caulking mechanism. The two first engaging elements 50 and the inner cylindrical surface of the cylindrical housing ring gear 224, and the two second engaging elements 80 and the outer cylindrical surface of the second sleeve 206 are circumferentially fixed by spline teeth. Annular end caps 230a and 230b are fixed by screws 234 to the respective end faces of the cylindrical housing ring gear 224, positioning the latter radially on the second hub 206 and constituting a package housing. The adjusting nut 164 is threadedly coupled to an outer cylindrical surface of the ring post boss 248 of the ring end cap 230a, and is pressed and adjusted in axial distance between the two first engaging elements 50 by the axial stud of the intermediate ring 190, thereby achieving an effect of adjusting the axial fitting elastic force of the two working fitting mechanisms.

As shown in fig. 2 (b), the two blocking rings 100 have the same structure, and are each a contracting elastic split ring, and all the blocking teeth 102 are formed on the inner hole surface of the annular base 112 a. In a partial section corresponding to the crest 116 of the stopper tooth crest middle stopper protrusion, a portion of the annular base 112a is cut off to form a groove 137. The two rings are circumferentially linked by the linking teeth 139 respectively embedded in the grooves 137 of the two end stop rings 100, and a circumferential linkage mechanism is formed. As shown in fig. 24 (c) and (d), the interlocking teeth 139 are integrally formed on the outer circumferential surface of the annular base 112b, and the partial shoulders 246 are also formed on the outer circumferential surface of the teeth 139. Two springs 218 are mounted between the spline tooth end surface of the first engaging member 50 and the end surface of the shoulder 246 at both ends, respectively. The tie ring 220 may thus always be at the axial midpoint of the two blocker rings 100. Thus, it is sufficient to ensure that the axial engagement of the circumferential linkage is effective at the other operating torques, as long as it is ensured that the axial engagement of the mechanism is effective at the minimum operating torque. The circumferential self-orientation has been described in the embodiment of fig. 16 and will not be repeated here. Referring to fig. 19 (b) and (c), the structure of the auxiliary stopper ring 80 in this embodiment can be obtained by turning it radially inward and outward.

By the idea of single connection to double connection, the safe clutch schemes of four connection, six connection and the like can be easily obtained. Furthermore, the installation of a geometric displacement information sensing device on the axial moving path of the second engaging element 80 according to the known art can provide overload information or execute related commands in time, thereby achieving the purpose of automatic control. It is therefore to be understood that all of the foregoing is illustrative of the present invention, and that all changes, equivalents, permutations and alterations in the structure or arrangement of parts thereof, which have been set forth above are intended to be embraced by the spirit and scope of the inventive concept.

Claims (10)

1. A zero collision jaw type universal safety clutch is composed of a first joint element, a second joint element, a spring and an adjusting nut, wherein the first joint element is connected with a first rotating shaft, the second joint element can move axially, a characteristic curved surface capable of transmitting torque is formed on a part of non-embedding surface of the second joint element, the first joint element and the second joint element are axially opposite to form a working embedding mechanism with double functions of transmitting torque and overload separation, the spring is directly or indirectly arranged between the second joint element and the adjusting nut, axial embedding force is provided for the working embedding mechanism, and the adjusting nut finally forms direct or indirect axial limitation and support for the spring; the method is characterized in that:

the blocking and embedding mechanism is arranged for preventing the axial embedding of the working embedding mechanism in an overload separation state, is axially positioned in the working embedding mechanism, is radially positioned in or out of the working embedding mechanism, and is formed by axially embedding a blocking ring and an auxiliary blocking ring, and the peripheral surfaces of the embedding end surfaces of the two rings are all provided with the same number of radial blocking teeth with axial blocking effect; the minimum blocking height of the blocking embedding mechanism is larger than the initial separation height of the working embedding mechanism in two rotation directions and smaller than the full-tooth embedding depth of the working embedding mechanism; said secondary blocker ring being rigidly integral with its primary ring, which is the second or first engagement element; the stop ring is supported by the reference ring base in a single direction, and the sliding end face of the stop ring and the reference ring base form a circumferential free sliding friction pair; the reference ring is a first or second engagement element opposite the owner ring of the auxiliary blocker ring;

