CN101117987A - Stitching type jaw single and bidirectional over running clutch - Google Patents

Abstract

The present invention discloses a press-fitting type jaw overrunning clutch, which can be used as a single or double direction overrunning clutch or a single and double direction controllable glider, and has the characteristics of huge transmissible torque, high rotating speed, no collision, small volume, large impact resistance, simplicity and reliability, and long service life. The present invention is characterized in that the press-fitting type jaw overrunning clutch is provided with a blocking embedding mechanism preventing two embedding mechanisms of a force transmission embedding mechanism and a separation embedding mechanism from being embedded under the overrunning separating condition, the mechanism on the axial direction is positioned in the two mechanisms, and the mechanism on the radial direction is 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 is changed and the abrasion is automatically compensated; no collision characteristic of the overrunning operating condition of the two embedding mechanisms is maintained for a long time, and the separating block process and the embedding return process of the embedding mechanism are absolutely reliable. In addition, the direction control mechanism and the condition control mechanism are simple and reliable, the clutch manufacture is relatively easy, the assembly is simple, and the interchangeability of an old part and a new part is strong.

Description

Press-fit type jaw single-direction and two-direction overrunning clutch

Technical Field

The invention relates to a clutch device in the field of mechanical transmission, in particular to a jaw clutch with a rotary overrunning function.

Technical Field

The existing overrunning clutch is developed by a pawl-ratchet mechanism and has two types of an embedded type and a friction type. In three application fields of indexing, overrunning and non-return, the friction type is most suitable for the indexing field due to accurate positioning, and the embedded type is most suitable for two fields of overrunning and non-return which have relatively low requirements on slip angles but relatively high requirements on torque transmission capacity. However, due to the fact that the clutch is engaged, particularly, the dog type overrunning clutch is hardly used in practice because of collision and collision noise when the clutch is rotated in an overrunning manner, so that the advantages of large torque transmission, no slip after engagement, and the like are not exerted. The Chinese patents with the application numbers of 02102352.2, 99248119.8 and 99239680.8 disclose two technical schemes of a jaw overrunning clutch, but the three patents still have the problems of insufficient collision or transmission torque due to the fact that collision or torque still does not correspond to most or all of pressure on a transmission tooth surface and a half-tooth impact phenomenon is necessary.

Disclosure of Invention

The invention aims to provide a press-fit type jaw one-way overrunning clutch which can transmit large torque and has no collision and sound after overrunning separation, and a press-fit type jaw overrunning clutch with controllable direction and state.

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.

Blocking the 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 blocking ring in the axial direction is called a reference end face, and the cylindrical face which directly faces the blocking ring in the radial direction is called a reference cylindrical face.

Separating the reference ring: a rotating member as a reference object in which a separating ring is relatively stationary and circumferentially fixed in an overrunning clutch; the end face thereof which directly faces the separating ring in the axial direction is referred to as a reference end face.

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

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

δ angle and ρ angle: in the blocking working condition, on one hand, the sliding end surface or the cylindrical surface of the blocking ring is in contact with the reference end surface or the reference cylindrical surface of the blocking reference ring to form a sliding friction pair, on the other hand, the blocking working surface of the blocking tooth of the blocking ring is in axial contact with the blocking working surface of the auxiliary blocking tooth to form a static friction pair, and when the circumferential position of the blocking ring relative to the auxiliary blocking ring is limited only by the static friction pair, the static friction pair needs to be self-locked, wherein the minimum lift angle of the blocking working surface capable of ensuring self-locking of the static friction pair is defined as delta, and the maximum lift angle is defined as rho.

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

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

Minimum barrier height: 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 guaranteed 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.

Separation angle: the axial engagement mechanism is transited from the engagement state to the critical state between the engagement state and the separation opposite vertex state, and the minimum circumferential angle of relative rotation is required between the two gear rings.

