CN101117989A - Zero impacting jaw universal safety clutch - Google Patents

Abstract

The present invention discloses a no-collision jaw type universal safety clutch, which has the characteristics of great variety of single or double direction and single or double linked implementation forms, and no overload impact or no collision, huge work torque, high rotating speed, small residual torque which approximates to zero, small volume, simplicity and reliability, easy manufacture, and long service life. The present invention is characterized in that the no-collision jaw type universal safety clutch is provided with a blocking embedding mechanism preventing a work embedding mechanism from being embedded under the overload condition, the mechanism on the axial direction is positioned in the work embedding mechanism, and the mechanism on the radial direction is positioned in the work embedding mechanism or outside the work embedding mechanism; a lift angle of both sides blocking the working surface is formed to enough ensure the friction self-locking collided on the both sides and the stability of the blocking operating condition, in order that the lift angle has the capabilities that the adaptive axle base is changed and the abrasion is automatically compensated; no collision characteristic of the overrunning operating condition of the two embedding mechanisms, and the separating block of the blocking embedding mechanism and the absolute reliability of the embedding return process are maintained for a long time. After the overload separation, the positive rotation or negative rotation which is simple and convenient can evenly realize the embedment replacement of the clutch automatically.

Description

Zero-collision jaw-type universal safety clutch

Technical Field

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

Technical Field

Conventional security clutches (also referred to as torque limiters) are of three types, shear pin, snap-fit 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 type safety 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 the theory that the conventional dog clutch can only be used for shafting transmission parts with low rotating speed, low load (for example, no more than 315 revolutions per minute when 400 N.m) and low driven part rotational inertia is formed in the industry for more than one hundred years. The operation principle and related data are described in the third paper of "mechanical design manual" by the mechanical design manual editors, published by the mechanical industry publishers in 8 months 2004 (p 22-235 to p 22-240).

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 advantage that the transmission can be recovered immediately after overload is changed, the transmission needs to be recovered manually and reset after each overload, time and labor are wasted, the requirement on maintenance space is more directly strict, and a part of application range is reduced invisibly.

Disclosure of Invention

The invention aims to overcome the long-standing technical bias in the industry and provide a zero-collision jaw universal safety clutch which eliminates the inherent defects of the traditional jaw universal safety clutch, so that the zero-collision jaw universal safety clutch has the advantages of no overload impact, no continuous impact abrasion, long service life, simple structure, low manufacturing cost, quick, convenient or automatic recovery after overload, no limitation of installation position, high rotating speed and high torque.

The invention also aims to provide the jaw universal safety clutch which axially couples the zero-collision jaw universal safety clutch, so that the jaw universal safety clutch has the characteristics of double 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 to which the auxiliary stop ring or the auxiliary limit ring is attached.

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 mechanism, the tip surface portion of the tooth for abutting contact between the radial teeth of both the ring gears constituting the mechanism is denoted by λ.

Blocking working conditions: the blocking teeth of the blocking embedding mechanisms are in opposite contact with each other, so that the working condition of embedding of other axial embedding mechanisms positioned outside the blocking embedding mechanisms in the axial direction is prevented.

δ angle and ρ angle: in the blocking working condition, on one hand, the sliding end surface or the cylindrical surface of the blocking ring is in contact with the blocking reference end surface or the reference cylindrical surface of the reference ring to form a sliding friction pair (when two blocking rings in the duplex safety clutch are formed into a whole, the end surface sliding friction condition does not exist), on the other hand, the blocking working surface of the blocking tooth is in axial contact with the blocking working surface 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 only by the static friction pair, the static friction pair is required to be self-locked, wherein the minimum lift angle of the blocking working surface capable of ensuring the 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 surface is given to limit the circumferential relative position of the blocker 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 means is completely fitted, the axial distance from the highest tooth tip point of one fitting tooth to the highest tooth tip point of the other fitting tooth is set.

Minimum barrier height: transitioning from the unblocking condition (i.e., the stable engagement state) to the blocking condition, the minimum axial distance apart necessary to block the engagement mechanism.

Maximum limit embedding depth: the circumferential constraint action of the limiting embedding mechanism is ensured to exist, and the maximum distance which can be separated in the axial direction of the embedding mechanism is blocked. When the two limiting embedding mechanisms move together with the blocking embedding mechanism in the axial direction, the depth is the axial distance between the highest points in the upper boundaries of the limiting working surfaces of the two embedding parties in a complete embedding state; when the two parts of the limit embedding mechanism do not move together with the blocking embedding mechanism in the axial direction, the depth is infinite.

Initial separation height: under the action of the axial embedding force, the axial embedding mechanism can realize the minimum initial axial separation distance required by axial separation and relative rotation. The distance must be zero, whereas the distance may be non-zero, turning in the opposite direction allowed by the design.

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 two components of one fitting mechanism respectively use two components of the other fitting mechanism as axial supporting bases, the former fitting mechanism is said to be axially located inside the latter fitting mechanism, and vice versa. In addition, the blocking rings referred to in the invention are short for independent blocking rings.