the limiting and embedding mechanism is arranged for limiting the circumferential relative position of the blocking ring in the blocking and embedding mechanism and consists of the blocking ring and an auxiliary limiting ring; the auxiliary limiting ring and the auxiliary blocking ring are rigidly integrated into the same ring, the limiting embedding mechanism and the blocking embedding mechanism are superposed to form a control embedding mechanism, in the control embedding mechanism, the blocking teeth are also limiting teeth, and the auxiliary blocking teeth are also auxiliary limiting teeth;

in the control embedding mechanism, the working faces of tooth crests of the blocking tooth and the auxiliary blocking tooth are spiral faces with the lead angles not larger than rho, and a limiting bulge is formed in the middle of at least one of the tooth crest faces, wherein rho is the maximum lead angle of the working face, which can enable a static friction pair formed by axial contact of the working faces blocked by the two sides to successfully self-lock in the blocking working condition; and

the maximum limit embedding depth of the control embedding mechanism is larger than the full-tooth embedding depth of the working embedding mechanism.

2. The utility model provides a general safety clutch of twin zero collision jaw formula which characterized in that:

two first engaging elements are provided, and the two first engaging elements are circumferentially fixed on the first rotating shaft in a mode that the embedded end faces face to each other;

the two elements are respectively embedded with the two first joint elements in the axial direction to form a working embedding mechanism with the double functions of torque transmission and overload separation, and the two working embedding mechanisms are synchronously in an embedding state or an overload separation state;

at least one spring acting on the non-engaging end surfaces of the two second engaging elements to provide axial engaging force for the two working engaging mechanisms;

at least one adjusting nut to finally form a direct or indirect axial restraint and support of said spring;

two blocking embedding mechanisms are arranged, are synchronously in an embedding state or an overload separation state and respectively form a group of sub-clutch mechanisms with one working embedding mechanism; in each group of sub-clutch mechanisms, the blocking embedding mechanism is used for preventing the axial embedding of the working embedding mechanism in an overload separation state, the blocking embedding mechanism is radially positioned inside or outside the working embedding mechanism and is formed by axially embedding a blocking ring and an auxiliary blocking ring, the circumferential direction of the embedding end surfaces of the two rings is provided with the same number of radial blocking teeth with axial blocking effect, the minimum blocking height of the blocking embedding mechanism is greater than the initial separation height of the working embedding mechanism in two rotation directions and is less than the full-tooth embedding depth of the working embedding mechanism, the auxiliary blocking ring and the main ring of the auxiliary blocking mechanism are rigidly integrated, and the main ring of the auxiliary blocking mechanism is a second engaging element or a first engaging element;

in each group of sub-clutch mechanisms, limiting embedded mechanisms for limiting the circumferential relative positions of the blocking rings in the blocking embedded mechanisms are arranged, each limiting embedded mechanism consists of a blocking ring and an auxiliary limiting ring, the auxiliary limiting rings and the auxiliary blocking rings are rigidly integrated into a same ring, and the limiting embedded mechanisms and the blocking embedded mechanisms are superposed to form a control embedded mechanism;

in the control embedding mechanism, the working faces of tooth crests of the blocking tooth and the auxiliary blocking tooth are spiral faces with the lead angles not larger than rho, and a limiting bulge is formed in the middle of at least one of the tooth crest faces, wherein rho is the maximum lead angle of the working face, which can enable a static friction pair formed by axial contact of the working faces blocked by the two sides to successfully self-lock in the blocking working condition; and

in each group of sub-clutch mechanisms, the maximum limit embedding depth of the control embedding mechanism is larger than the full-tooth embedding depth of the working embedding mechanism in the same group of sub-clutch mechanisms.