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

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

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

The invention relates to a press-fit type jaw one-way overrunning clutch which comprises a first joint element, a second joint element, a stop ring, an auxiliary limiting ring, a spring and a spring seat, wherein the first joint element, the second joint element, the stop ring, the auxiliary limiting ring, the spring and the spring seat are all arranged on the basis of the same rotating axis; the first jointing element and the second jointing element are axially oppositely embedded to form a working embedding mechanism which is a force transmission embedding mechanism and a separation embedding mechanism; the method is characterized in that: 1) The blocking embedded mechanism is used for preventing the embedding of the working 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 arranged on the two rings; the minimum blocking height of the blocking embedding mechanism is larger than the initial separation height of the working embedding mechanism in two rotation directions and smaller than the full-tooth embedding depth of the working embedding mechanism; 2) The limiting embedding mechanism is arranged for limiting the circumferential relative position of the blocking ring in the blocking embedding mechanism and consists of the blocking ring and an auxiliary limiting ring, the auxiliary limiting ring and the auxiliary main ring are integrated, 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 of the limiting embedding mechanism is larger than the entrance margin of the blocking embedding mechanism.

The blocking embedding mechanism is axially positioned in the working embedding mechanism and radially positioned in or out of the working embedding mechanism, the auxiliary blocking ring is integrated with the auxiliary ring, the auxiliary ring is any one part of joint elements forming the working embedding mechanism, the blocking ring is supported in one direction by a blocking reference end face of the blocking reference ring, and a sliding end face of the blocking reference ring and the blocking reference end face form a circumferential free sliding friction pair; the blocking reference ring is a side engagement element axially opposed to the auxiliary ring of the auxiliary blocking ring.

As a simpler stop ring limiting scheme, the auxiliary stop ring and the auxiliary stop ring can be formed into the same ring, the limiting embedding mechanism and the blocking embedding mechanism are recombined into a control embedding mechanism, in the control embedding mechanism, the stop teeth are also limiting teeth at the same time, and the auxiliary stop teeth are also auxiliary limiting teeth at the same time; and the stopping working faces of the tooth tops of the stopping tooth and the auxiliary stopping tooth are spiral faces with the rising angle lambda not larger than rho, a limiting bulge is formed in the middle of at least one tooth top, and the maximum limiting embedding depth of the limiting embedding mechanism is larger than the full-tooth embedding depth of the working embedding mechanism.

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

The invention relates to a controllable press fit typeThe jaw overrunning clutch comprises a first joint element, a second joint element, a separating ring, an auxiliary separating ring, a blocking ring, an auxiliary limiting ring, a spring and a spring seat, and the first joint element, the second joint element, the separating ring, the auxiliary separating ring, the blocking ring, the auxiliary limiting ring, the spring and the spring seat are all arranged on the basis of the same rotating axis; the first joint element and the second joint element are axially oppositely embedded to form a force transmission embedding mechanism capable of transmitting torque in two directions; the method is characterized in that: 1) A separation embedding mechanism which can lead the two parts to separate when the two parts rotate relatively is arranged, the separation embedding mechanism is formed by axially embedding a separation ring and an auxiliary separation ring, and a circle of radial separation teeth are arranged on the two rings; 2) The blocking embedded mechanism which is composed of a blocking ring and an auxiliary blocking ring in the axial direction and prevents the separation embedded mechanism from being embedded in the overrunning separation state is arranged, and radial blocking teeth with the axial blocking function are arranged on the two rings; the minimum blocking height of the blocking embedding mechanism is greater than the full-tooth embedding depth of the force transmission embedding mechanism, greater than the initial separation height of the separation embedding mechanism in two relative rotation directions and less than the full-tooth embedding depth of the separation embedding mechanism; 3) The limiting embedded mechanism is arranged for limiting the circumferential relative position of a blocking ring in the blocking embedded mechanism and consists of the blocking ring and an auxiliary limiting ring, the auxiliary limiting ring and the auxiliary 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 of the limiting embedding mechanism is larger than the entrance margin of the blocking embedding mechanism; 4) Circumferential degree of freedom theta of force transmission embedding mechanism _t It is determined in such a manner that, i.e.,when the separating and embedding mechanism transcends the separation in two working rotating directions, the two components of the force transmission embedding mechanism do not contact or collide with each other; 5) The separating ring positioning and locking mechanism capable of fixing the separating ring on a specific circumferential position relative to the separating reference ring is arranged, and the overrunning clutch has the separating and overrunning functions only after the separating ring is locked in the circumferential direction.