In order to achieve the above purpose, the zero-collision jaw-type universal safety clutch of the invention comprises a first engaging element, a second engaging element, a spring and an adjusting nut, which are all arranged on the basis of the same rotating axis, wherein the first engaging element and the second engaging element axially oppositely form a working embedded mechanism with the double functions of torque transmission and overload separation; the method is characterized in that: 1) The blocking embedding mechanism is used for blocking the axial embedding of the working embedding mechanism in the axial separation overload state and is formed by axially embedding a blocking ring and an auxiliary blocking ring, and a circle of radial blocking teeth with axial blocking effect are arranged on the two rings; 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; 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 main ring are integrated into a whole, and the auxiliary limiting ring and the auxiliary stop ring are circumferentially fixed; when the axial separation distance of the blocking embedding mechanism is larger than the minimum blocking height, the circumferential freedom degree of the limiting embedding mechanism is larger than the entrance margin of the blocking embedding mechanism.

The blocking embedding mechanism is axially positioned in the working embedding mechanism and radially positioned in or out of the working embedding mechanism; the auxiliary blocking ring is integrated with an auxiliary ring which is any one of the joint elements forming the working embedding mechanism; the stop ring is supported unidirectionally by the reference ring base end face, and the sliding end face and the reference end face form a circumferential free sliding friction pair; the reference ring is a side engagement element axially opposite the auxiliary ring of the auxiliary blocker ring.

The invention also aims to provide a duplex zero-collision jaw-type universal safety clutch, which is characterized in that: the two embedded end faces are opposite to each other, the first joint elements are circumferentially fixed on the first rotating shaft, the two second joint elements capable of moving axially are circumferentially fixed with the second rotating shaft, part 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 axially embedded with one first joint element to form two working embedded mechanisms with double functions of transmitting torque and overload separation, the two working embedded mechanisms have the same stable working condition, and the stable working condition is an axial embedded force transmission state or an axial separation overload state; the non-embedded end surfaces of the two second joint elements are acted by springs, and the springs provide axial embedding force for the two working embedding mechanisms and are finally axially limited and supported by adjusting nuts; in order to prevent the axial embedding of the two working embedding mechanisms under the axial separation overload state, two blocking embedding mechanisms with completely same stable working conditions 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 mechanism is used for preventing the axial embedding of the same group of working embedding mechanisms in the axial separation overload state and is formed by axially embedding a blocking ring and an auxiliary blocking ring, a circle of radial blocking teeth with the axial blocking effect are arranged on the two rings, and the minimum blocking height of the blocking embedding mechanism is greater than the initial separation height of the same group of working embedding mechanisms in two rotation directions and is less than the full-tooth embedding depth of the same group of working embedding mechanisms; in each group of sub-clutch mechanisms, a limiting embedded mechanism for limiting the circumferential relative position of a blocking ring in the blocking embedded mechanism is also arranged, and consists of the blocking ring and an auxiliary limiting ring, wherein the auxiliary limiting ring is integrated with an auxiliary main ring, and the auxiliary limiting ring is circumferentially fixed with the auxiliary blocking ring; when the axial separation distance of the blocking embedding mechanism is larger than the minimum blocking height, the circumferential freedom degree of the limiting embedding mechanism is larger than the entrance margin of the blocking embedding mechanism.

Most directly, two blocking embedding mechanisms in the duplex safety clutch are axially and respectively positioned in working embedding mechanisms of one group of sub-clutch mechanisms, and radially and respectively positioned in or out of the same group of working embedding mechanisms; the auxiliary blocking ring is integrated with an owner ring which is any one joint element forming a working embedding mechanism; the two independent barrier rings are axially supported in a single direction by the reference end surface of the reference ring, and the reference ring is acted by the first joint element or the second joint element; meanwhile, the two stop rings can realize long-term related linkage of positions of the two stop rings in the circumferential direction by means of an axial embedding mechanism between the two stop rings.

In addition, two rings of blocking teeth of the blocking ring can be respectively formed on two end surfaces, an inner cylindrical surface or an outer cylindrical surface of the same annular base body in a mode that tooth tops face to each other, so that the two blocking embedding mechanisms are axially connected in a mode that the two blocking rings are formed into a whole and mutually axially supported, the two blocking embedding mechanisms are simultaneously positioned in the two working embedding mechanisms in the axial direction and are positioned in or out of the two working embedding mechanisms in the radial direction, the first joint element is used as a reference ring of the blocking ring, and the second joint element is used as an auxiliary main ring of the auxiliary blocking ring. Likewise, the object of forming the two first engaging elements in one piece may also be achieved by sharing one annular base body.

As a circumferentially fixed radial limit solution, the auxiliary stop ring may be attached to the second engagement element, and the auxiliary limit ring may be attached to a second rotating shaft circumferentially fixed to the second engagement element so as to directly face the inner cylindrical surface of the stop ring; the pin-and-slot radial interlocking mechanism is then disposed between the two rings.

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 function is provided, 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 inlet margin K of the blocking embedding mechanism (when the clutch working teeth are uniformly distributed in the circumferential direction) meets 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.

The optimal scheme of blocking and limiting is that the blocking working faces of the tooth tops of the blocking tooth and the auxiliary blocking tooth are spiral faces with the rising angle not larger than rho, a limiting bulge is formed in the middle of at least one of the tooth tops, and the blocking tooth and the auxiliary blocking tooth are objectively used as the limiting tooth and the auxiliary limiting tooth. Meanwhile, the auxiliary limiting ring and the auxiliary blocking ring are the same ring, and the limiting embedding mechanism and the blocking embedding mechanism are combined into a control embedding mechanism, so that the purposes of self-limiting of the blocking embedding mechanism and stepless change and self-adaption of the axial blocking height are finally achieved.