3. The security clutch of claim 2, wherein: the two blocking embedding mechanisms are respectively positioned in a group of sub-clutch mechanisms in the axial direction, in each group of sub-clutch mechanisms, the blocking rings are all supported in one direction by the reference end surfaces of the respective reference rings, and the sliding end surfaces of the blocking rings and the reference end surfaces form circumferential free sliding friction pairs; the reference ring is a first or second engagement element opposite the owner ring of the auxiliary blocker ring.

4. The security clutch according to claim 3, wherein: the circumferential relative position between the two stop rings is restricted by a circumferential linkage mechanism, the mechanism is an axial embedding mechanism which is always in an embedding state and positioned between the two stop rings, and the axial embedding mechanism is directly or indirectly composed of the two stop rings.

5. The security clutch of claim 2, wherein:

(a) The two blocking embedding mechanisms are axially connected in a rigid integrated mode of the two blocking rings, and are axially and simultaneously positioned in the two working embedding mechanisms;

(b) The blocking teeth of the two blocking rings are respectively formed on two end surfaces of the same annular base body, the inner cylindrical surface at the same side or the outer cylindrical surface in a mode that the tooth tops face to each other reversely;

(c) The second engagement element is the auxiliary ring of said auxiliary blocking ring and the first engagement element is a reference ring, the blocking ring being fitted inside or outside the reference ring quasi-cylindrical surface.

6. The security clutch according to claim 2, wherein: the two first jointing elements are rigidly integrated in a mode of connecting with non-embedded end surfaces.

7. The security clutch according to claim 1, 2, 3, 4, 5 or 6, wherein: the blocking ring in the fitted state can be relatively stationary on the reference end face or the reference cylindrical surface of the reference ring by the restraint.

8. The security clutch according to claim 1, 2, 3, 4, 5 or 6, wherein:

(a) The initial separation heights of the two working embedding mechanisms in two opposite rotating directions are zero, and the rotation of the mechanisms in the two opposite rotating directions can cause the axial separation of the mechanisms;

(b) The two stopping working surfaces of the tooth tops of the stopping tooth and the auxiliary stopping tooth are respectively and correspondingly formed on two sides of each tooth top surface;

(c) The entrance margin K of the blocking embedding mechanism conforms to the inequality: k > theta _c +θ _f + η, the relevant parameters are defined as follows:

θ _c : the circumferential included angle corresponding to the top surface of the working tooth on the first jointing element,

θ _f : the circumferential included angle corresponding to the top surface of the working tooth on the second jointing element,

eta: due to the lead angle and the circumferential clearance of the working embedding mechanism.

9. The security clutch according to claim 1 or 2, characterized in that: the side face of the limiting bulge in the control embedded mechanism, which is on the same side with the blocking working face, is a spiral face with a lead angle beta, and [ delta ] is more than or equal to beta and less than 180 degrees, wherein [ delta ] is the absolute value of the minimum lead angle delta of the blocking working face, which can enable a static friction pair formed by the blocking working face of the blocking tooth and the blocking working face of the auxiliary blocking tooth to be in axial contact to successfully self-lock in the blocking working condition.

10. The security clutch of claim 9, wherein:

(a) A stop ring rotation stopping mechanism is arranged between the reference ring and the stop ring, the rotation stopping mechanism is an embedded limiting mechanism which can forcibly limit the stop ring at a specific circumferential position relative to the reference ring, when the mechanism is embedded, the stop ring loses axial stopping capability, and when the mechanism is not embedded, the stop ring has axial stopping capability;

(b) The lead angle beta of the side surface of the limiting bulge meets the inequality: beta is more than or equal to | delta | and less than 90 degrees to phi, wherein phi is the friction angle of a friction pair formed between the side surface of the limiting bulge and the blocking tooth or the auxiliary blocking tooth, and | delta | is defined as above.

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