The separating and embedding mechanism is axially positioned in the force transmission embedding mechanism and radially positioned in or out of the force transmission embedding mechanism; the auxiliary separating ring is integrated with an owner ring which is any one joint element forming a force transmission embedding mechanism; the release ring is supported unidirectionally by a release reference end face of a release reference ring, which is a side engagement element opposed to the auxiliary ring of the auxiliary release ring.

In addition, 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 the owner ring, and the owner ring is one of the components forming a separating embedding mechanism or a force transmission embedding mechanism; the blocking ring is supported in a one-way mode by a blocking reference end face of the blocking reference ring, and a sliding end face of the blocking ring and the blocking reference end face form a circumferential free sliding friction pair; the blocking reference ring is a member facing the auxiliary ring of the auxiliary blocking ring.

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

When the fixed joint element is a reference ring and a different-shaft joint element, the pushing ring is used as a main ring of the auxiliary stop ring and is circumferentially fixed with the steel ball hub, the auxiliary stop ring is attached to the steel ball hub and directly faces the inner cylindrical surface or the end surface of the stop ring, and a radial or axial embedding mechanism is formed between the auxiliary stop ring and the corresponding surface of the stop ring, so that a radial stop scheme of the stop ring can be obtained.

For a one-way overrunning clutch or a controllable press-fit type jaw overrunning clutch, the most direct radial stop ring limiting scheme can be adopted: under the condition that the second rotating shaft and the second joint element are circumferentially fixed, the second joint element is used as a main auxiliary ring of the auxiliary stop ring, the second rotating shaft is used as a main auxiliary ring of the auxiliary limiting ring, the auxiliary limiting ring directly faces the inner cylindrical surface or the end surface of the stop ring, and an upper radial or axial embedding mechanism is arranged between the corresponding surfaces of the auxiliary limiting ring and the stop ring.

As a simpler stop ring limiting scheme, the auxiliary stop ring and the auxiliary stop ring can be formed into the same ring, the limiting embedding mechanism and the blocking embedding mechanism are recombined into a control embedding mechanism, in the control embedding mechanism, the stop teeth are also limiting teeth, and the auxiliary stop teeth are also auxiliary limiting teeth; and the stopping working surfaces of the tooth tops of the stopping tooth and the auxiliary stopping tooth are helical surfaces with the lead angle lambda not larger than rho, a limiting bulge is formed in the middle of at least one tooth top, and the maximum limiting embedding depth of the limiting embedding mechanism is larger than the full-tooth embedding depth of the separating embedding mechanism.

To obtain a bidirectional overrunning clutch, the first engagement element may be axially fixed; the second joint element is used as a common main ring of the auxiliary stop ring and the auxiliary limit ring, the stop ring is arranged in the inner hole of the separating ring,the separating ring is arranged in the inner hole of the first jointing element; two sides of the top surfaces of the radial teeth of the two sides for controlling the embedding of the embedding mechanism are respectively and correspondingly provided with a blocking working surface, the side surface of the limiting bulge, which is on the same side with the blocking working surface, is provided with a spiral surface with a lead angle beta, wherein delta is less than or equal to beta and less than 180 degrees, and the initial separation height of the separation embedding mechanism in two rotation directions is designed to be zero; correspondingly, the entrance margin K of the blocking and fitting mechanism conforms to the inequality: k > theta _c +θ _f + γ + η; meanwhile, the separating ring positioning and locking mechanism is made into an axial pin hole type positioning mechanism which can respectively fix the separating ring at two different specific circumferential positions relative to the first joint element, when the separating ring is fixed at the first relative position, the overrunning clutch can only transmit torque and separating overrunning in the first direction, when the separating ring is fixed at the second relative position, the overrunning clutch can only transmit torque and separating overrunning in the second direction, and in addition, a positioning and operating mechanism for operating the mechanism is also installed; in the above inequality, γ = max (γ) ₁ ，γ ₂ ) The relevant parameters are defined as follows:

