CN101118005A - Basic mode jaw self locking speed differential gear - Google Patents

Abstract

The present invention relates to a basic jaw type self-locking differential, which has the characteristics of no collision, high reliability, and long service life. The present invention is characterized in that a force transmission tooth and separating teeth and an accessory blocking tooth which are positioned on driven rings are connected as a whole; a self-limiting type blocking embedding mechanism is embedded by two embedding mechanisms of a force transmission embedding mechanism and a separation embedding mechanism under the differential condition, and axially positioned in the two mechanisms and radially positioned in the two mechanisms, between the two mechanisms or outside the two mechanisms, 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 changes and the abrasion is automatically compensated, and the slipping mode of no collision is unvaryingly maintained between the separating teeth in the operating condition, two processes of the self-separating block process and the embedding return process are absolutely reliable, and has no relation to the stability of the spring parameter compacted by the driven rings, hence the problem that the driven rings on the both sides are synchronously separated is not a problem any longer. The processing of the differential is obviously improved, the difficulty of the assembly is largely reduced, and the performance, the service life, and the interchangeability, etc. are remarkably improved.

Description

Basic tooth-embedded self-locking differential mechanism

Technical Field

The invention relates to a mechanical differential transmission device, in particular to a jaw self-locking differential used for a wheeled vehicle, and belongs to the field of mechanical transmission.

Technical Field

Since the invention in 1930 s, the jaw self-locking differential has been improved by people and has already good use performance, and becomes a main form of the self-locking differential. As shown in fig. 1, the main components are: the driving ring, the center ring, the driven ring, the stop ring, the spring seat, the spline hub and the snap ring. The center ring is embedded in the inner hole of the driving ring and is axially fixed by the clamping ring, the spring is installed between the driven ring and the spring seat, the spline hub and the inner hole of the driven ring are circumferentially fixed, and a characteristic curved surface for transmitting torque is formed on the spline hub. The two axial ends of the driving ring are respectively provided with four embedding mechanisms: the device comprises a power transmission embedding mechanism consisting of a driving ring and a driven ring, a separation embedding mechanism consisting of a center ring and a driven separation ring, a blocking embedding mechanism consisting of an opening blocking ring and an auxiliary blocking ring, and a limiting embedding mechanism consisting of a blocking ring and an auxiliary limiting ring. In the axial direction, the separating and embedding mechanism, the force transmission embedding mechanism and the blocking and embedding mechanism are fixed and synchronously separated or embedded; in the radial direction, the separation embedding mechanism is positioned in the force transmission embedding mechanism, the blocking embedding mechanism is positioned between the two embedding mechanisms, and the radial type limiting embedding mechanism is positioned between the blocking ring and the driving ring. The driven separating ring and the driven ring are made into a whole, the auxiliary blocking ring and the central ring are made into a whole, the auxiliary limiting ring with only one radial tooth is rigidly integrated with the driving ring, and the radial tooth and one driving ring transmission tooth are combined into a lengthened transmission tooth which is embedded in the circumferential groove of the blocking ring or between the opening sections 174. The opening blocking ring with the inner shaft shoulder is axially fixed in an annular groove on the embedded end face of the driven ring, and forms a circumferential sliding friction pair with the corresponding surface of the groove. In operation, the blocking ring actively enters or exits the blocking working state in a spiral motion mode. The driving force of its rotation is the friction force acting on its inner ring surface and sliding end surface, the resistance to its rotation is the friction force acting on its tooth crest surface, and the driving force of its axial movement is the friction force acting on its inner ring surface and the pressure on its shaft shoulder. In the service life of the differential, all the friction forces are changed to different degrees along with the increase of the abrasion, the increase of the smoothness of the friction surface, the change of the radial elastic force of the stop ring, the change of the working temperature and the change of the performance of the compression spring of the driven ring. Thus, there is a chance of failure both theoretically and in reality of the blocking engagement mechanism.

The working principle, structure and characteristics of the automobile axle design are described in detail in the book of automobile axle design (p 261-p 282) authored by mr. Liu Weixin published by the university of qinghua publisher, 4 months 2004. The structure of the stop ring is improved in 1990 by the American traction technology company, a novel jaw self-locking differential (engineering machinery, 11 th 1999, p 6-p 7) is developed, the tooth shapes and the tooth numbers of the stop teeth of the stop ring and the auxiliary stop ring are not equal to those of the separating teeth of a central ring or a driven ring any more, so that the resetting reliability of the stop ring is improved, and the processing difficulty of the stop ring and the driven ring is reduced.

However, the above-mentioned improvements do not change the circumferential limit mode of the blocker ring, and still follow the traditional radial pin-and-slot limit mode that the auxiliary blocker ring is only attached to the active ring, and the layout of the single blocker ring and the structural form of the single split ring are not changed at all, and many of the problems associated with the use performance and the manufacturing process related to the layout or structure are not improved or solved.

Disclosure of Invention

The invention aims to provide a basic jaw self-locking differential mechanism which is different from the existing barrier ring circumferential limiting mode and has multiple layout modes or structures for the barrier ring, and the basic jaw self-locking differential mechanism has the characteristics of more reasonable and simpler structure and assembly process, stronger wear resistance, more stability, excellent working performance and reliability, longer service life and lower manufacturing cost in different degrees. And broadly makes the jaw locking differential of the prior art a special case thereof.

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 referred to as a reference end face, and the cylindrical surface which directly faces the blocker ring in the radial direction is referred to as a reference cylindrical surface.

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

And (3) blocking working conditions: the blocking teeth of the blocking 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, a sliding friction pair is formed by a sliding end face or a cylindrical surface of the blocking ring and a reference end face or a reference cylindrical surface of the reference ring, on the other hand, a static friction pair is formed by a blocking working face of the blocking tooth and a blocking working face of the auxiliary blocking tooth in axial contact, 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 face 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 limiting surface is given to the circumferential relative position of the blocking ring. For the control embedded mechanism, when lambda is less than delta, the self-locking can not be realized due to the opposite vertex contact between the blocking teeth of the two sides, so that only the side surface of the blocking tooth and the side surface of the limiting bulge in the middle of the tooth top of the blocking tooth are limiting working surfaces; when delta is more than or equal to lambda is less than or equal to rho, all the side faces and the blocking working faces of the blocking teeth are limiting working faces because the abutting contact between the blocking teeth of the two sides can be reliably self-locked.

Full-tooth embedding depth: when the axial fitting 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.

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 a jaw differential, K must satisfy the following inequality: k > theta _c +θ _f + γ + η (when the end face teeth are circumferentially uniformly distributed), the relevant parameters are defined as follows:

θ _c : the central ring separates the circumferential included angle corresponding to the tooth top surface;

θ _f : the driven separating ring separates the circumferential included angle corresponding to the tooth top surface;

γ: the separating and embedding mechanism is transited from the embedding state to the critical state between the embedding state and the separating opposite vertex state, and the minimum circumferential angle of relative rotation is required between the two gear rings;

eta: the technological correction is the correction brought by the fact that a guide angle, a force transmission tooth root are contracted, a circumferential gap of the separation embedding mechanism and the full-tooth embedding depth of the force transmission mechanism and the separation embedding mechanism are not equal.

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 are called independent blocking rings for short.

The basic technical conception for achieving the aim of the invention is as follows: the circumferential relation between the blocking embedding mechanism and the limiting embedding mechanism is completely fixed in an integrated or circumferential fixing mode. The specific technical scheme is as follows:

a basic tooth-embedded self-locking differential comprises a driving ring, a central ring, a driven ring, a stop ring, a spring seat, a spline hub, a snap ring, an auxiliary stop ring and an auxiliary limiting ring, wherein the central ring is embedded in an inner hole of the driving ring and axially fixed by the snap ring; the axial both ends of initiative ring have all arranged: a force transmission embedding mechanism formed by embedding the driving ring and the driven ring in the axial direction; the separation embedding mechanism is formed by axially embedding the central ring and the driven separation ring, the axial direction and the radial direction are both positioned in the force transmission embedding mechanism, and the driven separation ring and the driven ring are formed into a whole; the blocking embedded mechanism is used for preventing the embedding of the separation embedded mechanism in the overrunning separation 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 formed on the two rings; the minimum blocking height of the blocking embedding mechanism is larger than the full-tooth embedding depth of the force transmission embedding mechanism and smaller than the full-tooth embedding depth of the separation embedding mechanism; the method is characterized in that: a limit embedding mechanism for limiting the circumferential relative position of the blocking ring in the blocking embedding mechanism is also arranged and consists of the blocking ring and an auxiliary limit ring; the auxiliary limiting ring and the auxiliary main ring are integrated into a whole, and the auxiliary limiting ring and the auxiliary blocking 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 X of the limiting embedding mechanism is larger than the entrance margin K of the blocking embedding mechanism, namely X is larger than K.