In order to make better, the side surface of the limiting bulge in the control embedding mechanism, which is on the same side with the blocking working surface, can be made into a spiral surface with the lead angle beta, and beta 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 forced embedding of the clutch can be easily realized. Here, Φ is a friction angle of a friction pair formed by both the sides constituting the fitting control mechanism in frictional contact on the side surfaces of the stopper projection. The stop ring rotation stopping mechanism may be pin slot type embedding mechanism comprising reference ring reference end face or axial or radial through hole in the reference cylinder, corresponding notch or split ring notch in the corresponding friction surface of the stop ring and rotation stopping pin.

The safety clutch can also be integrally packaged in a shell, the shell is composed 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 characteristic curved surface is fixed with the inner hole surface of the first joint element in the circumferential direction or directly and rigidly manufactured into a whole, a characteristic curved surface capable of transmitting torque is formed on the outer surface of the annular sleeve type transmission ring, the inner hole surface of the characteristic curved surface is fixed with the outer cylindrical surface of the second joint element in the circumferential direction 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 through 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.

In the invention, the blocking embedded mechanism with axial blocking function and the blocking ring rotation stopping mechanism are added into the working embedded mechanism, thereby well achieving the proposed purpose. When the auxiliary limiting ring and the auxiliary blocking ring are formed into a whole, the limiting bulge or the self-locking blocking working surface at the middle part of the tooth crest is utilized, and when the auxiliary limiting ring and the auxiliary blocking ring are only fixed in the circumferential direction, the limiting working surface formed on the blocking part independently, namely the control embedding mechanism and the independent radial pin groove type limiting embedding mechanism are respectively utilized or comprehensively utilized, so that the circumferential relative position inside the blocking embedding mechanism under the blocking working condition is well maintained, the blocking relation is well maintained, the embedding resetting of the working embedding mechanism in the overrunning state is prevented, and the purposes of separating impact or collision are eliminated; the blocking ability is forcibly released by means of reverse rotation or a blocking ring rotation stopping mechanism, so that the aims of quick, convenient or automatic restoration of embedding after overload, no limitation of installation position and long service life are well achieved. Meanwhile, the inherent properties of high rotating speed and large torque are naturally released. In addition, only one simple stop ring is added, and the clutch still has the characteristics of simplicity and low manufacturing cost. In addition, through the duplex two-jaw universal safety clutch and the mode of forming the two stop rings into a whole to thoroughly eliminate the sliding friction resistance of the end face, the invention achieves the purposes of doubling the transmission torque and reducing the residual torque after overload.

Compared with the friction type or spring steel ball type safety clutch in the prior art, the invention has the advantages of no comparison in the aspects of torque transmission capacity, working rotating speed, overload frequency, overload duration, residual torque coefficient, service life and application range.

Drawings

Fig. 1 is an axial 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 mechanism is shown in various cases (a) to (c) which show three special tooth profiles, (d) to (i) which show all tooth profiles when | δ | < λ ≦ ρ, and (e) to (i) which show special tooth profiles in which β = λ and are coplanar; (j) The tooth profile is suitable for a radial type position-restricting fitting mechanism.

FIG. 6 is an axial half-sectional view of a second embodiment of the invention.

Fig. 7 (a) is an axial cross-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).

Figure 8 is an axial cross-section of a fourth embodiment of the invention in a radial limit mode.

Fig. 9 (a) is an axial sectional view of a fourth embodiment of the present invention, and (b) is a schematic view of a fitting end face of the first engaging element in (a).

Fig. 10 is an axial cross-sectional view of the simplest embodiment of the invention.

Fig. 11 is an axial cross-section of an embodiment six of the invention in the form of a package.

FIG. 12 is an axial cross-sectional view of a seventh embodiment of the present invention, which is packaged and can be forcibly fitted.

Fig. 13 is an axial cross-sectional view of an embodiment eight of the present invention in another package form.

Fig. 14 is an axial cross-section of a specific application of the invention in a coupling.

Fig. 15 (a) is an axial sectional view of a ninth embodiment of the present invention, (b) is an axial sectional view of a stopper ring in (a), and (c) is a schematic sectional view of an axial symmetric plane T-T in (b).

Fig. 16 is an axial cross-sectional view of an embodiment ten of the invention in the form of a package.

Fig. 17 (a) is an axial sectional view of an eleventh embodiment of the present invention, (b) is an axial sectional view of a left blocker ring in (a), (c) is an axial sectional view of a right blocker ring in (a), and (d) is a simplified left view of (c).

Fig. 18 is an axial cross-sectional view of a twelfth embodiment of the invention having tension springs.

Fig. 19 is an axial cross-sectional view of a thirteen embodiment of the invention in packaged form.

FIG. 20 (a) is an axial sectional view of the fourteenth embodiment of the 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. 21 (a) is an axial sectional view of a fifteenth embodiment of the present invention, (b) is a schematic 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. 22 is an axial cross-sectional view of sixteen embodiments of the present invention.

Fig. 23 is an axial cross-sectional view of a seventeenth embodiment of the invention.

Fig. 24 (a) is an axial sectional view of eighteen embodiment of the invention, (b) is a front view of a blocker ring in (a), (c) is an axial sectional view of a coupling ring in (a), and (d) is a front view of (c).