θ _c : the separation ring separates the circumferential included angle corresponding to the tooth top surface,

θ _f : the auxiliary separating ring separates the circumferential included angle corresponding to the tooth top surface,

γ ₁ : a separation angle of the separation and engagement mechanism in the first direction,

γ ₂ : a separation angle of the separation and embedding mechanism in the second direction,

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.

Furthermore, to obtain a compulsory bidirectional overrunning clutch or a bidirectional slider, an embedding type limiting mechanism which can forcibly limit the blocking ring at a specific circumferential position relative to the separating ring, namely a blocking ring rotation stopping mechanism is arranged, the blocking ring can lose axial blocking capability only when limited at the specific position, and the overrunning clutch can be axially embedded and reset; accordingly, the circumferential limit position of the release ring relative to the first engagement element is limited by a release ring stop mechanism, which is arranged between the release ring and the first engagement element, and whose circumferential degree of freedom, which is not less than the circumferential angle between the first relative position and the second relative position and which is not so great that the release ring starts to have the ability to completely prevent the clutch from axially engaging, is sufficient for the release ring positioning and locking mechanism to perform its function in the rotational range corresponding to this circumferential degree of freedom; and, the lift angle β must satisfy the inequality: beta is more than or equal to | delta | and less than 90-phi, wherein phi is a friction angle of a friction pair formed by the two sides forming the control embedding mechanism in friction contact on the side surface of the limiting bulge; in addition, the separating ring positioning and locking mechanism is an axial pin hole type positioning mechanism, and the axial positions of two groups of locking pins and the stop ring rotation stopping mechanism are controlled by the positioning control mechanism.

In addition, to obtain a controllable pairA runner for unidirectional force transmission and overrunning, which can axially fix the first jointing element; the second jointing element is used as a common main ring of the auxiliary stop ring and the auxiliary limit ring, the stop ring is arranged in the inner hole of the separating ring, and the separating ring is arranged in the inner hole of the first jointing element; the initial separation height of the separation and engagement mechanism in at least one rotation direction is zero; the side surface of the limit bulge in the control embedding mechanism, which is on the same side with the barrier working surface, is a spiral surface with a lead angle beta, wherein beta is more than or equal to delta and less than 90-phi; in addition, the overrunning clutch state control mechanism is specially arranged and is formed by combining a separating ring positioning and locking mechanism, a separating ring limiting mechanism and a stop ring rotation stopping mechanism, and the separating ring, the stop ring and the stop ring can be connectedThe mechanism limits the circumferential position among the first joint element, the overrunning function of the overrunning clutch can be canceled at any time without condition by the mechanism, so that the overrunning clutch can enter the working condition of the jaw coupling immediately; here, the separating ring positioning locking mechanism is a pin-hole type circumferential positioning mechanism consisting of corresponding axial pin holes and pins distributed on the separating ring and the first joint element; a release ring limiting mechanism for limiting the circumferential limit position of the release ring relative to the first engagement element, arranged between the release ring and the first engagement element, the circumferential degree of freedom of which is not so small as to affect the force-transmitting engagement mechanism to realize the circumferential degree of freedom theta thereof _t The degree of the clutch is not so large that the separating ring starts to have the capability of completely preventing the clutch from being embedded in the axial direction, and the separating ring positioning and locking mechanism can fully realize the function in a rotating interval corresponding to the circumferential freedom degree; the stop ring rotation mechanism can limit the stop ring on a specific circumferential position relative to the separating ring in a forced mode, at the moment, the stop ring loses axial stopping capacity, and the overrunning clutch can be embedded and reset in the axial direction.

