CN201041203Y

CN201041203Y - Axially self-controlled clutch separation and maintenance device

Info

Publication number: CN201041203Y
Application number: CNU2007201469093U
Authority: CN
Inventors: 洪涛
Original assignee: Individual
Current assignee: Individual
Priority date: 2007-04-06
Filing date: 2007-04-06
Publication date: 2008-03-26
Anticipated expiration: 2017-04-06

Abstract

The utility model relates to a separation retaining mechanism of an axial self control clutch which consists of a blocking ring, an attached blocking ring, and an attached limiting ring. The blocking ring and the attached blocking ring are combined into an interlocking blocking mechanism, to retain the separation state of the working connecting mechanism to be served, and the blocking ring and the attached limiting ring are combined into an interlocking limiting mechanism, to retain a steady opposite relation between gear tops inside the interlocking blocking mechanism. The utility model is characterized in that the blocking ring is reposed on a basic reference end surface by being constrained, the interlocking blocking mechanism is arranged inside the working connecting mechanism in the axial direction, and arranged inside or outside the working connecting mechanism in the radial direction, and the interlocking limiting mechanism and the interlocking blocking mechanism are fixed in the circumferential direction. Compared with the retaining mechanism in a jaw type self-locking differential device, the structure of the utility model is simple, the reliability during the separation blocking and the interlocking resetting is higher, to be more important, the utility model is not influenced by the size and the parameter of a compressed spring, an axial presser of the compressed spring can be adjusted, the assembly is simple, therefore, the utility model can be suitable for all axial spring compressed type self control clutches.

Description

Separation holding mechanism of axial self-control clutch

Technical Field

The utility model relates to an axial pressfitting formula automatic control clutch among the mechanical transmission field, a retaining mechanism who is used for maintaining its disengagement state behind the axial separation of spring pressfitting formula automatic control clutch is particularly concerned with, belongs to the mechanical transmission field.

Technical Field

In the axial spring press-fit type self-control clutch in the prior art, except for a jaw self-locking differential, the jaw overrunning clutch, the safety clutch and the spring steel ball type safety clutch do not have the state retaining function after axial separation. After the driving and driven engagement elements are axially separated, the relative rotation of the driving and driven engagement elements can cause impact, collision, noise and excessive wear of the end face teeth, and the jaw safety clutch with large axial elastic engagement force can even be serious to the extent of breaking the end face teeth. Therefore, in both theoretical and engineering fields, it has been widely recognized in the transmission field that the axial spring press-fit type self-controlled clutch is not suitable for shafting transmission parts with high relative rotating speed or high load inertia of the separated driving and driven engagement elements. For example, the working speed of the jaw clutch is not more than 200 r/min generally, the load is not more than 400 N.m, and the highest working speed of the spring steel ball type safety clutch is not more than 400 r/min generally on the load of 1,000N. M magnitude. Therefore, their application is greatly limited, making it difficult to utilize the advantages of great torque transmission, simple structure, and no slip and heat generation after engagement. Despite the technology of possessing a separate holding mechanism in a jaw self-locking differential, the technology has not been applied to other related clutches until now due to the influence of the special layout form of the driving ring, the severe requirements on the spring stiffness, the spring length and the assembly, and the limitation factors of the incapability of adjustment and the like. Moreover, the reliability problems of the two processes of separation blocking and embedding resetting exist.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a simple structure, reliable operation and do not receive spring parameter stability influence, adapt to different axial gomphosis power, assemble simple can be used to all axial spring pressfitting formula automatic control clutch's separation state retaining mechanism to eliminate or eliminate the original impact and the collision of this type of clutch basically.

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 limit 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 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.

Angle δ: 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 reference end surface or the reference cylindrical surface of the reference ring to form a sliding friction pair, on the other hand, the blocking working surface of the blocking tooth of the blocking ring 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 by only the static friction pair, the static friction pair needs to be self-locked, wherein the minimum lift angle of the blocking working surface which can ensure the self-locking of the static friction pair is defined as delta.

max (): take the maximum function, i.e., extract the maximum in the column of numbers in parentheses.

Limiting the working surface: a limiting surface is given to the circumferential relative position of the blocking ring. Namely, the circumferential interface of the stopper groove in the stopper fitting mechanism.

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.

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, whereas the distance may be non-zero, turning in the opposite direction allowed by the design.