The blocking embedding mechanism is axially positioned in the separating embedding mechanism or the force transmission embedding mechanism, and is radially positioned in, between or outside the force transmission embedding mechanism and the separating embedding mechanism; the auxiliary stopper ring is integrated with an auxiliary ring which is a member constituting either the separable fitting means or the force-transmitting fitting means; the stop ring is supported by the reference end face of the reference ring in a one-way mode, and the sliding end face of the stop ring and the reference end face form a circumferential free sliding friction pair; the reference ring is the other member axially opposed to the master ring of the slave stopper ring in the separating/fitting mechanism or in the force-transmitting fitting mechanism.

As a radial spacing mode of circumferential fixation, a stop ring may be installed in a circular groove in the end face of a center ring, an auxiliary spacing ring is attached to a spline hub with the center ring as a reference ring, directly faces the inner bore face of the stop ring, and a pin-and-slot radial fitting mechanism is disposed between the two rings.

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 form 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 can be finally achieved, and meanwhile, the maximum limiting embedding depth of the limiting embedding mechanism must be ensured to be larger than the full-tooth embedding depth of the separating embedding mechanism.

More simply, the side of the limit bulge in the control embedding mechanism is preferably made into a spiral surface with the lead angle of beta, and the beta is more than or equal to | delta | and less than 180 degrees.

In addition, when the driven ring separating tooth is directly adjacent to the driven ring force transmission tooth, or the driven ring separating tooth is directly adjacent to the auxiliary blocking tooth which is connected with the driven ring force transmission tooth into a whole in the radial direction, the driven ring separating tooth and the directly adjacent tooth are connected into a whole in the radial direction with the effect that after a part of tooth bodies of the driven ring separating tooth are cut by taking the radial extension surface of the tooth sheave profile surface of the driven ring force transmission tooth as a boundary, the circumferential freedom degree of the separating and embedding mechanism is kept unchanged; similarly, the auxiliary catch tooth is connected with the radial type face tooth on the auxiliary main ring of the auxiliary catch ring or other radial type face teeth which are connected with the face tooth into a whole in the radial direction, and the radial extension face of the tooth socket profile face of the radial type face tooth on the auxiliary main ring is in the form of a partial tooth body for cutting off the auxiliary catch tooth, and is completely connected into a whole in the radial direction; the radial face teeth on the main ring are driving ring force transmission teeth, driven ring force transmission teeth or central ring separation teeth.

In order to achieve the effect, under the premise that the circumferential freedom degree of the separation and embedding mechanism is kept unchanged, the tooth thickness of the separation tooth of the driven ring can be reduced, and meanwhile, the tooth thickness of the separation tooth of the central ring can be correspondingly increased.

In order to make the blocking engagement means work perfectly and reliably, it is preferable to impose constraints on the blocking ring so as to force it to rest relatively on the corresponding reference surface of the reference ring in the engaged condition.

To provide more options for an optimal design, the facing radial teeth on the blocker ring may be formed on the inner or outer cylindrical surface of the blocker ring annular base.

In addition, in order to improve the performance and the reliability of the differential mechanism, a limit pin which is limited in the radial direction is installed in a center ring dismounting hole on the driving ring or the center ring, the head of the limit pin is embedded into a groove on a corresponding cylindrical surface on the center ring or the driving ring in the radial direction and is positioned in a gap of the clamping ring in the circumferential direction, a center ring limit mechanism which limits the circumferential relative position between the driving ring and the center ring is formed, and the circumferential freedom degree of the mechanism is not less than the circumferential freedom degree of the force transmission embedding mechanism.

For a simplified application, the driven ring and the splined hub can be made as a rigid one-piece body and form a characteristic curved surface on its inner or outer cylindrical surface, which can transmit torque.

In the invention, the auxiliary limit ring used as the core part of the limit embedding mechanism can be a spline hub, a driven ring or a central ring without being limited to one main ring, and simultaneously, the limit mode of the stop ring is not limited to one radial pin slot type, and can be an embedding type between stop teeth or a friction self-locking blocking type between tooth crests, and in addition, the circumferential fixing of the limit embedding mechanism and the stop embedding mechanism is realized. Moreover, the installation position of the stop ring is distributed to all six positions among the driving ring, the center ring and the driven ring, and the stop ring can be a complete ring without an opening, so that the aim of the invention is fulfilled. Namely, when the auxiliary limit ring and the auxiliary stop ring are formed into a whole, the limit bulge or the self-locking stop working surface at the middle part of the tooth crest is utilized, when the auxiliary limit ring and the auxiliary stop ring are only fixed in the circumferential direction, the limit working surface formed on the stop independently, namely the control embedding mechanism and the independent radial pin-slot type limit embedding mechanism are respectively utilized or are comprehensively utilized, the circumferential relative position in the stop embedding mechanism under the stop working condition is well maintained, and the purposes of maintaining the stop relation, preventing the embedding reset of the separation embedding mechanism in the overrunning state and eliminating the collision are well achieved; the purpose of limiting the circumferential relative position of the blocking ring in the blocking embedding mechanism in different modes and different layout modes under the blocking working condition is achieved. All schemes directly reduce the processing difficulty and the assembly difficulty of the whole differential mechanism and improve the reliability.

In addition, the technical proposal of the blocking working surface with friction self-locking function contained in claim 4 has better effect: firstly, block that gomphosis mechanism has ideal and block the performance, its separation blocks and gomphosis resets two simple and very reliable processes, and more importantly, relative motion between the both sides separation tooth of centre ring and driven separation ring can reach zero contact's pure sliding state in the very first time, has eliminated the collision formula wearing and tearing phenomenon between the separation tooth, has reduced their wearing and tearing speed and has prolonged the life of differential mechanism remarkably. And secondly, the blocking embedding mechanism has the capability of self-adapting to the axial separation distance and the capability of automatically compensating various axial abrasion within a certain range, and in the blocking working condition, the tooth tops of the separation teeth can keep a zero-collision sliding mode for a long time, so that the high-frequency micro-compression phenomenon of the axial compression spring of the driven ring is eliminated, the working stability and reliability of the whole system are enhanced, and the differential mechanism can keep the optimal working state for a long time. Thirdly, the two processes of separating blocking and embedding resetting of the blocking embedding mechanism are not related to the stability of the performance of the axial pressing spring of the driven ring, and the driven ring does not have any sensitivity, so that the requirements on the performance of the pressing spring are not strict, the faults of the differential mechanism related to the pressing spring are greatly reduced, and the requirements on the assembly process and the related cost are further reduced. And fourthly, the assembly, the maintenance and the assembly of the differential become relatively simple, the assembly is similar to the assembly, the quality is ensured, and all parts, if qualified, have no compatibility or matching problem no matter whether new or old, and have no influence on the assembly quality and the service performance. Fifthly, the blocking ring can be made into a non-split ring form, the manufacturing process and the assembly process are both simplified, and the assembly requirement, the precision requirement and the production cost are relatively reduced. Sixthly, even if two driven rings of the differential mechanism are in an abnormal state of separation and blocking, any phenomenon of repeated separation and embedding can not occur. Seventhly, the differential has very simple, fast and reliable active capability of handling the abnormal situation that the double-sided driven rings are simultaneously in the separation blocking state, especially for the solution of claim 10 arranged with a center ring limit mechanism; correspondingly, the separating teeth of the central ring and the driven separating ring can be completely manufactured into common low-cost trapezoidal teeth, the width of the tooth grooves of the force transmission teeth can be reduced, the torque transmission capacity of the differential is improved, and meanwhile, the central ring limiting mechanism also has the advantages of simple structure, easiness in processing and manufacturing and low cost.