Detailed Description

The essential explanation 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 symbols and are only described in detail when they appear for the first time, and no repeated detailed description will be given when they appear again thereafter.

Fig. 1 to 4 show a first embodiment of the invention, a two-way safety clutch in the form of a shaft-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 shafts are fixed to the first and second coupling members 50 and 206, respectively, by flat keys (not shown). 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 collar 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 by the spring seat 162. The blocking ring 100 is located radially within the working engagement means and, with the secondary blocking ring, forms a blocking engagement means, the sliding end face 124 of which abuts against 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 externally splined teeth of the second hub 206. A rotation stop 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 circumferentially distributed at one end of the rotation stop pin coupling ring 180, and the three rotation stop pins 182 are respectively inserted into three rotation stop pin installation through holes 188 on the first engagement element 50, and the top surface of the rotation stop pin is close to but not contacted with the stop ring 100.

The specific structure of the second engaging element 80 is shown in fig. 2. The second working teeth 82 are radial teeth with trapezoidal cross sections, the teeth are uniformly distributed on the outer ring side of the embedding end face, and the auxiliary blocking teeth 142 are uniformly distributed on the inner ring side of the embedding end face. The auxiliary blocking tooth 142 is radially connected with the second working tooth 82 into a whole, the tooth top surface 144 of the auxiliary blocking tooth is higher than the tooth top surface 84 of the second working tooth, the blocking working surface 148 of the auxiliary blocking tooth is a spiral surface with a lead angle lambda, and lambda is greater than delta lambda and less than rho. To simplify the structure and facilitate the integral manufacture, the secondary blocker tooth flank 150 and the tooth root surface 146 are completely coplanar with the second working tooth flank 88 and the tooth root surface 86, respectively, and the secondary blocker tooth 142 is therefore divided into two parts, the tooth tip surface 144 corresponding to the second working tooth gullet and part of the intermediate tooth body not being restored. The layout and the tooth profile of the engagement end face of the first coupling element 50 are entirely identical to those of the second coupling element 80, except that there is no auxiliary blocking tooth and the crest of the first working tooth 52 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 surface type blocking working surfaces 108 with the lead angle lambda, two tooth side surfaces 110, two limiting protrusion spiral side surfaces 118 with the lead angle beta, wherein the lead angle delta is larger than or equal to beta and is smaller than 180 degrees, and a limiting protrusion top surface 116. One end having the stopper working surface 108 is a stopper ring fitting end surface, and the other end is a stopper ring circumferential sliding end surface 124. To simplify the structure, the blocker ring rotation stopping groove 126 is occupied by a blocker tooth groove. The circumferential position, the circumferential width, and the circumferential width of the rotation stop pin 182 of the rotation stop pin mounting through hole 188 are determined with such effects that the position where the stopper ring 100 stays must result in the stopper fitting mechanism failing to successfully block the axial fitting of the working fitting mechanism when the rotation stop pin 182 is fitted into the rotation stop groove 126.

As shown in fig. 4 (a), (b) and (f), the first engaging element 50 and the second engaging element 80 constitute a bidirectional 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)

And, K > θ _c +θ _f + η; axial separation distance greater than

The circumferential freedom of the positive locking mechanism defined by the blocking running surface 108 is then naturally greater than K. In the state of being embedded, the first and second bodies are,

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 engagement 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 form relationship of each embedding mechanism under the overload working condition, and fig. 4 (e) shows the tooth form relationship diagram of the one-way control embedding 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 equispaced three, that the blocking ring 100 and the secondary blocking ring each have three equispaced identical radial teeth, that the secondary blocking tooth 142 circumferentially exactly spans two of the second working teeth 82, and that the arrangement of the blocking tooth gullet as the rotation stop notch 126 is not essential, but is purely for the sake of simplicity of construction and process, etc. In the case where the auxiliary stopper ring cannot be formed integrally with the main ring, the auxiliary stopper ring can be handled by a method of manufacturing the auxiliary stopper ring separately in advance and then rigidly combining the auxiliary stopper ring with the main ring by welding or interference fit. Similarly, the restraining spring 120 and the return spring 186 are wave springs, but may be any other type of elastic body.

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

In the engaged state, the working torque is transmitted via the first coupling element 50 to the second coupling element 80 and then via the spline to the second hub 206, completing the torque transmission within the clutch, although the transmission paths may be reversed. In the case of overload in any direction, that is, 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 larger than the engaging pressure provided by the spring 160, referring to fig. 4 (a) or 4 (f), the second working tooth 82 is inevitably separated axially against the elastic pressure, and is withdrawn from the engaging position, so that the engaging relationship of the entire working engaging mechanism is not present, the torque transmission path between the two engaging elements is disconnected, and the mechanism is brought into the overload separating working state.

After the overload separation begins, due to parameters

So that 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. Since the blocking ring 100 is held stationary on the first coupling element 50 by the spring 120, the process of separation during rotation is sufficient to ensure that D is achieved in the first synchronization of the axial separation distance of the blocking engagement mechanism, provided that the access margin K of the blocking engagement mechanism does not depart from its lower limit value _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 collision, particularly at the moment of separation. This will significantly reduce the wear rate of the two, eliminate noise, and prolong the life. In addition, can be made ofThe top surface of the first working tooth or the second working tooth is made into a step shape with a high inner end so as to obviously reduce the average sliding friction radius and the residual torque under the overload working condition. The residual torque coefficient will be much smaller than the sliding friction coefficient.