Full tooth engagement depth: the extent of the change in axial distance between the first and second engagement elements is such that upon one revolution of the two components of the axial engagement or engagement mechanism relative to each other, axial contact is ensured irrespective of the initial separation height. Which may also be referred to as full tooth depth of engagement.

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.

Crest barrier angle Θ: under the action of the pressing spring, when the influence of the blocking embedding mechanism is not considered, the automatic control clutch in the axial separation state has the aim of avoiding the blocking of the tooth crest face related to the automatic control clutch in the automatic control clutch to achieve the axial connection, and the two connection parts of the automatic control clutch need to be continuously staggered with each other at the maximum circumferential angle.

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 so-called "barrier ring" is independent barrier ring's abbreviation.

In order to achieve the above object, the separation maintaining mechanism of the axial self-control clutch of the present invention is composed of a first engaging element, a second engaging element, a spring and a spring support based on the same axial lead; the second engaging element is axially movable and axially interposed between the first engaging element and the spring, the other end of the spring being supported by the spring support; under the action of the spring, the first jointing element and the second jointing element axially and oppositely form a working jointing mechanism, when the first jointing element and the second jointing element rotate synchronously, the axial distance between the first jointing element and the second jointing element is minimum and is in a stable jointing state, and when the first jointing element and the second jointing element rotate asynchronously, the axial distance between the first jointing element and the second jointing element is maximum and is in a separated state; the method is characterized in that: 1) The device is provided with a blocking embedded mechanism for blocking the axial joint of the working joint mechanism in a separated state, the blocking embedded mechanism is axially positioned in the working joint mechanism, the blocking embedded mechanism is radially positioned in or out of the working joint mechanism and is formed by axially embedding a blocking ring and an auxiliary blocking ring, the same number of radial blocking teeth with axial blocking effect are arranged on the periphery of the embedded end surfaces of the two rings, the blocking working surfaces of the blocking teeth are all spiral surfaces with the lead angle of lambda, and lambda is less than or equal to max (0, delta); the minimum blocking height of the blocking embedding mechanism is larger than the initial separation height of the working engagement mechanism in two rotation directions and smaller than the full-tooth engagement depth of the working engagement mechanism; the secondary blocker ring being rigidly integral with an owner ring, the owner ring being either the first engagement element or the second engagement element; 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 second joint element or a first joint element which is opposite to the auxiliary main ring of the auxiliary blocking ring; 2) The limiting embedding mechanism is arranged for limiting the circumferential relative position of the blocking ring in the blocking embedding mechanism and consists of the blocking ring and an auxiliary limiting ring; the auxiliary limiting ring is rigidly integrated with the auxiliary main ring, and the auxiliary limiting ring is circumferentially fixed with the auxiliary stop ring; the circumferential freedom degree of the limiting embedding mechanism is larger than the entrance margin of the blocking embedding mechanism.

As a holding mechanism with a bidirectional blocking function, the initial separation height of the working joint mechanism in two relative rotation directions is zero, blocking working surfaces are respectively and correspondingly formed on two sides of each tooth crest in the blocking tooth mechanism, and the entrance margin of the blocking embedding mechanism is larger than the tooth crest blocking angle of the automatic control clutch.

The limit embedding mechanism in the holding mechanism can be a pin-slot type limit mechanism which is arranged between two cylindrical surfaces or between two end surfaces of the auxiliary limit ring and the stop ring and consists of a bulge and a groove.

For a desired performance, the blocker ring in the engaged state may rest relatively on a reference end face or a reference cylindrical surface of the reference ring by being constrained.

In addition, the stop ring is regarded as an annular component consisting of two parts, namely an annular base body and end face radial teeth, and the end face radial teeth can be formed on two ends or inner and outer cylindrical surfaces of the annular base body.

Alternatively, the auxiliary blocking ring can be manufactured separately and then forms a rigid and integrated combined component with the main ring of the auxiliary blocking ring in a welding mode, a direct interference fit mode or an axial pin hole interference fit mode.