In contrast, in the embodiments of claims 1 to 4, in which the working surface is not provided with a friction self-locking function, the relative movement between the tops of the separating teeth of the central ring and the driven separating ring may still have a slight impact. Nevertheless, the blocking and engaging mechanism of the corresponding embodiment still has the advantages of simple and reliable separation of the blocking process and the engaging and returning process, and fully has the full benefits of manufacturing the blocking ring into a complete ring. In addition, a limiting embedding mechanism is arranged between the spline hub and the inner hole cylindrical surface of the stop ring, and the manufacturing process and the assembling process of the limiting embedding mechanism are superior to those of the prior art.

In addition, the integral tooth structure of claim 6 of the present invention has the advantages of optimizing the structure and mechanical properties of the driven ring, making the structure more reasonable, significantly improving the processing manufacturability of the driven ring, reducing the processing difficulty and production cost, and significantly improving the product quality and production efficiency. The integral tooth structure has the most obvious benefit on the layout mode that the blocking embedded mechanism is not positioned between the force transmission embedded mechanism and the separating embedded mechanism, in the radial direction, the force transmission tooth and the separating tooth or the auxiliary blocking tooth are connected into a whole, and the tooth sides of the force transmission tooth and the separating tooth or the auxiliary blocking tooth can be processed and formed at one time; at the same time, the bending resistance of the disengaging teeth is not reduced, but rather improved due to the cooperative nature of the tooth body connection, and allows the tooth thickness thereof to be reduced so that the circumferential clearance of the disengaging and engaging mechanism remains unchanged, and yet has sufficient tooth flank area to enhance the wear resistance thereof. Because the connected force transmission teeth greatly enhance the bending resistance of the driven ring separation teeth, and the two teeth cannot bear the action of bending moment simultaneously. Furthermore, the increased separating ring radius further reduces the separating forces acting on it and the torque on the separating tooth root.

In the embedding working condition, the stop ring is relatively kept still on the reference end surface or the reference cylindrical surface of the reference ring through the restraint of claim 8, so that the accuracy and the reliability of the two processes of separating, blocking and embedding resetting of the blocking embedding mechanism are obviously improved. Especially, for the technical scheme that the limit embedding mechanism adopts a friction self-locking limit mode, and the auxiliary blocking ring and the driven ring are integrated, because the blocking ring does not need circumferential acceleration or axial movement in the two processes, the performance of the blocking embedding mechanism is nearly ideal or perfect: the action qualification of the mass inertia of the blocking ring in the two processes of blocking the separation and blocking and embedding resetting of the embedding mechanism is completely cancelled, the blocking ring does not need to do any action in the two processes, all necessary actions are completed by the driven ring which is the driving part leading to the separation and blocking and embedding resetting actions, and therefore the factors of synchronism, consistency, performance stability of the driven ring compression spring and responsiveness caused by inertia and a mechanical structure are removed from the two processes in a congenital mode, potential structural hazards are eliminated, and reliability and stability of the differential are remarkably improved.

In addition, after the radial teeth on the end face of the stop ring can be formed on the inner or outer cylindrical surface of the annular base body of the stop ring, the axial and radial sizes of the stop ring can be changed in a larger range, and more choices are certainly provided for the optimal design of a blocking embedding mechanism and even the whole differential mechanism.

Drawings

FIG. 1 is an axial cross-sectional view of a prior art dog-type self-locking differential.

Fig. 2 is an axial cross-section of a first embodiment of the invention.

Fig. 3 is a schematic view of the driven ring of fig. 2, (a) is an axial sectional view in a right side view, (b) is a front view, and (c) is an expanded schematic view of a partial tooth profile radial projection in the T direction in (b) in an enlarged manner.

Fig. 4 is a schematic view of the blocker ring of fig. 2, (a) is an enlarged expanded view of the partial radial projection of the T-direction partial tooth profile of (c), (b) is an axial sectional view of the right side view of (c), and (c) is a front view.

Fig. 5 is a partially developed view of radial projections of the relative relationship between the sets of tooth profiles on the same outer cylindrical surface when the left half of the differential mechanism in fig. 2 is in the engaging force transmission state and the right half is in the separating blocking state, (a) is a schematic view of the tooth profile relationship of the corresponding engaging mechanism, and (b) is a schematic view of the tooth profile relationship of the corresponding force transmission engaging mechanism, and (c) is a schematic view of the tooth profile relationship of the corresponding separating engaging mechanism, and (d) is a schematic view of the parameters of the force transmission teeth in the engaging state, and (e) is a schematic view of the parameters of the separating teeth in the engaging state.

FIG. 6 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 suitable for the radial type position-restricting fitting mechanism is shown.

Fig. 7 is a simplified schematic diagram of one of the constraining forms of the blocker ring of fig. 2.

Fig. 8 is a simplified schematic diagram of a second form of restraint of the blocker ring of fig. 2.

Fig. 9 is a simplified schematic illustration of a third form of restraint of the blocker ring of fig. 2.

FIG. 10 is a simplified representation of a fourth of the constrained forms of the blocker ring of FIG. 2, with (a) being a structural representation of the toothed end of the retaining ring of (b) and (b) being an axial cross-section.

Fig. 11 is a simplified schematic diagram of five of the constraining forms of the blocker ring of fig. 2.

Fig. 12 is an axial cross-sectional view of a second embodiment of the invention.

Fig. 13 is a schematic view of the driven ring of fig. 12, where (a) is a front view and (b) is a cross-sectional view taken along a T-T section of (a).

Fig. 14 is a schematic view of an alternative form of containment of the blocker ring of fig. 12.

Fig. 15 is an axial cross-sectional view of a third embodiment of the invention.

Fig. 16 is a schematic view of the center ring of fig. 15, (a) is a front view, (b) is an axial sectional view of a left side view, and (c) is an enlarged expanded schematic view of a radial projection of the partial tooth profile in the T-direction in (a).

Fig. 17 is an axial cross-sectional view of a fourth embodiment of the invention.

Fig. 18 is a schematic view of the center ring in fig. 17, wherein (a) is a front view, and (b) is a half-sectional view of a left side view.

Fig. 19 is a cross-sectional view of a fifth embodiment of the present invention.

FIG. 20 is a schematic view of the axial substrate barrier ring of FIG. 19, with (a) being a front view and (b) being a cross-sectional view from the left.

Fig. 21 is an axial cross-sectional schematic view of an application example of a simplified structure of the present invention.

FIG. 22 is a diagrammatic view in axial cross-section of an example of the use of the present invention in a tractor differential.

Detailed Description

The essential description is as follows: in the text of this description and in all the figures, identical or similar components and features thereof are provided with the same reference signs and are only described in detail when they first appear, and no repeated detailed description will be given when they appear again thereafter.

Fig. 2 to 5 show a first embodiment of the present invention, i.e., a preferred embodiment of the present invention. The central ring 150 is embedded in the inner hole of the driving ring 110 and is axially fixed by the snap ring 56, the two driven rings 120 are installed at the two ends of the driving ring 110, and the four embedded end surfaces of the four rings are opposite to each other pairwise to form two force transmission embedding mechanisms and two separation embedding mechanisms. The two springs 54 press the driven ring 120 from both ends, respectively, to ensure the continuation of the fitting pressure, and the outer ends of the two springs 54 are supported by the two spring seats 50. And the two spring seats 50 are axially retained by the outer shoulders of the two splined hubs 60 that are nested within their bores. The two splined hubs 60 are each fixed circumferentially in splined engagement with the inner bores of the two driven rings 120, and the inner bores of the splined hubs 60 have splined teeth machined therein for transmitting torque to the output half shafts (not shown). The two stopper rings 170 are fitted into the circular recesses in the end face of the center ring 110 so that the fitting end faces face the driven ring 120, and the inner wall of the recess is used as a reference end face and the center ring 110 is used as a reference ring. Two restraining springs 192 are installed between the blocker ring 170 and the inner end surfaces of the external spline teeth of the spline hub 60, respectively, to press the blocker ring 170 against the reference end surfaces. A center ring removal hole 160 is radially machined in the four radial lugs of the drive ring 110, and a center ring stop pin 162 is mounted in one of the holes with its pin head fitting into a corresponding groove 164 in the outer cylindrical surface of the center ring 150 and into the axial gap of the snap ring 56, see fig. 5 (c). The whole differential mechanism has completely symmetrical layout and structure in the axial direction, the transmission teeth and the separation teeth on all the components have completely the same quantity and are circumferentially and uniformly distributed, and meanwhile, the end face teeth at the two ends of the driving ring 110 and the central ring 150 are circumferentially and tightly matched.