Since the bidirectional blocking engagement mechanism is used, the safety clutch of the present embodiment has the characteristic of being free from any impact and collision in both directions of overload release. It should be emphasized that the features of the helicoidal surface controlling the blocking face in the engagement means are the precondition for ensuring zero collision of the working teeth in the blocking condition, i.e. λ > 0 is necessarily required. The lambda is more than delta and less than or equal to rho is not only a necessary condition for friction self-locking between the blocking working surfaces in the blocking working condition, but also a blocking embedding mechanism has a self-adaptive axial separation distance in a certain rangeThe ability to disengage and the ability to automatically compensate for various axial wear significantly increases the overall performance, reliability and life requirements of the security clutch, and the amount that can be compensated can also be set as desired at the time of manufacture. 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 a butting way cannot be self-locked, and the axial separation distance of the blocking and embedding mechanism is larger than D _c Until encountering the limit projection 114. That is, through proper design, we can get the overload rotation condition that makes two working teeth have no contact. In addition, the self-locking relationship between the blocking faces only exists in the corresponding overload rotation, i.e., in the relative rotation that makes the lift angle of the blocking face in the butt contact positive, but never in the relative rotation that makes it negative, because the lift angle λ ' = - λ < "| δ |, λ ' in the latter rotation falls completely outside the lower limit of the self-locking requirement λ ' ≧ δ. Therefore, by changing the relative rotation direction of the two engagement elements in the blocking condition, the original self-locking relationship between the blocking working surfaces will disappear immediately, and the blocking ring 100 will not rotate integrally with the auxiliary blocking tooth 142, but will rest on the reference ring reference end surface 70.

Therefore, for the fitting reset of the safety clutch, a method of the present embodimentThe method is a reverse method, and the prerequisite for implementation is that K is more than theta _c +θ _f + η. At this time, no matter what extreme condition 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 be synchronously engaged and reset with the second working tooth 82, and the reverse disengagement blocking situation can not occur, especially when the one-way blocking engagement mechanism is used, the blocking tooth notch rotates synchronously with the auxiliary blocking tooth 142, see fig. 4 (e). Another method of fitting reduction in this embodiment is a rotation stop method. That is, while maintaining the overload rotation state, the rotation stop pin link ring 180 is axially pressed to overcome the axial reaction force of the spring 186, and then the rotation stop pin 182 is axially pressed into the rotation stop groove 126 on the sliding end surface 124 of the blocker ring, and the blocker ring 100 is circumferentially stopped at a specific relative position where its axial blocking capability is lost, so that the auxiliary blocker tooth 142 is forced to slide and climb relative to the blocker tooth 102, and after passing over the limit protrusion 114 at the middle thereof, is inserted into the next tooth groove of the blocker ring 100, thereby achieving the purpose of clutch controllable engagement reset.

Obviously, the embedding reset of the safety clutch is simple in mechanism and reliable in process, automation and remote control are easily realized through reverse rotation or electricity, liquid and machinery, the performance of the jaw type safety clutch is improved in a crossing mode, the working rotating speed, the torque and the adaptable overload frequency of the jaw type safety clutch are greatly increased, and the jaw type safety clutch can be installed on a part. 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 rotation stopping mechanism and the rotation stopping method of the controllable fitting 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: is | < δ | < β < 90 ° - φ, and is best with the side surface 118 coplanar with the barrier work 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. 15 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 stop 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 chinese patents with application numbers 200720146912.5 and 200720146911.0 and the patents of the same name, which are all incorporated herein by reference, and will not be described in detail herein.

Fig. 5 shows all possible abutting contact conditions 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 of β = λ and the tooth flank 118 of the stopper tooth tip middle stopper projection is coplanar with the stopper face 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 constraint spring 120 and the constraint snap 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 layout of the secondary blocker tooth 142 to 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 in turn fitted with a wave spring 120 and a restraining snap ring 122, the snap ring 122 being fitted in a snap ring groove 212 on the outer cylindrical surface at the opening of the annular groove. To complete the necessary restraint of team blocker ring 100. The anti-rotation pin 182 in this example is mounted in a corresponding axial through bore 188 of the second engagement element 80 and is restrained in axial opposition by a return spring 186 therebetween. The operation of the anti-rotation pin coupling ring 180 is performed by means of an intermediate ring 190, both rings having the same structure. In addition, the fitting spring 160 is formed by four disc springs, and the radial position therebetween is defined by a disc spring T-shaped positioning ring 166 having a cross-sectional shape of a "T" shaped inner shoulder, on both sides of which the spring 160 is symmetrically located. 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 the only embodiment of the present invention having a radial type position-restricting fitting mechanism. The key difference compared to the embodiment of fig. 1 is that the elevation angle of all the blocking faces in the blocking engagement is zero, see fig. 5 (j), the limiting engagement means is no longer limited by the limiting projection 114 of the self-locking or blocking tooth tip of the blocking face, and the auxiliary blocking ring is fixed circumferentially instead of rigidly integral with the auxiliary limiting ring, one attached to the second engagement element 80 and one attached to the second collar 206. Specifically, the inner ring surface of the blocking ring is provided with a radial protrusion 129, the protrusion 129 and a circumferential limiting groove 250 attached to the second shaft sleeve 206 are matched to form a radial type limiting embedding mechanism, and the circumferential freedom degree X of the limiting embedding mechanism is larger than the entrance margin K of the blocking embedding mechanism. Further, the circumferential relative positions of the stopper fitting mechanism and the circumferential dimensions of the respective members are determined with the effect that, for the one-way stopper fitting mechanism: in the state of the fitting of the barrier fitting mechanism, the radial projection 129 must be able to contact the stopper working face of the stopper groove 250 in the non-working direction; the bidirectional blocking embedding mechanism comprises: the spacing engagement means must not prevent the blocking engagement means from establishing a blocking relationship in both directions, but is preferably positioned such that both means can be simultaneously centrally engaged.