The utility model discloses in, through adding the gomphosis mechanism that blocks that plays the axial and block the effect in the work coupling mechanism to the automatic control clutch, perhaps make this mechanism and the fixed form of the spacing gomphosis mechanism circumference of its inside circumference relative position of restriction, perhaps all arrange the constitution both sides of work coupling mechanism as the mode of the owner's ring that belongs to of attached barrier ring, realized well the utility model discloses a purpose has kept blocking the inside circumference relative position of gomphosis mechanism under the operating mode well, has reached and has kept and has blockked the relation, prevents that the automatic control clutch joint from restoreing and eliminate the purpose of assaulting or colliding, has high reliability moreover, irrelevant with pressfitting spring performance, adjustable axial separation power and the simple advantage of assembly. The shaft system is suitable for shaft system parts with high rotating speed and large torque. In addition, the stop ring has simple structure and low manufacturing cost.

Drawings

Fig. 1 is an axial sectional view of an overrunning clutch according to an 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), and (b) is a front view.

Fig. 3 is a schematic view of the blocker ring of fig. 1, with (a) a front view and (b) an axial half-sectional view of the left side view.

Fig. 4 is a partial development view of radial projection 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 schematic view of the tooth profile relationship of the working interlocking mechanism in an interlocking state, (b) is a schematic view of the tooth profile relationship of the corresponding blocking interlocking mechanism in (a), (c) is a schematic view of the tooth profile relationship of the working interlocking mechanism in a blocking condition, (d) is a schematic view of the tooth profile relationship of the corresponding blocking interlocking mechanism in (c), and (e) is a partial enlarged schematic view of (a), and arrows represent relative overrunning rotation directions.

Fig. 5 is an axial sectional view of a safety clutch according to a second embodiment of the present invention.

Fig. 6 is an axial sectional view of an overrunning clutch according to a third embodiment of the present invention.

Fig. 7 is an axial sectional view of an overrunning clutch according to a fourth embodiment of the present invention.

Fig. 8 is an axial sectional view of a spring steel ball safety clutch according to a fifth embodiment of the present invention.

Fig. 9 is an axial sectional view of a self-locking differential according to a sixth embodiment of the present invention.

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 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.

As shown in fig. 1 to 4, a first embodiment of the present invention is a one-way overrunning clutch in the form of a wheel-axle transmission. Wherein the first engagement element 50 is a reference ring of the blocker ring 100, the second engagement element 80 is a primary ring of the secondary blocker ring, and the second collar 206 is a primary ring of the secondary stop ring. The first engagement element 50 is fitted over a smooth section of the second sleeve 206 with a bearing 216 therebetween to unidirectionally restrain the first engagement element 50, which in turn is unidirectionally restrained on the second sleeve 206 by the snap ring 210 a. Second engaging member 80 is received over the splined tooth segment of second hub 206 and is circumferentially fixed therebetween. The first engaging element 50 and the second engaging element 80 constitute a working engaging mechanism. The fitting spring 160 is mounted between the non-fitting end surface of the second engaging element 80 and the spring seat 162. The spring seat 162 is axially defined on the outer end side of the second bushing 206 by a snap ring 210 b. The stop ring 100 is located radially inside the working engagement means, with its sliding end face 124 facing the reference end face 70 of the first engagement element 50, and constitutes a stop engagement means with the secondary stop ring, and a limit engagement means with the limit pin 134 embedded on the second collar 206. The wave restraining spring 120 is interposed between the blocker ring 100 and the end face of the external spline teeth of the second hub 206.

On the second coupling element 80 shown in fig. 2, the second coupling teeth 82 are radial teeth with a saw-tooth-shaped cross section, which are arranged on the outer ring side of their engagement end faces, and the auxiliary blocking teeth 142 are arranged on the inner ring side of their engagement end faces. The secondary blocker tooth 142 is radially integral with the second engagement tooth 82 and has a top land that is the blocker working surface 148. To simplify construction and ease of manufacture, the blocking face 148, flank 150a and root face 146 of the secondary blocking tooth are substantially coplanar with the second engaging tooth top face 84, flank 88a and root face 86, respectively. That is, the satellite blocking tooth 142 is fully served by the radially extending portion of the second engagement tooth 82. The layout and tooth profile of the mating end face of the first engaging element 50 is identical to that of the second engaging element 80, except that there is no secondary blocking tooth, and the engaging tooth top face has a curvature.

In the blocking ring 100 shown in fig. 3, the blocking teeth 102 are uniformly and integrally formed on the outer circumferential surface of the annular base 112, and the limiting recesses 136 are uniformly and integrally formed on the inner circumferential surface of the annular base 112. Axially, barrier tooth 102 is significantly higher than annular base 112. The blocker tooth tip land 104 is the blocker working face 108 and the

blocker tooth flanks

110a, 110b define a tooth slot that receives the secondary blocker tooth 142 with a circumferential degree of freedom greater than zero therebetween. The top end of the blocking tooth 102 is the engaging end of the blocking ring, and the bottom end face thereof is the circumferential sliding end face 124 of the blocking ring 100.