As shown in fig. 3, in the three annular regions on the fitting end surface of the driven ring 120, the driven ring force transmission teeth 122 with an inverted trapezoidal cross section, the driven ring separation teeth 142 with a trapezoidal cross section, and the auxiliary blocking teeth 202 are uniformly distributed from outside to inside in sequence. In the radial direction, the three teeth are connected into a whole, the radial relationship between the three is shown in fig. 3 (a) and fig. 3 (b), and the tooth surface relationship between the three is shown in fig. 3 (c). The driven ring force transmission tooth top surface 124 and the driven ring separation tooth top surface 144 are easy to be formed accurately in one step; for simple structure and easy processing, the driven ring transmits the force tooth root surface 128, the driven ring separates the tooth root surface 148, the accessory barrier tooth root surface 210 three coplane; after cutting away part of the tooth flanks of the driven ring separator tooth 142 and the auxiliary blocking tooth 202, bounded by the radially extending surface of the driven ring force transmission tooth flank 126, the driven ring separator tooth flank 146 remains partially, the auxiliary blocking tooth is divided into two parts, each of which has a blocking face 204, whose tooth flank 206 no longer exists, and whose tooth flank 208 is coplanar with the driven ring force transmission tooth flank 126. Here, the blocking working faces 204 of all the subsidiary blocking teeth 202 are helicoids with a lead angle λ, | δ | < λ ≦ ρ. Correspondingly, the drive ring force transmission teeth 112 are identically toothed to the driven ring force transmission teeth 122, and the central ring separator teeth 152 are crowned trapezoidal, see fig. 5 (d) and 5 (e).

Compared with the prior art, the driven ring 120 is simpler in structure and more reasonable in mechanics, the manufacturability is obviously improved, the processing difficulty and the cost are reduced, the tooth thickness of the driven ring separating tooth 142 is reduced, the tooth side working area is properly increased, and the contact strength is reduced. The engagement of the thickened center ring separator teeth 152 with the thinned driven ring separator teeth 142 is illustrated in fig. 5 (e).

The structure of the blocker ring 170 is shown in fig. 4. The ring has a radial-type base. The three stop teeth 172 are uniformly formed on the outer ring side of the annular base 188 in the circumferential direction, a limit protrusion 182 is formed in the middle of the tooth top, and the tooth surface of the limit protrusion 182 is composed of the top surface 184 of the limit protrusion 182, a spiral surface type limit side surface 186 with a lead angle of beta, a spiral surface type stop working surface 176 with a lead angle of lambda, and a tooth side surface 178, wherein | δ | is | ≦ β ≦ 180 °. The bottom end face of the blocker ring 170 is its circumferential sliding end face 190 and the top end face is its fitting end face. The annular base 188 has the function of bearing the pressure of the restraining spring 192.

The blocker ring 170 without the requirement for radial elasticity would be easier to manufacture and assemble than the prior art. In addition, to facilitate manufacturing and reduce the axial dimension, the limiting protrusion 182 at the middle of the tooth top of the blocking tooth can be hidden. That is, the lead angle β of the convex flank 186 is made equal to the lead angle λ of the stop face 176 and is identical in complete succession to the corresponding stop face 176. See fig. 6 (e).

As shown in fig. 2, 5 (c) and 5 (d), the center ring stopper pin 162 and the stopper groove 164 formed on the outer circumferential surface of the center ring 150 constitute a center ring stopper mechanism having a circumferential degree of freedom θ _p . In the fitted state, the degree of freedom in the circumferential direction is theta _p Not less than circumferential degree of freedom theta of force-transmitting embedded mechanism _t I.e. theta _p ≥θ _t . And the two fitting mechanisms are simultaneously at the intermediate values of the respective circumferential degrees of freedom. The tail thread of the limit pin 162 is matched with the center ring dismounting hole 160, so that the function of convenient dismounting is achieved. Compared with the prior art, the mechanism has simpler structure and easier manufacture and assembly, and borrowsThe center ring removing hole 160 further reduces the manufacturing cost. The assembling process is also simple, namely, a small process pin is embedded into a radial through hole at the center of the central ring limiting groove 164, then the notch of the snap ring 56 is circumferentially aligned with the small process pin and sleeved into the snap ring groove on the outer circular surface of the central ring 150, the small process pin and the snap ring are completely pressed into the snap ring groove, then the central ring 150 with the circumferentially positioned snap ring 56 is arranged into the central hole of the driving ring 110, and the snap ring is pushed into the central ring 150The clamping ring groove can automatically open. The center ring 150 is adjusted circumferentially to align the gap of the snap ring 56 with a center ring removal hole 160 on one of the drive rings, and then a center ring stop pin 162 is assembled into the center ring removal hole 160 and into the gap of the snap ring 56, and finally the process is finished by withdrawing the small pin.

All the fitting relationships in the differential are shown in fig. 5. The driving ring 110 and the driven ring 120 respectively form a force transmission embedding mechanism, and the full-tooth embedding depth and the circumferential freedom degree of the mechanism are respectively D _t And theta _t ， θ _t Is sufficient to ensure that the two end driven rings 120 are capable of achieving differential speed separation simultaneously in different directions. The central ring 150 and the driven separating ring form a separating and embedding mechanism, and the depth of the full-tooth embedding of the mechanism is D _c . The blocking ring 170 and the auxiliary blocking ring form a control embedding mechanism which is not only a blocking embedding mechanism but also a limiting embedding mechanism, and the entrance margin K of the mechanism is

(the correlation symbol represents the circumferential angle between the corresponding points), and K > θ _c +θ _f + γ + η, where A and D, B and C, E and J, G and H are sets of axial isocenters or lines, respectively. In the state where the differential is fitted to the differential,

wherein the content of the first and second substances,

representing the minimum blocking height of the control engagement means (the horizontal line symbols indicate the axial distance)The separation is the same as the following steps,

representing the maximum limit embedding depth of the limit embedding mechanism. The axial separation distance of the control jogging mechanism is larger than the minimum blocking height

In the process, the limit working face of the limit embedding mechanism is converted into the friction self-locking stop working faces 176 and 204 from the stop tooth flanks 178 and 208, so that the circumferential freedom degree X of the limit embedding mechanism at the moment is naturally larger than K. See fig. 3 (c), 4 (a) and 5 (a). The right half of fig. 5 (a) - (c) shows the relationship of the fitting mechanism in the blocking condition. All possible abutting contact conditions of the blocking engagement with various tooth profiles in the blocking mode can be seen in fig. 6.

It will be appreciated that the provision of three uniformly distributed, diametrically identical radial teeth on each of the blocker ring 170 and the satellite blocker ring, and the arrangement of the satellite blocker teeth 202 circumferentially exactly spanning the two driven ring separator teeth 142, is not necessary, purely for reasons of simplicity of construction and manufacture, etc. In the case where the secondary stopper ring cannot be formed integrally with the primary ring, the secondary stopper ring can be handled by a method of manufacturing the secondary stopper ring separately in advance and then rigidly combining the secondary stopper ring with the primary ring by welding or interference fit. In addition, the final axial support of the spring 54 or spring seat 50 may be provided by the differential housing, by a housing in the case or bearing between the housing and the rotating shaft, or by other axially fixed components (e.g., snap rings). It must be noted, however, that although the spring retainer 50 may be eliminated in form, the spring 54 cannot have a fulcrum, but rather is acted upon by a substitute member such as a shoulder on the outer circumferential surface of the splined hub 60, and therefore remains a substantial equivalent to the spring retainer 50.

This embodiment is further described with reference to fig. 2 and 5 in conjunction with the working process.

The present embodiment is used in a state of being incorporated into a differential case assembly of the known art. Under the condition of no differential rotation inside the differential mechanism, or simply corresponding to the straight-line running of the vehicle, the differential mechanism is in a completely embedded state. At this time, the torque of the input differential is transmitted from the driving ring 110 to the driven rings 120 through the force-transmitting engaging mechanisms at both ends, and then transmitted from the spline hubs 60 at both ends to the output half shafts at both ends through the two spline engaging pairs, and finally transmitted to the driving wheels at both ends. Under the condition that the differential rotation exists in the differential mechanism, or simply corresponds to the condition that the vehicle runs in a steering mode, the differential mechanism is in an overrunning separation state. For the sake of symmetry, only the case where the right driven ring 120 rotates over the driving ring 110 corresponding to the left-hand steering of the vehicle will be described here. The result of the overrunning rotation is only one of the first or second cases that the right driven ring is separated or the left driven ring is separated but the power of the other end is not interrupted, and the third case that the left and right driven rings are separated into free rings at the same time. The first case will be described first.