For further options, the condition control mechanism may further comprise a positioning operation mechanism for operating the separating ring positioning locking mechanism and the blocking ring rotation stopping mechanism.

All the stop ring rotation stopping mechanisms are pin groove type axial embedding mechanisms consisting of axial grooves or section gaps on the sliding end surfaces of the stop rings, axial through holes on the stop reference end surfaces of the separating rings and rotation stopping pins; all the separating ring limiting mechanisms are pin-hole limiting mechanisms consisting of axial pin holes in toothless end surfaces of the separating rings, axial through holes in separating reference end surfaces of the first joint elements and limiting pins embedded into the two holes simultaneously; all the positioning control mechanisms achieve the aim of giving and controlling the axial positions of a locking pin of the separating ring positioning locking mechanism and a rotation stopping pin of the stop ring rotation stopping mechanism in a purely mechanical mode.

In addition, the separating ring positioning and locking mechanism can also be a cylindrical cam type radial pin slot positioning mechanism, the mechanism is also a separating ring limiting mechanism, the radial pin slot positioning mechanism comprises a group of linked axial locking pins with the number of not less than one, the group of locking pins are respectively embedded in corresponding axial pin holes on the toothless end surfaces of the first joint element or the separating ring and mutually form a circumferentially fixed axial sliding relationship, guide bulges are respectively formed at one end of the head parts or one end of the tail parts of the group of locking pins in a radial mode and are matched with a spiral guide slot formed on a corresponding cylindrical surface of the separating ring or the first joint element to form the radial pin slot positioning mechanism, and the locking pins move along the axial direction of the axial pin holes and can relatively slide along the axial direction of the spiral guide slot through the guide bulges so as to directly change the circumferential position and the state of the separating ring relative to the first joint element.

For perfect and reliable operation of the blocking engagement mechanism, it is preferable to impose a constraint on the blocking ring to force it to rest relatively on the reference end face or reference cylindrical face of the blocking reference ring in the engaged state.

Optimally, in order to ensure the matching precision and facilitate the lubrication, the overrunning clutch can be uniformly packaged into a shell, the shell consists of a shaft sleeve, a bowl-shaped shell and an end cover, and the torque transmission or overrunning between the rotating shaft or the shaft sleeve and the shell is realized by the circumferential fixing mode that the shaft sleeve is circumferentially fixed or directly integrated with the inner hole surface of the first joint element and the circumferential fixing mode that the outer cylindrical surface of the combined shell and the outer cylindrical surface of the second joint element are formed in a spline connection mode, wherein the shell also has the function of a spring seat.

In the invention, the torque transmission link does not have any unmatched place, and the force transmission embedding mechanism can be a sawtooth-shaped or rectangular-section end face tooth for transmitting large torque. After the blocking embedding mechanism, the limiting embedding mechanism, the separating ring positioning and locking mechanism, the separating ring limiting mechanism, the blocking ring rotation stopping mechanism and the positioning control mechanism are added in time, the aims provided by the invention are well realized. When the auxiliary limit ring and the auxiliary stop ring are integrated, the limit bulge or the self-locking stop working surface at the middle part of the tooth top is utilized, and 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 comprehensively utilized, so that the circumferential relative position inside the stop embedding mechanism under the stop working condition is well maintained, the purposes of maintaining the stop relationship, preventing the embedding reset of the separation embedding mechanism in the overrunning state and eliminating the separation impact or collision are well achieved; the control mechanism of state type is used for controlling the respective circumferential relative positions of the separating ring and the blocking ring, so that the purposes of controlling the existence and nonexistence of the overrunning capacity and the blocking capacity and the directions of torque transmission and separating overrunning are well achieved.