It should be noted that the radial limiting scheme is a scheme in which a slight collision occurs after overload, and the engagement reset after overload can only adopt a reverse rotation method, but cannot adopt a forced engagement method.

FIG. 9 shows an embodiment of the present invention having in situ chimerization capabilities. 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 complete and unique 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 tooth grooves 56 of the first engaging element 50 is blocked by the tooth groove stopper 68 to be differentiated into the short tooth groove 66, while the length of one of the second working teeth 82 is shortened to be differentiated 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, the complete sealing of the tooth grooves 66 and the non-equidistant circumferential spacing of the running gear ring also serve the purpose of a completely circumferential single engagement.

Several embodiments with independent modalities are shown in fig. 10-13. 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. 10 has its simplest form, the first engagement element 50 being rigidly integral with the first hub 204, and the adjustment nut 164 directly coupling the first engagement element 50 and the spring 160. All the configurations of the second coupling element 80 are almost entirely as shown in fig. 2, the only difference being that the characteristic curve on which the torque is transmitted is changed from an inner cylindrical surface to an outer cylindrical surface, i.e. the tooth flanks of the gear teeth 98. Fig. 11 is an addition to fig. 10 of a packaging shell consisting of a bowl-shaped shell 226 and an annular end cap 230, which are fixed therebetween by screws 234. The bowl-shaped housing 226 is circumferentially fixed to the second engagement element 80 by spline teeth 228 on its inner bore surface, enabling torque transmission 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 nested 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. 12 is a modification of fig. 11. The spring 160 is indirectly mounted 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. 13, the second hub 206 and the first coupling element 50 are both part of the package housing. The equivalent component of the adjustment nut, the bowl-shaped housing 226, is directly associated in screw thread with the outer cylindrical surface of the first engagement element 50, so as to achieve the axial support and adjustment of the chimeric spring 160.

Fig. 14 shows an embodiment of a pin-type safety coupling. Wherein the pin 242 is closed on both sides by retainers 244. In the present embodiment, the second bushing 206 is a preferred form as the drive shaft.

Fig. 15 shows an embodiment of a one-way security clutch in the form of a duplex. The first engagement element 50 is a reference ring of the blocking ring 100, the inner bore surface of which is the reference cylindrical surface 72, and the second engagement element 80 is an auxiliary ring of the auxiliary blocking ring. The end-face radial teeth at both ends of the first engagement element 50 and the blocking ring 100, respectively, are strictly symmetrical about the respective axial symmetry plane. 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 engaging springs 160 are pressed against the second engaging element 80 by both ends, respectively, and 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 inside 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 increase the projection 114 on the blocking ring 100 in such a way that it always engages in the annular groove of the second coupling element 80. Detent lever 136 and detent return spring 138 are disposed in radial bores in the axial plane of symmetry on reference cylindrical surface 72. A circumferential ratchet 134 is formed in a central recess of an outer cylindrical surface of the blocker ring 100, and a detent lever 136 is inserted therebetween to restrain the blocker ring 100 to the reference cylindrical surface 72. The ratchet-pawl mechanism only allows the blocker ring 100 to continue rotating on the reference cylindrical surface 72 in the overload direction, and the reverse direction is blocked. The number of teeth and the circumferential position of the ratchet teeth 134 are determined in such a way that the stop ring 100 stays at a position where the engagement mechanism can be engaged and reset when the stop ring is stopped by the detent lever 136. And the optimal positioning is that the auxiliary blocking teeth are centered in the tooth slot of the blocking teeth after being embedded. The same number of teeth as the working teeth and the same uniform distribution are good choices.

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 of 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 the present embodiment are numerically smaller than δ and ρ in the embodiment of fig. 1, since there is no 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 surface is forcibly destroyed by utilizing the unidirectional of the ratchet mechanism instead of utilizing 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. The stop recesses 126 are provided at corresponding positions on the outer circumferential surface of the blocking ring 100, and the stop pin coupling ring 180 is arranged on the corresponding outer circumferential surface of the first coupling member 50, the inner circumferential surface of the ring being a grooved cam surface which engages with the radially outer end of the stop pin 182 and is axially retained by the latter, so that when the stop pin coupling ring 180 is circumferentially stopped, i.e. the cam is rotated relative to the first coupling member 50, the stop pin 182 is radially pressed into the stop recesses 126 of the blocking ring 100, thereby circumferentially stopping the blocking ring 100 at a relative position where it loses its axial blocking capability. With the circumferential detent removed, centrifugal force and radial spring force will again force the anti-rotation stud 182 back to the maximum outer diameter of the cam surface, thereby ejecting its pin out of the anti-rotation recess 126. To improve reliability, the blocker ring 100 may also be made in the form of a resilient split ring 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 clear 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 transmission shafting which must transmit high rotation speed and high torque without stopping, such as wind power generation. Moreover, due to the trapezoidal cross section of the working teeth, even if a form and position error exists between the units in the circumferential direction, the slight axial separation of one sub-clutch mechanism in the force transmission state is caused, 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. 16 shows the package form of fig. 15. Wherein the first engagement element 50 is given 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. 17 shows a modified embodiment of fig. 15. 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 takes the minimum clearance amount as the upper limit, after the blocking embedding mechanism at one end is embedded and reset, the blocking embedding mechanism at the other end can not be in a blocking state and can only enter the embedding process or complete the embedding process. 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 to fig. 15, this embodiment can conveniently achieve bidirectional operation by simply forming the bi-directional stop faces 108 on the stop rings 100a and 100 b.