In the assumption that the left-end driven ring is not separated, that is, all the fitting mechanisms at the left end are completely fitted, the rotation of the right-end driven ring 120 relative to the driving ring 110 is equivalent to the rotation relative to the center ring 150. This continued rotation inevitably results in the axial separating force generated between the contact surfaces of the right driven ring separating teeth 142 and the center ring separating teeth 152 being greater than the engaging pressure of the spring 54, and the two separating teeth slide and climb against the engaging pressure until the axial separating distance of the driven ring 120 from the center ring 150 reaches Dc, so that the right separating engaging mechanism and the force-transmitting engaging mechanism are completely separated. Due to the parameters

Thus, the lowest point a of the secondary blocking tooth stop face 204 in the control engagement mechanism already axially passes the lowest point G of the blocking tooth stop face 176. Since the stopper ring 170 is held by the spring 192 and is stopped by the center ring 150, the above-mentioned state of being separated is exceeded as long as the entrance margin K of the stopper fitting mechanism is not far from the lower limit value thereofThe process is sufficient to ensure that D is achieved in the first synchronization of the axial separation distance of the control engagement means _c Then, the auxiliary blocking tooth blocking working face 204 has reliably jumped over the blocking tooth blocking working face 176, and the auxiliary blocking tooth blocking working faces collide with each other and establish a stable self-locking static friction relationship, thereby driving the blocking ring 170 to circumferentially slide on the reference end face of the center ring 150 and reach D for the first or second time at the axial separation distance _c The axial separation process of the separation and engagement mechanism is stopped at the maximum separation distance D in the time (extreme design condition) _c The above. Therefore, the axial distance between the right driven ring 120 and the center ring 150 is constant at zero, and the two rings are in a zero-contact sliding friction condition without any impact or collision, so that the collision-type abrasion phenomenon of the separation teeth and the high-frequency micro-compression phenomenon of the spring 54 in the prior art are eliminated, the abrasion speed of the two is remarkably reduced, the stability and the reliability of the differential are enhanced, and the service life of the differential is prolonged.

For the second result that the right driven ring overruns and rotates to cause the left driven ring to separate, the mechanism of the process is completely the same, namely the process is equal to the separation process that the left driven ring overruns and rotates reversely relative to the driving ring; in the case of simultaneous forward overrunning separation and reverse overrunning separation of the left and right driven rings, the separation mechanism is the same as the first two separation conditions because the central ring 150 is substantially stationary relative to the driving ring 100 during the separation process, and thus the description of the separation process in the latter two conditions is completely identical to the description in the first condition and does not need to be repeated.

It should be emphasized that the helicoidal surface characteristic of the blocking face in the controlled engagement mechanism of the present embodiment is a prerequisite for ensuring zero collision of the force-transmitting teeth in the blocking condition, i.e., λ > 0 is required. The lambda less than or equal to the lambda is a necessary condition for blocking friction self-locking between working surfaces in a working condition, and also a necessary condition for blocking the embedding mechanism to have the capability of self-adapting to the axial separation distance and the capability of automatically compensating various axial abrasion in a certain range, improving the overall performance, reliability and service life of the differential, and can compensateThe amount of (A) can also be given as desired at the time of manufacture. Particularly, when delta is more than 0 and 0 < lambda < delta, the auxiliary blocking tooth 202 can slide and climb relatively because the two blocking working faces which are contacted with each other in opposite directions can not self-lock, so that the blocking is enabledThe axial separation distance of the engaging means is greater than D _c Until the stop projection 182 is encountered. That is, with proper design, one can achieve an overrunning rotational condition that allows no contact between the driven ring 120 and the center ring 150. In addition, the self-locking relationship between the blocking working faces only exists in the corresponding overrun rotation, that is, the relative rotation in which the lift angle of the blocking working face in the opposite contact is made positive, but never exists in the relative rotation in which the lift angle is made negative, because the lift angle λ ' = - λ < - δ |, λ ' in the latter rotation completely falls outside the lower limit of the self-locking requirement λ ' ≧ δ. Thus, by changing the relative rotation direction between the two separating teeth in the blocking condition, the original self-locking relationship between the blocking working faces will disappear immediately, and the blocking ring 170 will no longer rotate integrally with the secondary blocking teeth 202, but will rest on the reference end face of the reference ring, i.e. on the inner wall of the circular recess of the end face of the central ring 150.

Therefore, the fitting reset of the embodiment is very simple, and the reverse overtaking is enough, which corresponds to the process of returning the vehicle from the left-steering running to the straight running. That is, as soon as the overrun rotation speed of the right driven ring 120 starts to become smaller than zero, the respective engagement mechanisms at that end are engaged and reset immediately. Or, whatever the extreme case, as long as K > theta _c +θ _f The + γ + η parameter ensures that, without K being far from its lower limit, at most one tooth position has to be rotated in the reverse overrun direction, i.e. the driven ring 120 is rotated in the reverse direction relative to the driving ring 110 by at most one tooth position, and the auxiliary blocking teeth 202 can slide off the blocking tooth blocking face 176, and are synchronously engaged and reset together with the driven ring disengaging teeth 142 and the driven ring force transmission teeth 122, see fig. 5. The driven ring force transfer teeth 122 have circumferentially staggered the drive ring force transfer tooth notch only until the lowest point a of the secondary blocking tooth barrier face 204 has not yet slid off the lowest point G of the blocking tooth barrier face 176In this case, the engagement reset process needs to be performed by one tooth, but the reverse separation blocking does not occur.

In the second separation case, as long as the reverse overrunning of the left driven ring 120 begins to change into the forward overrunning, the engaging mechanisms at the end are engaged and reset immediately, the process is the same, and the description is not repeated. In the third situation of simultaneous separation and blocking of the left end and the right end, the method for recovering the embedding reset is also very simple and fast, and only one of the two conditions needs to be accelerated or decelerated. The guiding idea is that the abnormal separated overrunning state is changed, and the existing friction self-locking relation in the blocking embedding mechanism is destroyed, so that the relative overrunning direction of one driven ring at one end is necessarily changed as long as the rotating speed of the central ring 150 is not between the rotating speeds of the left driven ring and the right driven ring, and the embedding transmission force at the end is immediately recovered. The process description is exactly the same and is not repeated. It should be noted that the center ring position limiting mechanism between the active ring 110 and the center ring 150 is the best choice for implementing the above described relief method, but is not required. This can be done without the free wheel differential of the mechanism, but with a slight reduction in processing speed. The guiding idea of relieving difficulty is completely the same as the above, and the specific method is that the vehicle in running turns right once.

The above-described guiding concept of overcoming difficulty can also be applied to overcoming the abnormal situation in which other double-end fitting mechanisms are simultaneously separated, for example, the abnormal situation in which the double-end blocking fitting mechanism separates the blocking in the same direction with respect to the center ring 150. But only slightly different in the order of priority of the particular method, but equally at most two attempts. That is, regardless of whether the vehicle speed is zero or not and regardless of the type of abnormal separation, if the original traveling direction is known, only one acceleration or one steering is required, and if not, the acceleration and deceleration or the left and right steering is required at most. It can be seen that with the present invention, the anomaly of the simultaneous disengagement of the two-sided driven rings in the prior art is no longer a problem, even if it is not perceived as ever occurring while the vehicle is in motion. Therefore, the performance of the differential and the steering performance of the vehicle in the curve can be obviously improved. And because the friction between the blocking working surfaces is self-locked, even if the embedding resetting is not forced, the impact phenomenon of repeated embedding and separating of the separating embedding mechanism in the prior art can not occur.

In fact, from the standpoint of maneuverability, an abnormal separation of the driven ring that occurs when coasting on a curve should be desirable. Since, after disengagement, the present embodiment allows the differential to operate immediately with only one acceleration event, there is no power interruption, and a drive mode is achieved that is also advantageous for steering and control of the vehicle, i.e. the outside of the curve, rather than the inside wheels, receive drive torque. And after entering the straight path, the working condition of bilateral driving can be automatically recovered. Therefore, the separating teeth 152 are not necessarily drum-shaped, and all the separating teeth of the separating and fitting mechanism should be formed as common trapezoidal teeth. This simplifies the process and reduces the cost, and also increases the torque transfer capability of the differential by reducing the width of the power transmission tooth spaces.