As shown in FIGS. 4 (a), (b) and (e), the first engagement element 50 and the second engagement element 80 constitute both a force-transmitting engagement mechanism and a disengagement engagement mechanismThe unidirectional working engagement mechanism, the barrier ring 100 and the auxiliary barrier ring form a unidirectional blocking embedding mechanism, and the circumferential freedom degree of the two embedding mechanisms can be zero. The limit pin 134 on the second shaft sleeve 206 and the limit groove 136 of the stop ring 100 form a limit fitting mechanism (shown in a dotted line), and the circumferential degree of freedom X of the mechanism is greater than the entrance margin K of the stop fitting mechanism, namely, X is greater than K, wherein

(the relevant symbols indicate the circumferential angle between the corresponding points). The circumferential relative positions of the stopper fitting mechanism and the barrier fitting mechanism and the circumferential dimensions of the respective members are determined to have such an effect that the stopper pin 134 must be able to contact the stopper working surface 138b of the stopper groove 136 in the state of the barrier fitting mechanism fitting. In addition, in the fitted state,(the horizontal line symbol represents the axial distance, the same applies hereinafter) wherein D _t Representing the initial separation height of the working engagement mechanism in the non-designed separation override direction, which is constant to zero in the designed separation override direction, D _c Representing the full tooth engagement depth of the working engagement mechanism,

representing the minimum blocking height of the blocking engagement means. The interrelation of the mechanisms in the overtaking condition is shown in fig. 4 (c) and (d).

It will be understood that in the present embodiment, three circumferentially spaced retaining recesses 136 and three circumferentially spaced retaining pins 134 are provided as secondary retaining teeth, the blocking ring 100 and the secondary blocking ring each have three radially spaced identical

radial teeth

102 and 142, and the arrangement that the secondary retaining teeth 142 circumferentially extend exactly radially of the second engagement teeth 82 is not essential, but is purely for the sake of simplicity of construction and process. In the special case where the secondary stopper ring cannot be formed integrally with the primary ring, the secondary stopper ring can be handled by manufacturing it separately in advance and then rigidly combining it with the primary ring by welding or interference fit. Similarly, the restraining spring 120 may be any type of elastic body other than a wave spring.

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

In the engaged state, the torque on the first engaging element 50 (counterclockwise as viewed from the left side of fig. 1) is transmitted to the second engaging element 80 via the working engaging mechanism and then to the second hub 206 via the spline pair, or is transmitted in the reverse path when reversed. When the relative rotation speed of the two engaging elements in the designed direction of mutual separation is greater than zero, i.e. the relative rotation shown by the arrows in fig. 4 (c) and (d) occurs, the overrunning clutch begins to separate and overrun, and the second engaging tooth 82 and the first engaging tooth 52 overcome the pressing spring 160Are slidably moved up and down along the disengaging tooth surfaces 58a and 88a until the axial separation distance between the two reaches D _c . Due to the existence of parameters

And the blocking ring 100 is relatively stationary on the first coupling element 50 by the spring 120, so that, as long as the entrance margin K of the blocking engagement is not far from its lower limit value, the process of overriding the disengagement is sufficient to ensure that D is reached in the first synchronization at the distance of axial disengagement of the blocking engagement _c At this point, the secondary blocker tooth blocking face 148 has jumped the blocker tooth blocking face 108 and established an axial blocking relationship. In this blocking condition, the rotation of the second engagement element 80 relative to the first engagement element 50 and the blocking ring 100 is a jump-slip with a jump or collision amplitude D _c And

the difference between them. As shown in FIGS. 4 (c) and (d), when the stopper pin 134 fixed to the second engaging element 80 in the circumferential direction abuts against the stopper working surface 138a of the stopper groove 136, the stopper ring 100 is driven by the stopper pin 134 to rotate synchronously with respect to the first engaging element 50, and the stopper ring 100 and the auxiliary stopper teeth 142 are located immediatelyIn a relatively static state, the blocking working condition of the blocking embedding mechanism is stabilized.