Compared with the existing jaw overrunning clutch, the jaw overrunning clutch has the advantages that the rotating speed is higher, the transmitted torque is larger, no noise exists in the overrunning state, and the working direction and the working state are simply controlled; compared with a friction type overrunning clutch, the friction type overrunning clutch has incomparable torque transmission capacity, particularly in the one-way field, has higher working rotating speed, smaller residual torque, higher reliability and efficiency, longer service life and lower cost under the condition of the same torque, and has the advantages of relatively simple structure, fewer parts, relatively lower precision requirement, smaller volume and mass, relatively easy manufacture, very simple assembly, convenient and easy use and operation because an asymmetric rotary component is not arranged and the friction torque is irrelevant to the rotating speed. In the field of non-classified application, the potential is huge.

Drawings

FIG. 1 is an axial cross-sectional view of a simplest embodiment of a one-way overrunning clutch.

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

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

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

FIG. 5 is a schematic view of all possible abutting contact relationships of the blocking and embedding mechanism with various tooth shapes in the blocking working condition, which are shown in the form of a radial projection expansion diagram, wherein the left side contour lines in all the figures belong to the blocking ring, and the right side contour lines in all the figures belong to the auxiliary blocking ring; (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. 6 is an axial sectional view of an embodiment of the present invention having an axial fitting locking function.

Figure 7 is an axial half-sectional view of the axial locking ring of figure 6.

Fig. 8 is an axial half-sectional view of the second coupling member of fig. 6.

Figure 9 is an axial cross-section of an embodiment of the blocker ring of the present invention in the form of an axial displacement.

Figure 10 is an axial cross-section of one embodiment of the wheel-wheel transfer form of the present invention.

Fig. 11 is an axial cross-sectional view of a first package form of the present invention.

Fig. 12 is an axial cross-sectional view of a second package form of the present invention.

FIG. 13 is an axial cross-sectional view of an embodiment of the present invention in a two-axis assembly.

FIG. 14 is an axial cross-sectional view of a second embodiment of the present invention in a two-axis assembly.

FIG. 15 is an axial cross-sectional view of a third embodiment of the present invention in a two-axis assembly.

FIG. 16 is an axial cross-sectional view of an example of the use of the present invention in a two-axis assembly.

FIG. 17 is an axial cross-sectional view of an example of the use of the present invention in a two-axis assembly.

FIG. 18 is an axial cross-sectional view of a sixth embodiment of the present invention in a two-axis assembly.

Fig. 19 is an axial cross-sectional view of an example of the application of the present invention in a power motor start clutch.

Fig. 20 is an axial cross-sectional view of an axially twin embodiment of a first package form of the present invention.

Fig. 21 is a schematic axial cross-section of an axial, radial quad embodiment of a first package of the present invention.

Fig. 22 is a schematic axial cross-sectional view of an axial quad embodiment of a second package of the present invention.

Fig. 23 is a schematic axial cross-sectional view of an axial, radial quad embodiment of a second package of the present invention.

FIG. 24 is an axial cross-sectional view of a first embodiment of a controllable overrunning clutch.

Fig. 25 (a) is an axial sectional view of a right side view of the first engaging element in fig. 24, and (b) is a front view.

Fig. 26 (a) is an axial sectional view of a right side view of the separating ring in fig. 24, and (b) is a front view.

Fig. 27 is a schematic view of the second engaging element of fig. 24, (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. 28 is a schematic view of the blocker ring of fig. 24, (a) is a front view, (b) is an axial cross-sectional view of a left side view, and (c) is an enlarged expanded schematic view of a partial radial projection of the T-direction of (a).

Fig. 29 is a schematic view of the latch pin spring of fig. 24, with (a) being a right side view and (b) being a front view.

Fig. 30 is a schematic view of the manipulation ring of fig. 24, in which (a) is a front view and (b) is a left side view.