Figure 18 shows the only embodiment of the invention with tension springs. The layout of the two fitting mechanisms is completely as shown in fig. 17, the two blocking rings 100 are both open elastic rings, the rotating 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 projecting from respective axial holes of the second engagement elements 80 to be respectively associated with 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. 19 shows a fourteenth embodiment of the present invention. Corresponding to the results of radially interchanging the component positions in fig. 16. The packaging form is completely the same as that shown in fig. 12, and only one sub-clutch mechanism is added. As with fig. 15-17, 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 collar 204 will change slightly, unless a symmetrical adjustment is employed as shown in fig. 21. This amount of change is equivalent to half the total compression of the spring 160, but its effect is easily eliminated.

Fig. 20 shows a fifteenth embodiment of the invention, in the form of a tooth coupling, which is a variation of fig. 19. 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. 19 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. 20 (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 stopper rings 100 in this embodiment cannot achieve both rigidity integration and circumferential interlocking, and therefore reliability is relatively lowered.

Fig. 21 shows a sixteen embodiment of the present invention, a modification of fig. 15. 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. For this purpose, a constraining snap ring 122 is specially provided, by which the annular base 112 of the blocking rings 100a and 100b is pressed, so as to axially fix the latter two on the outer cylindrical faces of the spline teeth of the second engaging element 80, always abutting 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 top 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 degree of circumferential freedom is already described in the embodiment shown in fig. 17, and will not be repeated here. Specific structures of the bicyclic ring are shown in FIGS. 21 (b) to (d).

It is understood from fig. 20 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. 22, the first coupling element 50 is a reference ring of the stop ring 100 and the second coupling element 80 is a secondary primary ring of the secondary stop ring, the stop-and-ring mechanism being located radially and axially inside the working engagement mechanism. 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. 21 (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 secondary blocker ring 80 is shown in figures 20 (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, respectively, and are radially supported and integrated as a sealed housing. 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. 23 shows yet another tooth coupling. The layout form of the sub-clutch mechanism is basically as shown in FIG. 22. The difference is that the two stop rings are connected into a rigid body by the radial base body, so that the two first joint elements 50 cannot be pressed to adjust the embedded elastic force and only limited by the two snap rings 210; a form of unidirectional drive unidirectional constraint ratchet mechanism is employed as shown in fig. 15. 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 a pawl lever 136 and a pawl return spring 138 are arranged in a radial through hole in the reference cylindrical surface 72 and the ratchet teeth 134 are integrally formed on corresponding inner shoulders of the inner hole 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 also only a slight frictional resistance torque from the ratchet mechanism, as is the case in fig. 15. Of course, the ratchet mechanism can also be arranged in an axial manner in the corresponding annular revolution region between the blocking ring 100 and the first engaging 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. 24 shows yet another encapsulated two-up embodiment. Corresponding to the results of radially interchanging the arrangement of the components in fig. 22. 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 radially outside the second working teeth 82, i.e. the stop-and-ring mechanism is axially inside the working engagement mechanism and radially outside the working engagement 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 tubular housing ring gear 224, radially positioning the latter on the second hub 206 and constituting a containment casing. The adjusting nut 164 is coupled to the outer cylindrical surface of the ring column boss 248 of the annular end cap 230a in a threaded manner, and presses and adjusts the axial distance between the two first engaging elements 50 by the axial stud of the middle ring 190, thereby achieving the effect of adjusting the axial engaging elastic force of the two working engaging mechanisms.

As shown in fig. 24 (b), the two stop rings 100 are identical in structure and are each a shrink type elastic split ring, and all the stop 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 reside 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 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. 17 and will not be repeated here. Referring to fig. 20 (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 should be understood, therefore, that the foregoing description and drawings, while indicating only limited embodiments of the invention, are given by way of illustration only, since various changes, equivalents, substitutions and alterations in the structure or arrangement of parts thereof will be seen without departing from the spirit and scope of the inventive concept.

Claims (10)

1. A zero-collision jaw-type universal safety clutch comprises a first joint element, a second joint element, a spring and an adjusting nut, which are all arranged on the basis of the same rotating axis, wherein the first joint element and the second joint element axially and oppositely form a working embedding mechanism with the double functions of torque transmission and overload separation; the method is characterized in that:

the blocking and embedding mechanism is used for blocking the axial embedding of the working embedding mechanism in the axial separation overload state and is formed by axially embedding a blocking ring and an auxiliary blocking ring, and radial blocking teeth with axial blocking effect are arranged on the two rings; 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; and

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 main ring are integrated into a whole, and the auxiliary limiting ring and the auxiliary stop ring are circumferentially fixed; when the axial separation distance of the blocking embedding mechanism is larger than the minimum blocking height, the circumferential freedom degree of the limiting embedding mechanism is larger than the entrance margin of the blocking embedding mechanism.