Obviously, the blocking embedding mechanism in the differential mechanism has two processes of separating blocking and embedding resetting, the mechanism is simple, the process is reliable, the effect is ideal, and the overall performance and the service life of the differential mechanism are obviously improved.

In addition, for the minimum lead angle δ and the maximum lead angle ρ for controlling the self-locking of the friction pair of the working face in the fitting mechanism, the present specification has given clear definitions, and therefore the functional relation can be easily derived by the definitions, and the functional relation is only related to the basic geometric dimension, the axial pressure, the circumferential friction and the related friction coefficient (for the taper hole-shaped sliding end face as shown in fig. 19, the equivalent friction coefficient). The spring 54, restraining spring 192 and circumferential restraining friction have little or no effect on δ and ρ, and the coefficient of friction has little effect on the size of the self-locking region between δ and ρ. The relative position of λ within the self-locking interval bounded by δ and ρ changes little throughout the life cycle of the differential (assuming a coefficient of friction of 0.1 and no binding force, the interval is about 11 degrees in size). Therefore, as long as the rising angle lambda of the blocking working surface in the blocking embedding mechanism is set in the middle of the interval, the blocking embedding mechanism can be ensured to have friction self-locking capability for a long time in the whole life cycle of the differential mechanism, and can work reliably and effectively. Therefore, compared to the prior art, the reliability of the stopper fitting mechanism is not related to the performance stability of the spring 54, and the failure related thereto is necessarily reduced greatly. Not only can the harsh requirement on the differential mechanism be cancelled, the requirement and the difficulty of the differential mechanism assembly process are reduced, but also the assembly, the maintenance and the assembly of the differential mechanism become relatively simple, the assembly is similar to the assembly, the quality is ensured, and all parts, if qualified, no matter whether new or old, have no problem of compatibility or matching performance, and no problem of influencing the assembly quality and the use performance exists.

Fig. 6 shows all possible abutting contact conditions of the blocking engagement with various tooth profiles in the blocking operating mode. In FIGS. 6 (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. 6 (d) shows a case where β ≠ λ; fig. 6 (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 176, which is advantageous for manufacturing. Fig. 6 (a), 6 (b) and 6 (j) correspond to various tooth relationships with impact wear after overload separation.

It should be noted that the stop ring 170 is stopped on the reference end face by constraint in this embodiment only for the purpose of obtaining desired performance and reliability, and is not necessarily required. The restraining mode is not limited to the spring compression, and the whole or part of the center ring 150 or the blocking ring 170 can be made of magnetic materials to cause the magnetic attraction of the two; the blocking ring 170 can also be made into an elastic open ring with a positioning shaft shoulder or an elastic open ring with a conical revolution surface, and the axial component of the elastic counter force of the conical revolution surface forces the blocking ring to be tightly attached to the reference end surface in a self-restraining mode; the blocking ring can also be in a radial pressing mode that radial elastic force acts on a local conical revolution surface of the blocking ring to force the blocking ring to be close to a reference end surface, such as a spring ball or an elastic snap ring; alternatively, the system shown in fig. 7 to 11 may be used.

As shown in fig. 7, the outer circular surface of the V-groove snap ring 80 is provided with a circumferential groove with a V-shaped section, two side surfaces of the groove are matched with corresponding tapered end surfaces of the blocking rings, and the radial expansion force of the snap ring 80 forces the blocking rings 170 at two ends to be always attached to the reference end surface 78 in the center ring 150.

Fig. 8 shows the two-end blocker ring 170 tensioned directly against the reference end face 78 of the center ring 150 by the positioning spring 92. A washer 86, a washer 90 and balls 88 are spaced between the retainer spring 92 and the inner shoulder end faces of the two blocker rings 170 to prevent circumferential movement of the two blocker rings. Four radial projections 104 are uniformly distributed on the inner side of the washer 90. Four annular axial bulges 106 bent by the outermost circle of spring steel wire are uniformly distributed at the corresponding end of the positioning tension spring 92, and the other end of the positioning tension spring is made into a bell mouth shape. The final step of assembly is to rotate the four radial projections 104 of the washer 90 from the beginning of the spring wire at the projecting end of the positioning tension spring 92 to between the two outermost turns of the spring and into the through holes surrounded by the respective corresponding axial projections 106. Variations are possible that eliminate the washer 86 and ball 88 at that end; alternatively, the tension spring 92 could be made symmetrical with both ends provided with the projections 106 and the washer 90 would replace the washer 86.

As shown in FIG. 9, retaining ring 94 has an outer shoulder disposed on one end and an inner shoulder disposed on the other end, all or a portion of the inner end surface of the inner shoulder being a tapered bore surface. The balls 88 are disposed between the outer shoulders of the retaining ring 94 and the inner shoulders of the blocker ring 170, respectively. After the two symmetrical positioning rings 94 press the blocking rings 170 from both ends, the distance between them is still larger than zero. The sides of the "V" shaped circumferential groove on the outer circumferential surface of the snap ring 80 engage the corresponding tapered surfaces of the retaining rings 94 and force the retaining rings 94 to pull the blocking rings 170 against the reference end surface 78 of the center ring 150 by the radial expansion force of the snap ring 80.

This embodiment can also be configured as follows: the ball 88 at one end is replaced by a wave spring, and the V-shaped groove of the snap ring 80 is changed into a rectangular groove; or the positioning tension spring 92 replaces the clamping ring 80, and a plurality of radial convex teeth replace the inner shaft shoulder of the positioning ring 94; or directly make the positioning ring 94 and the blocking ring 170 into a rigid integral body; or the balls 88 and retaining ring 94 may be eliminated and the axial dimension of the snap ring 80 increased to the form shown in fig. 7.

As shown in fig. 10, an outer shoulder 100 is disposed at one end of a positioning ring 108, four axial convex teeth are uniformly disposed at the other end, radial convex teeth 96 are formed on inner ring sides of top ends of the four convex teeth, two positioning rings 108 press against corresponding stop rings 170 from left and right ends respectively in a staggered embedding manner, a group of balls 88 are disposed between the outer shoulder 100 of the left positioning ring 108 and the inner shoulder of the stop ring 170, a wave-shaped restraining spring 192 is mounted between the outer shoulder 100 of the right positioning ring 108 and the inner shoulder of the stop ring 170, and a locking snap ring 102 is mounted between the two staggered embedding radial convex teeth 96 to axially restrain the two positioning rings 108 to ensure compression of the restraining spring 192, thereby ensuring that the two stop rings 170 are tightly attached to the reference end face 78.

Of course, it is also possible to eliminate the restraining spring 192 or replace it with the balls 88 and to suitably deepen the axial splines 98 of the retaining ring 108, while replacing the locking snap ring 102 with a helical compression spring, the axial force of which presses the blocking rings 170 at both ends. The helical compression spring is brought into position in the manner of rotation described above.

The construction shown in fig. 11 is also typical of a jaw differential, and the main difference is that the form of action of the spring 54 is changed, substantially without difference from the layout shown in fig. 2, and will not be described repeatedly. In this manner, the blocker ring 170 is positioned in exactly the same manner as shown in FIG. 2, except that the inner ring shoulder of the blocker ring 170 extends radially a great deal and the axial bearing surface of the restraining spring 192 is replaced by the end surface of the outer spline of the splined hub 60 as the end surface of the annular base of the splined hub 60.

It should be noted that the restraining spring 192 of the present invention is not limited to the coil spring and the wave spring, and the diaphragm spring, the disc spring, the elastic rubber, the elastic plastic, etc. are all equivalent; also the support ring of the restraining spring 192 may be a splined hub, a driven ring, a center ring, a driving ring, and a blocker ring itself. After the stop ring 170 is restrained, the accuracy, reliability and time effectiveness of the two processes of separating stop and tabling reset of the blocking tabling mechanism are reliably guaranteed, and the performance of the blocking tabling mechanism is nearly ideal or perfect. In the two processes of the separation blocking and the embedding resetting of the blocking embedding mechanism, the blocking ring 170 does not need to do any action, all necessary actions are completed by the driven ring 120 which is a motive power element leading to the separation blocking and the embedding resetting actions, so that the factors of synchronism, consistency, performance stability of the spring 54 and responsiveness caused by inertia and mechanical structures in the prior art are inherently excluded from the two processes, the structural hidden danger is eliminated, and the reliability and the stability of the differential are obviously improved.