Compared with the prior art, the above separation blocking process is simple and reliable, the blocking ring 100 is passively stopped on the reference ring first joint element 50, no matter what the ring does in the circumferential direction or the axial direction is needed before the blocking relation is established, no problems such as motion response, idle stroke, driving friction force and the like exist, and all separation actions are executed by the driven ring which is rigidly integrated with the auxiliary blocking ring and is a prime mover leading to the separation blocking action, so that the separation blocking relation is particularly favorable for establishing the blocking relation, and the separation blocking relation is more obviously superior to the prior art. Moreover, locating blocker ring 100 radially inward of the work engagement mechanism also reduces residual torque and wear consumption. In addition, the blocking working surface 108 of the present embodiment may also be a helicoid with a lead angle λ, λ < δ. 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 embedding mechanism is equal to or more than D _c Until the stop pin 134 abuts against the stop working surface 138a of the stop groove 136. That is, with proper design, one can achieve an overrunning rotational condition with zero or no contact between the two engagement elements. Because of the limitation that lambda is less than or equal to max (0, delta), the two sides in the blocking embedding mechanism can block the opposite-top contact between the tooth tops of the teeth, and can not self-lock when delta is more than 0 or can self-lock when delta is less than 0 but is subject to parameter

The resulting jump-slip pattern is broken, and therefore, the stopper ring 100 cannot automatically follow the second engaging element 80 to rotate integrally without the effect of the limit fitting mechanism regardless of the forward or reverse overrun, but is stationary on the reference end surface 70 of the first engaging element 50.

Therefore, the fitting and resetting of the present embodiment is very simple and natural, and it is sufficient to perform reverse override. That is, the satellite blocking tooth 142 is rotated only by relatively rotating the second engaging member 80 with respect to the first engaging member 50 in the direction opposite to the arrow in FIGS. 4 (c) and 4 (d)Can slide off the blocking tooth blocking working surface 108 and can be synchronously engaged and reset together with the second engaging tooth 82. However, before the point a of the auxiliary blocking tooth blocking working surface 148 does not slip off the point G of the blocking tooth blocking working surface 108, the second engaging tooth 82 circumferentially misses the notch of the first engaging tooth, and the fitting reset is completed by rotating one tooth, but the phenomenon of seizing or tooth breakage never occurs. Because of the existence of

I.e., the initial separation height, the two engaging

teeth

52 and 82 must reverse beyond separation. At the same time, the limit pin 134 interferes with the limit groove 136When the working surface 138B is limited, the rear point B of the tooth top surface 148 of the subsidiary blocker tooth does not miss the point H of the entrance of the tooth space of the blocker tooth, and the entire tooth top surface 148 is still positioned above the entrance of the tooth space of the blocker tooth. As can be seen from the above description, the fitting-returning process of the present embodiment is simple and reliable compared to the prior art, and besides the spring 160 is required to provide the fitting pressure, there is no relation to the size, specific performance parameters and stability of the spring. The influence of the fitting spring 160 on the fitting return process of the block fitting mechanism is completely eliminated, so that it is possible to basically change the fitting pressure and adjust the size of the spring. Naturally, the manufacturing accuracy, cost and clutch assembly requirements of the spring 160 will be greatly reduced and the service life significantly improved.

The present embodiment can also be used as a jaw-type safety clutch, or the snap ring 210 is replaced by the adjusting nut 164, and the outer end of the second sleeve 206 is threaded to form an adjustable safety clutch, or the two engaging teeth are designed to be an upper phase safety clutch with a regular trapezoid cross section, or the present embodiment can also be modified to have a two-way safety clutch as shown in fig. 5. In the bidirectional safety clutch, a block fitting mechanism having a bidirectional block function is preferably used. The mechanism is almost identical to the one-way blocking embedding mechanism in working principle and basic structure and parameter requirements, and is only different in that the inlet margin K in the two-way blocking embedding mechanism is required to be larger than the tooth crest blocking angle theta of the automatic control clutch, and the relative circumferential positions of the limiting embedding mechanism and the blocking embedding mechanism and the circumferential sizes of the respective components are determined with the effect that the limiting embedding mechanism cannot prevent the blocking embedding mechanism from establishing blocking relation in two directions, and the optimal positioning is that the two mechanisms can be simultaneously embedded in a centered mode. In the embedding and resetting process of the bidirectional blocking mechanism, the parameter limitation of K & gttheta is enough to ensure the success of embedding and resetting during reverse overrunning, and the condition of reverse separation and blocking cannot be entered. In the bidirectional blocking/fitting mechanism, the auxiliary blocking tooth 142 is preferably formed by two separate radially extending portions of the second engaging tooth 82 in the circumferential direction, and the middle portion of the tooth is discontinuous.