2. The zero-crash dog-type universal security clutch according to claim 1, wherein: the blocking embedding mechanism is axially positioned in the working embedding mechanism and radially positioned in or out of the working embedding mechanism; the auxiliary blocking ring is integrated with an auxiliary ring which is any one of the joint elements forming the working embedding mechanism; the stop ring is supported unidirectionally by the reference ring base end face, and the sliding end face and the reference end face form a circumferential free sliding friction pair; the reference ring is an engagement element of the working engagement mechanism that is axially opposed to the attachment stopper ring.

3. The zero-crash dog-type universal safety clutch according to any one of claims 1 to 2, wherein: the stop ring in the fitted state can be relatively stationary on the reference end surface or the reference cylindrical surface of the reference ring by the restraint.

4. The zero-crash dog-type universal safety clutch according to any one of claims 1 to 2, 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.

5. The zero-crash dog-type universal safety clutch according to any one of claims 1 to 2, wherein:

(a) The auxiliary limiting ring and the auxiliary blocking ring are the same ring, the limiting embedding mechanism and the blocking embedding mechanism are overlapped 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;

(b) In the control embedding mechanism, the working faces of tooth crests of the blocking tooth and the auxiliary blocking tooth are spiral faces with a lead angle 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 teeth to successfully self-lock in the blocking working condition;

(c) The maximum limit embedding depth of the limit embedding mechanism is larger than the full-tooth embedding depth of the working embedding mechanism.

6. The zero-crash dog-type universal security clutch according to claim 5, wherein: the side face of the limiting bulge in the control embedding 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 of the blocking working face, which can enable a static friction pair formed by axial contact of the blocking working face of the blocking tooth and the blocking working face of the auxiliary blocking tooth to successfully self-lock in the blocking working condition.

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

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

the two second joint elements are fixed with the second rotating shaft in the circumferential direction and axially slide, and are respectively axially embedded with one first joint element to form two working embedding mechanisms with double functions of torque transmission and overload separation, the two working embedding mechanisms have the same stable working condition, and the stable working condition is an axial embedding force transmission state or an axial separation overload state;

at least one spring, which acts on the non-jogged end surfaces of the two second jointing elements respectively and provides axial joggling force for the two working joggling 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, have the same stable working condition and respectively form a group of sub-clutch mechanisms with one working embedding mechanism; the stable working condition is an axial embedding state or an axial separation blocking state; in each group of sub-clutch mechanisms, the blocking embedding mechanism is used for preventing the axial embedding of the same group of working embedding mechanisms in the axial separation overload state and is formed by axially embedding a blocking ring and an auxiliary blocking ring, radial blocking teeth with the axial blocking effect are arranged on the two rings, and the minimum blocking height of the blocking embedding mechanism is greater than the initial separation height of the same group of working embedding mechanisms in two rotation directions and is less than the full-tooth embedding depth of the same group of working embedding mechanisms; and

and each group of sub clutch mechanisms is provided with a limiting embedding mechanism for limiting the circumferential relative position of the stop ring in the stopping embedding mechanism, the limiting embedding mechanism consists of the stop ring and an auxiliary limit ring, the auxiliary limit ring and the auxiliary limit ring are integrated into a whole, the auxiliary limit ring and the auxiliary stop ring are circumferentially fixed, and when the axial separation distance of the stopping embedding mechanism is greater than the minimum stopping height, the circumferential freedom degree of the limiting embedding mechanism is greater than the entrance margin of the stopping embedding mechanism.

8. A twin zero-crash dog-type universal security clutch according to claim 7, wherein: the two blocking embedding mechanisms are axially and respectively positioned in the working embedding mechanisms of one group of sub-clutch mechanisms, and radially and respectively positioned in or out of the same group of working embedding mechanisms; in each set of sub-clutch mechanisms, the auxiliary blocking ring is integrated with an owner ring which is any one of the engagement elements constituting the same set of working engagement mechanisms; in each group of sub-clutch mechanisms, the barrier rings are supported in a single direction by the reference ring reference end faces of the respective reference rings, and the sliding end faces and the reference end faces form circumferential free sliding friction pairs; the reference ring is a side engagement element of the same set of working engagement means axially opposed to the dependent ring of the dependent blocker ring.

9. A dual-link zero-crash dog-type universal security clutch according to claim 8, wherein: the circumferential relative position between the two stop rings is constrained by a circumferential linkage mechanism, the mechanism is an axial embedding mechanism which is always in an embedding state and is positioned between the two stop rings, and the mechanism is composed of the two stop rings directly or indirectly.

10. A twin zero-crash dog-type universal security clutch according to claim 7, wherein:

(a) The two blocking embedding mechanisms are axially connected in a mode that the two blocking rings are formed into a whole, are both positioned in the two working embedding mechanisms in the axial direction and are positioned in or out of the two working embedding mechanisms in the radial direction;

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

(c) Said secondary blocker ring being integral with an owner ring, which is a second engagement element; the first engagement element is a reference ring, the blocking ring being fitted inside or outside the reference ring quasi-cylindrical surface.

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