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.

A second embodiment is shown in fig. 12 to 13. The fitting control means of the first embodiment is radially moved from the inside of the fitting control means to the inside of the fitting force transmission means. This embodiment thus has almost all of the features of the first embodiment. The specific difference is that the spring 54 is composed of a plurality of circumferential members, and the stop ring 170 is an elastic split ring with an axial base body, and the rotational friction surface between the ring and the center ring 150 is in the shape of a conical hole with a conical top at one end of the stop ring sliding end surface 190.

The construction of the driven ring 120 is shown in fig. 13. The auxiliary blocking ring is radially positioned between the driven ring force transmission gear ring and the driven ring separation gear ring, the physical connection between part of the driven ring force transmission teeth 122 and the driven ring separation teeth 142 is directly cut, and the potential for reducing the tooth width of the driven ring separation teeth 142 is obviously smaller than that of the first embodiment.

As in the first embodiment, the blocker ring 170 may also be a pure cylindrical complete ring and need not be given a positive axial positioning at the expense of not being able to guarantee that a zero-crash blocking mode is established at the first time. Alternatively, axial positioning of the blocker ring 170 may be achieved by making the rotational friction surface between the blocker ring 170 and the center ring 150 in the form of a cylindrical surface with shoulders for positioning. Alternatively, as shown in fig. 14, the blocker ring 170 is formed as a complete ring whose axial position is limited by at least one axial positioning pin 82. The positioning pin 82 is axially arranged in a through hole on the tooth root surface 210 of the auxiliary blocking tooth from the axial direction, one end of the positioning pin 82 is propped against the tooth crest 184 of the limiting bulge at the middle part of the tooth crest of the independent blocking tooth, referring to fig. 4, the small diameter of the end head at the other end is sleeved with a positioning pin pressure spring 84 with the outer diameter not larger than that of the positioning pin 82, and the positioning pin pressure spring 84 is pressed on the spring seat 50. The drive pin 82 is stationary with respect to the blocker ring 170 as the follower ring 120 moves axially, and the amount of circumferential rotation of the follower ring 120 is insufficient to cause the tip of the drive pin 82 to disengage from the raised tooth top surface 184 at the mid-tip limit of the blocker tooth. To reduce friction, a bore may be drilled in the head of the dowel 82 to embed the ball.

Fig. 15 to 16 show a third embodiment of the present invention. The position of the blocking/fitting mechanism in the first embodiment is changed in the axial direction. That is, the blocker ring 170 uses the driven ring 120 as its reference ring, the inner ring side end face of the driven ring separating teeth 142 as its reference end face, the sub blocker ring uses the center ring 150 as its sub ring, and the sub blocker teeth 202 are integrally connected to the center ring separating teeth 152 at the inner diameter end, see fig. 16. Also, a restraining spring 192 is mounted directly between the two blocker rings 170 with a spacer 62 disposed between the two splined hubs 60. This embodiment has almost all the characteristics of the first embodiment.

The compression of the restraining spring 192 ensures that the blocker ring 170 synchronously follows the axial movement of the driven ring 120 as the driven ring 120 moves axially apart. The separate blocking and fitting resetting process of the blocking and fitting mechanism is understood in an overriding manner in which the center ring 150 is rotated relative to the driven ring 120, and is completely the same as that described in the first embodiment, and thus, a repetitive description thereof will not be made. It is apparent that the blocker ring 170 is accelerated in rotation and moved axially during the blocking of the blocking engagement mechanism in this embodiment, but is inert and stationary in the first embodiment, and thus, the present embodiment is clearly subject to inertia and synchronization problems. To ensure the synchronization of the movements, the stiffness of the restraining spring 192 should be significantly increased, and therefore, the wear will be relatively increased. Therefore, this embodiment is slightly inferior to the first embodiment.

It should be noted that to reduce wear and interference, a washer and a set of balls may be used to space the blocker ring 170 from the restraining spring 192. Alternatively, the restraining spring 192 may be eliminated and the blocker ring 170 may be formed as a resilient split ring with a tapered or locating shoulder on its outer circumference. In addition, as shown in fig. 16 (c), the tooth flank 210 of the satellite blocker tooth 202 is lower than the center ring split tooth flank 158, with its tooth flank coplanar with the center ring split tooth flank 156 and its tooth crest 206 coplanar with the center ring split tooth crest 154, wherein the considerations of simplified construction are the same as in fig. 3 and are not repeated here. More freely, the satellite blocker tooth blocker face 204 may be higher or lower than the crest 154 of the center ring separator tooth 202 and may even be lower than the root face 158 of the center ring separator tooth 202, see FIG. 18.

A fourth embodiment of the present invention is shown in fig. 17 to 18. The position of the blocking and fitting mechanism in the second embodiment is axially interchanged to obtain the solution. That is, the elastic split blocker ring 170 with a positioning shoulder or conical surface of revolution is fitted into the annular groove between the driven ring force-transmitting teeth 122 and the driven ring disengaging teeth 142 with the driven ring 120 as its reference ring, and the auxiliary blocker ring with the center ring 150 as its owner ring with the inner wall of the groove as its reference end face, and the auxiliary blocker teeth 202 are integrally connected to the center ring disengaging teeth 152 at their outer diameter ends. The secondary blocker tooth tip land 206 is at the same height as the central ring split tooth root land 158, which facilitates machining, and the secondary blocker tooth flank 208 may be angled from the secondary blocker tooth root land 210 with a transition circle. Therefore, the present embodiment has almost all the characteristics of the second embodiment.

As in the third embodiment, the blocking ring 170 is also axially movable in this embodiment, and is not as reliable and simple as the solution with the central ring 150 as a reference ring. It will be readily appreciated that the ability of this embodiment to reduce the width of the driven ring separator teeth 142 is less than that of the first and third embodiments, and that the mechanical properties and manufacturing process are relatively poor, and although not a good choice, are superior to the prior art solutions in the other respects described.

Fig. 19 to 20 show the only embodiment of the present invention having the radial type position restricting fitting mechanism. The key difference compared to the embodiment shown in fig. 1 is that the secondary blocker ring and secondary retainer ring are fixed circumferentially rather than rigidly integral, one attached to the driven ring 120 and one attached to the splined hub 60, and that the lead angle of all blocking faces is zero degrees. In addition, three radial protrusions 129 are formed on the inner ring surface of the blocking ring 170, and a radial limit fitting mechanism is formed by the limit groove 222 formed at a corresponding position of the spline hub 60. The circumferential degree of freedom X of the mechanism is larger than the entrance margin K of the blocking embedding mechanism, and the two embedding mechanisms can be synchronously embedded in the middle in the circumferential direction. After the blocking engagement mechanism enters the blocking condition, the spline hub 60 drives the blocking ring 170 to rotate integrally through the radial protrusions 194, and the blocking condition of the blocking engagement mechanism is maintained. In addition, the sliding end surface 190 of the blocking ring 170 is a conical hole surface which has an included angle with the rotation axis which is not equal to 90 degrees, so that the 6-value improvement, the constraint capability of the blocking ring 170 and the reliability of the blocking and embedding mechanism are facilitated.

Obviously, it is also possible to arrange the limit recesses 222 of the radial-type limit fitting mechanism to the inner annular surface of the blocker ring 170 and to arrange the radial projections 129 to the spline hub 60. In both arrangements, the manufacturing process and assembly process are superior to the prior art. In addition, if the blocking engagement mechanism in this embodiment is raised radially between the separating engagement mechanism and the force-transmitting engagement mechanism, and accordingly, only one auxiliary limiting ring with radial teeth is rigidly integrated with the driving ring 110, the circumferentially fixed relationship between the two auxiliary rings becomes a circumferentially limited relationship, which is a special case in the broad sense of the present invention.

Referring to fig. 20, the lead angles of all the barrier working faces in the barrier fitting mechanism are zero. Therefore, the subject parameterThe separation engagement means and the blocking engagement means cannot be simultaneously brought into abutting contact, i.e. the friction between the tips of the separation teeth in the blocking condition is of the collision type, see fig. 6 (j). The interference fit mechanism also has no ability to compensate for wear. In addition, this embodiment has almost all of the features of the first embodiment, including the fitting reliability due to the non-self-locking property at the fitting reset time. Since the blocking ring 170 is at least temporarily out of contact with the secondary blocking tooth 202 when the disengaging teeth collide with each other, the restrained spring 192 rests on the reference end face of the central ring 150, which is equivalent to the blocking engagement mechanism being unable to self-lock.