It should be noted that the constraint of the blocker ring 100 is not required in this embodiment, but is done to ensure that the blocking engagement mechanism is positively capable of establishing an axial blocking relationship at a 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 open ring with a shoulder, or an elastic open 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, the auxiliary blocking ring (teeth) and the restraining method of the blocking ring 100 are more thoroughly described in the present patent application 'basic jaw self-locking differential' and 'pressing jaw single-and two-way overrunning clutch', which are incorporated by reference in their entirety and will not be described in detail herein.

It should be noted that, since the basic structures, basic relationships, basic parameter requirements, basic operation principles and processes of the blocking engagement mechanism and the limiting engagement mechanism are completely the same or similar, repeated descriptions will not be given in the following embodiments, and only the specific structures are explained as necessary.

As described above, the jaw-type bidirectional safety clutch shown in fig. 5 has a shaft-shaft transmission form, which is substantially the same as the embodiment of fig. 1, except that the radial protrusion 132 of the limit fitting mechanism is formed on the inner hole surface of the barrier ring 100, and the limit groove 136 is formed on the second hub 206. Has relatively high reliability and is simpler to assemble.

Fig. 6 shows the simplest embodiment of the invention, an overrunning clutch or a safety clutch in the form of a bore-shaft transmission. The first coupling member 50 is in a rigid integral form with the first hub 204 and the gear teeth 214 are formed directly on the outer cylindrical surface of the second coupling member 80. The most significant difference from the first two embodiments is that the components of the block fitting mechanism are axially reversed in position. That is, the secondary blocker ring has the first engagement member 50 as its primary ring and the blocker ring 100 has the second engagement member 80 as its reference ring. The blocking ring 100 is therefore axially unsecured and secured axially to the second engagement element 80 in a self-restraining manner by itself being formed as a resilient split ring with an external shoulder, the disengagement blocking process being identical to that of the prior art. Correspondingly, the secondary stop ring is fixed circumferentially to the secondary blocking ring, which is also replaced by the first engagement element 50. The secondary stop teeth are still served by the stop pin 134.

As long as the operation of the present embodiment is considered as the rotation and separation of the first engaging element 50 with respect to the second engaging element 80, the separation blocking and fitting resetting process is exactly the same, and the description thereof will not be repeated. It should be noted, however, that this embodiment still has many of the advantages of the embodiment of fig. 1 and 5, except for the lost motion problem due to the axial follow-up of blocker ring 100. Moreover, the tapered hole-shaped reference end surface 70 has the effect of raising the angle δ and reducing or eliminating the influence of the spring 160 during the fitting return process, for the amplification of the frictional force.

Fig. 7 is a schematic diagram of the structure of the encapsulated overrunning clutch for a bore-shaft transmission of the present invention. The first engaging element 50 is rigidly integrated with the first sleeve 204, and the stop ring 100 is fitted around the stepped cylindrical surface outside its engaging teeth, with the stepped end surface as its reference end surface 70. The second engagement element 80 is fitted over the first sleeve 204 in such a manner that the fitting end faces oppose each other, constitutes a working engagement mechanism with the first engagement element 50, and is circumferentially fixed to the tubular housing 226 by spline teeth on the outer cylindrical surface thereof to transmit torque. The tubular housing 226 has spline teeth 212 formed on an inner cylindrical surface thereof, and a key groove 230 and a snap ring groove 232 for fixing the ring gear formed on an outer cylindrical surface thereof. The wave restraining spring 120 is installed between the end face of the spline teeth 212 and the annular base of the blocker ring 100. The limit pins 134 are radially inserted into corresponding holes in the tubular housing 226, and form limit engagement means with limit grooves 136 formed in the annular base body of the stop ring 100.

Annular end caps

224a and 224b are secured to the open end faces at both ends thereof, respectively, by screws 228, and are radially fixed or sealed with the first sleeve 204 by the bearing 216 and the seal ring 218. The compression spring 160 is mounted between the annular end caps 224b of the second splice element 80.

In contrast to the embodiment of fig. 1, it is clear that the two are substantially in a relationship where the inner and outer rings are inverted with respect to each other. Therefore, both have almost the same characteristics, except that the residual torque of the latter is slightly greater.

Fig. 8 shows a schematic structural diagram of the spring steel ball safety clutch of the present invention. First coupling member 50 is received by one end of steel ball hub 90 on the outer cylindrical surface of the unthreaded end of second bushing 206 and is axially fixed by snap ring 210. The second bushing 206 is made rigid with the steel ball hub 90. The blocking ring 100 is placed in the end face circular groove of the fitted end of the first coupling element 50. The blocking teeth 102 are uniformly distributed on the outer cylindrical surface of the annular base body and the radial protrusions 132 are uniformly distributed on the inner cylindrical surface of the annular base body. The radial projection 132 and the limit recess 136 formed on the corresponding outer cylindrical surface of the second bushing 206 constitute a limit fitting mechanism. A restraining spring 120 is mounted between the annular base of the stop ring 100 and the steel ball hub 90, forcing the stop ring 100 against the wall of the end face circular recess, i.e. the reference end face 70, with the latter resting on this reference end face 70. The steel ball 60 is placed in the axial through hole of the steel ball hub 90 with its part-sphere inserted in one direction into a recess in the corresponding end face of the first coupling element 50 and at the same time with a part-sphere still resting in the other direction against the end face of the second coupling element 80. The second engagement member 80 is sleeved by the other end of the steel ball hub 90 on the outer cylindrical surface of the threaded end of the second bushing 206. The auxiliary blocking teeth 142 attached to the auxiliary blocking teeth penetrate through the avoiding through holes on the steel ball hub 90 and form a blocking embedding mechanism with the blocking ring 100. The spring 160 is installed between the second coupling member 80 and the adjustment nut 164. The adjustment nut 164 is threadably coupled to the external threads of the second bushing 206. The tapered bushing 208 is used to fixedly couple the second bushing 206 to the second shaft, and is axially biased by the bolt 220 and the threaded bore.

Although this embodiment is significantly different from the embodiment shown in fig. 1, the first engaging element 50 is used as a reference ring of the stop ring 100, the second engaging element 80 is used as a primary ring of the auxiliary stop ring, and the second bushing 206 circumferentially fixed to the second engaging element is used as a primary ring of the auxiliary stop ring. Therefore, the two mechanisms are completely the same from the perspective of the blocking embedding mechanism and the limiting embedding mechanism, and have completely the same working process and advantages. The description will not be repeated here. In addition, it is obvious that both mechanisms can also be arranged radially on the outer cylindrical surface of the steel ball embedding mechanism, but the residual torque is obviously increased.

Fig. 9 is a schematic structural diagram of the jaw-type self-locking differential according to the present invention. The first engaging element 50 in the form of a central ring is embedded in the inner bore of the driving force transmission ring 240 and is axially fixed by the retainer ring 210, the two second engaging elements 80 are mounted at the two ends of the driving force transmission ring 240, and the four engaging end faces of the four rings are opposite to each other in pairs to form two working engaging mechanisms which are actually separated and embedded mechanisms and two force transmission and embedded mechanisms. The two springs 160 press the second engaging element 80 from both ends, respectively, to ensure the continuation of the fitting pressure, and the outer ends of the two springs 160 are supported by the two spring seats 162. The two spring seats 162 are axially limited by the outer shoulders of the two second bushings 206 which are sleeved in the inner bores of the two spring seats. The two second shaft sleeves 206 are fixed circumferentially to the inner bores of the two second engaging elements 80, respectively, in a spline coupling manner, and spline teeth for transmitting torque to an output half shaft (not shown) are machined in the inner bores of the second shaft sleeves 206. The two stop rings 100 are respectively installed in the end face circular groove of the first engaging element 50 with the fitting end face facing the second engaging element 80, with the inner wall of the groove as a reference end face and the first engaging element 50 as a reference ring. The blocking teeth 102 are uniformly distributed on the outer cylindrical surface of the annular base body integrally, and the limiting grooves 136 are uniformly distributed on the inner cylindrical surface of the annular base body integrally. The limit groove 136 and the limit pin 134 embedded on the corresponding outer cylindrical surface of the second shaft sleeve 206 form a limit embedding mechanism. Two restraining springs 120 are respectively installed between the annular base body of the blocking ring 100 and the inner end faces of the external spline teeth of the second shaft sleeve 206, and the blocking ring 100 is tightly pressed on the reference end face. A central ring removal hole is radially machined into the four radial lugs of the drive transfer ring 240. The whole differential has completely symmetrical layout and structure in the axial direction, the number of the joint teeth and the number of the transmission teeth on all the components are completely the same and are circumferentially and uniformly distributed, and meanwhile, the radial teeth on the two end faces of the first joint element 50 and the main transmission ring 240 are circumferentially and strictly in-phase.