Of course, the lift angle of the blocking working surface of the blocking and fitting mechanism in this embodiment may be set within the friction angle interval, that is, | δ | < λ ≦ ρ, so that the zero-collision sliding friction working mode between the separated teeth can be realized, but this is the first but not the present embodiment. This is possible even if only the stopper projection 182 is added, because it is impossible to simultaneously function both stopper fitting mechanisms.

In the application example of the simplified structure shown in fig. 21, the gear teeth 58 are directly formed on the outer cylindrical surface of the driving ring 110, the driven rings 120 on both sides are respectively formed integrally with the spline hub 60, and the spline inner hole is a blind sealing hole, the seal ring 66 is disposed between the differential case and the spline hub 60, and the blocker ring 170 is a tapered elastic split ring. In addition, a center ring removal hole 160 is provided on the center ring 150.

The simplest structure can transmit large torque, and is very suitable for differential systems of various automatic propelling machines and light-duty vehicles, such as snow plows, grass trimmers, concrete cutters, asphalt cutters, golf carts, hand tractors, various miniature agricultural implements and the like.

Fig. 22 shows an example of application of yet another simplified construction of the present invention, namely a tractor differential application. In contrast to fig. 21, fig. 22 illustrates the transmission teeth 130 on the splined hub 60 changed from inner to outer cylindrical surfaces, while the two half-shafts, which are not torque-transmitting and rotating, are combined to form a steering through-shaft 68, which is only radially oriented, on which all components of the drive ring 110, etc., float axially.

The embodiment is suitable for a steering system of a walking tractor, particularly suitable for the use occasions of a steering wheel with a guide wheel or a guide function, can reduce the labor intensity of a driver, and improves the safety and the operation performance of a vehicle.

With the idea of the invention in mind, it is easy to conceive of a design in which the blocking engagement is arranged radially outside the force-transmitting engagement, but that is not a good option, not only is the residual torque too high, but it is also not very well assembled. The spring 54 may be any other compression spring such as a diaphragm spring.

The foregoing is a description and illustration of the invention, given for the purpose of illustration only, with a certain degree of particularity, it is understood that the embodiments referred to have been made by way of illustration, and that various changes, equivalents, permutations and alterations in structure or arrangement of parts thereof may be resorted to without departing from the spirit and scope of the inventive concept.

Claims (10)

1. A basic jaw self-locking differential comprises a driving ring, a central ring, a driven ring, a stop ring, a spring seat, a spline hub, a snap ring, an auxiliary stop ring and an auxiliary limiting ring, wherein the central ring is embedded in an inner hole of the driving ring and is axially fixed by the snap ring; the axial both ends of initiative ring have all arranged:

the power transmission embedding mechanism capable of transmitting torque in two directions in relative rotation is formed by axially embedding a driving ring and a driven ring, and the embedding end faces of the two rings are all provided with:

a radial force transfer tooth;

the separation embedding mechanism can be rotated relatively in two directions to separate the separation embedding mechanism, is axially and radially positioned in the force transmission embedding mechanism and is formed by axially embedding a central ring and a driven separation ring, and radial separation teeth are arranged on the embedding end surfaces of the two rings; the driven separating ring and the driven ring are formed into a whole; and

the blocking embedding mechanism is used for preventing the embedding of the separation embedding mechanism in the overrunning separation state and is formed by axially embedding the blocking ring and the auxiliary blocking ring, and radial blocking teeth with axial blocking effect are formed on the two rings; the minimum blocking height of the blocking embedding mechanism is larger than the full-tooth embedding depth of the force transmission embedding mechanism and smaller than the full-tooth embedding depth of the separation embedding mechanism; the method is characterized in that:

the limiting embedding mechanism is also arranged for limiting the circumferential relative position of a blocking ring in the blocking embedding mechanism and consists of the blocking ring and the 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 blocking ring are circumferentially fixed; when the axial separation distance of the blocking and embedding mechanism is larger than the minimum blocking height, the circumferential freedom degree of the limiting and embedding mechanism is larger than the entrance margin of the blocking and embedding mechanism.

2. The self-locking differential according to claim 1, wherein: the blocking embedding mechanism is axially positioned in the separating embedding mechanism or the force transmission embedding mechanism, and is radially positioned in, between or outside the force transmission embedding mechanism and the separating embedding mechanism; the auxiliary blocking ring is integrated with an auxiliary ring which is one of the components forming the separation embedding mechanism or the force transmission 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 member axially opposed to the auxiliary ring of the auxiliary stopper ring in the separating/fitting mechanism or in the force-transmitting fitting mechanism.

3. The self-locking differential according to claim 1, wherein:

(a) The stop ring is arranged in a circular groove in the end face of the central ring, the auxiliary main ring of the auxiliary stop ring is a driven ring, the auxiliary main ring of the auxiliary limiting ring is a spline hub, and the direct contact face of the auxiliary limiting ring is opposite to the inner cylindrical surface of the stop ring;

(b) The limit embedding mechanism is a pin-slot type radial embedding mechanism arranged between the auxiliary limit ring and the inner cylindrical surface of the stop ring.

4. The self-locking differential according to claim 1, 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, two blocking working faces are correspondingly formed on two sides of each tooth crest face of the blocking tooth and the auxiliary blocking tooth respectively, the two blocking working faces are spiral faces with a lead angle not larger than rho, a limiting bulge is formed in the middle of at least one tooth crest face, and rho is the maximum lead angle of the blocking working face, which can enable a static friction pair formed by axial contact of the blocking working faces of the two blocking working faces to be successfully self-locked in a blocking working condition;

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

5. The self-locking differential according to claim 4, wherein: two side surfaces of the limiting bulge in the control embedding mechanism are spiral surfaces with a lead angle of beta, beta is more than or equal to | delta | and less than 180 degrees, wherein | delta | is the absolute value of the minimum lead angle of a blocking working surface which can enable a static friction pair formed by the axial contact of the blocking working surface of the blocking tooth and the blocking working surface of the auxiliary blocking tooth to be successfully self-locked in the blocking working condition.

6. The self-locking differential according to any one of claims 1 to 5, wherein:

(a) When the driven ring separating tooth is directly adjacent to the driven ring force transmission tooth or an auxiliary blocking tooth which is connected with the driven ring force transmission tooth into a whole in the radial direction, the driven ring separating tooth and the directly adjacent tooth are connected into a whole in the radial direction with the effect that the circumferential freedom degree of the separating and embedding mechanism is kept unchanged after a part of tooth bodies of the driven ring separating tooth are cut off by taking the radial extension surface of the driven ring force transmission tooth grooved wheel profile surface as a boundary;

(b) The auxiliary blocking teeth and radial end face teeth on an auxiliary main ring of the auxiliary blocking ring or other radial end face teeth which are connected with the end face teeth into a whole in the radial direction are connected into a whole in the radial direction by taking the radial extension surface of the tooth sheave profile surface of the radial end face teeth on the auxiliary main ring as a form of cutting off part of tooth bodies of the auxiliary blocking teeth; the radial end face teeth on the owner ring are driving ring force transmission teeth, driven ring force transmission teeth or center ring separation teeth.

7. The self-locking differential according to claim 6, wherein: on the premise of keeping the circumferential freedom degree of the separation embedding mechanism unchanged, the tooth thickness of the separation tooth of the driven ring can be reduced, and the tooth thickness of the separation tooth of the central ring can be correspondingly and equally increased.

8. The self-locking differential according to any one of claims 1 to 5, 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.

9. The self-locking differential according to any one of claims 1 to 5, wherein: the barrier ring is considered to be an annular member consisting of two parts, an annular base body and end face radial teeth formed on the inner or outer cylindrical surface of the annular base body.

10. The self-locking differential according to any one of claims 1 to 5, wherein: and a limiting pin which is limited in the radial direction is arranged in a central ring dismounting hole on the driving ring or the central ring, the head part of the limiting pin is embedded into a groove on the corresponding cylindrical surface on the central ring or the driving ring in the radial direction and is positioned in the gap of the clamping ring in the circumferential direction, so that a central ring limiting mechanism which limits the circumferential relative position between the driving ring and the central ring is formed, and the circumferential freedom degree of the mechanism is not less than that of the force transmission embedding mechanism.

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