The foregoing description and drawings are given as illustrative of the present invention only with respect to a limited number of embodiments thereof, and it is to be understood that the embodiments are presented by way of illustration and that various changes, equivalents, permutations and alterations in structure or arrangement of parts may be made without departing from the spirit and scope of the inventive concept.

Claims

1. A separation holding mechanism of an axial self-control clutch is composed of a first engaging element, a second engaging element, a spring and a spring support based on the same axial lead; the second engaging element is axially movable and axially interposed between the first engaging element and the spring, the other end of the spring being supported by the spring support; under the action of the spring, the first jointing element and the second jointing element axially face each other to form a working jointing mechanism, when the first jointing element and the second jointing element rotate synchronously, the axial distance between the first jointing element and the second jointing element is minimum and is in a stable jointing state, and when the first jointing element and the second jointing element rotate asynchronously, the axial distance between the first jointing element and the second jointing element is maximum and is in a separated state; the method is characterized in that:

(a) The blocking and embedding mechanism is arranged for blocking the axial connection of the working connection mechanism in a separation state, is axially positioned in the working connection mechanism, is radially positioned in or out of the working connection mechanism, and is formed by axially embedding a blocking ring and an auxiliary blocking ring, the peripheral surfaces of the embedding end surfaces of the two rings are provided with the same number of radial blocking teeth with axial blocking effect, the blocking working surfaces of the blocking teeth are spiral surfaces with a rising angle of lambda, and lambda is less than or equal to max (0, delta), wherein delta is the minimum rising angle of the blocking working surfaces which can enable a static friction pair formed by the axial contact of the blocking working surfaces of the two rings to be successfully self-locked in the blocking working condition; the minimum blocking height of the blocking embedding mechanism is larger than the initial separation height of the working engagement mechanism in two rotation directions and smaller than the full-tooth engagement depth of the working engagement mechanism; the auxiliary blocking ring is rigidly integrated with an auxiliary ring, the auxiliary ring is a first joint element or a second joint element, the blocking ring is supported unidirectionally by a reference end face of the reference ring, and a sliding end face of the blocking ring and the reference end face form a circumferential free sliding friction pair; the reference ring is a second or first engagement element opposite the owner ring of the auxiliary blocker ring;

(b) 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 is rigidly integrated with the auxiliary main ring, and the auxiliary limiting ring is circumferentially fixed with the auxiliary stop ring; the circumferential freedom degree of the limiting embedding mechanism is larger than the entrance margin of the blocking embedding mechanism.

2. The separation retaining mechanism of claim 1, further comprising:

(a) The initial separation height of the working engagement mechanism in two opposite rotation directions is zero, and the rotation of the mechanism in the two opposite rotation directions can cause the mechanism to axially separate;

(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 of the blocking embedding mechanism is larger than the tooth crest blocking angle of the automatic control clutch.

3. The retaining mechanism of claim 1 or 2, wherein: the limit embedding mechanism is a pin-slot type limit mechanism which is arranged between two cylindrical surfaces of the auxiliary limit ring and the stop ring or between two end surfaces and consists of a bulge and a groove.

4. A separation holding mechanism according to claim 1 or 2, wherein: the stop ring in the fitting state can be relatively stopped on the reference end surface or the reference cylindrical surface of the reference ring by restraint.

5. A separation holding mechanism according to claim 1 or 2, wherein: the stop ring is regarded as an annular component consisting of two parts, namely an annular base body and end face radial teeth, wherein the end face radial teeth can be formed on two ends or inner and outer cylindrical surfaces of the annular base body.

6. A separation holding mechanism according to claim 1 or 2, wherein: the auxiliary blocking ring can be manufactured independently and then forms a rigid integrated combined component with the auxiliary main ring in the modes of welding, direct interference fit or axial pin hole interference fit and the like.