FIG. 31 is a partially developed schematic view of the radial projection of the tooth profiles of the individual interlocking mechanisms of FIG. 24 on the same outer cylindrical surface under different operating conditions; (a), (b) and (c) are schematic diagrams of the tooth form relationship when torque is transmitted in a first direction, wherein (a) belongs to the separation embedding mechanism, (b) belongs to the force transmission embedding mechanism and (c) belongs to the control embedding mechanism; (d) The (e) and (f) are the tooth-shaped relation schematic diagrams when the separation and the overrunning are carried out in the first direction, wherein (d) belongs to a separation embedding mechanism, (e) belongs to a force transmission embedding mechanism, and (f) belongs to a control embedding mechanism; (g) The (g) belongs to a separation embedding mechanism, (h) belongs to a force transmission embedding mechanism, and (i) belongs to a control embedding mechanism, and the arrow head represents the relative overrunning rotating direction.

FIG. 32 is a schematic diagram of a second embodiment of the controllable overrunning clutch shown in expanded partial cross-section (a) with the axis of the locking pin of the separator ring in the circumferential cross-section and (b) in the circumferential cross-section.

FIG. 33 is an axial cross-sectional view of a third controllable overrunning clutch embodiment.

Fig. 34 (a) is a front view of the control ring assembly of fig. 33, and (b) is an axial sectional view of the left side view.

FIG. 35 is a schematic diagram of a fourth embodiment of the controllable overrunning clutch, where (a) is an axial cross-sectional view of a compact structure and (b) is a schematic diagram of the operating ring of (a) corresponding to the position shown in (a).

Fig. 36 is a schematic diagram of a fifth embodiment of the controllable overrunning clutch, in which (a) is an axial sectional view of a simplified structure, (b) is an H-direction view of a release ring in (a), (c) is an H-direction view of a first engagement element in (a), (d) is a front view of a stop ring in (a), and (e) is an axial sectional view of a left side view of (d).

Fig. 37 is a schematic diagram of a sixth compact configuration of an embodiment of the controllable overrunning clutch, where (a) is a schematic diagram corresponding to the T-T section in (b), (b) is an H-direction view of the first engagement element in (a), (c) is an H-direction view of the release ring in (a), (d) is a front view of the operating ring in (a), (e) is an axial section view of the left side view of (d), (f) is a T-T section in (g), and (g) is an H-direction view of the break ring assembly in (a).

FIG. 38 is an axial cross-sectional view of a seven compact arrangement of an embodiment of a controllable overrunning clutch.

FIG. 39 is an axial cross-sectional view of a nine simplification of the controllable overrunning clutch embodiment.

FIG. 40 is an axial cross-sectional view of a highly compact configuration of an embodiment of the controllable overrunning clutch.

Fig. 41 is a schematic diagram of an eleventh exemplary controllable overrunning clutch, in which (a) is an axial sectional view of a simplified structure, (b) is an H-direction view of a first engagement element in (a), (c) is a front view of a link ring in (a), and (d) is an enlarged axial sectional view of a left side view of (c).

Fig. 42 is a schematic diagram of an eighth embodiment of the controllable overrunning clutch, in which (a) is an axial sectional view of a simplified structure, (b) is an H-direction view of a first engagement element in (a), and (c) is an axial sectional view of an operating ring in (a).

FIG. 43 is a schematic view of a twelfth embodiment of the controllable overrunning clutch, where (a) is an axial cross-sectional view of a compact structure and (b) is an H-direction view of the first engagement element in (a).

Fig. 44 is a schematic diagram of a thirteenth embodiment of the controllable overrunning clutch, in which (a) is an axial sectional view of a simplified structure, (b) is a front view of an unlocking ring in (a), and (c) is an axial sectional view of a left side view of (b).

FIG. 45 is a cross-sectional view of a fourteen compact structure of a controllable overrunning clutch embodiment.

FIG. 46 is a schematic representation of a fifteenth embodiment of the controllable overrunning clutch shown in FIG. 46, wherein (a) is an axial cross-sectional view of a compact structure, (b) is a front view of the control ring of (a), and (c) is an axial cross-sectional view of the left side view of (b).

FIG. 47 is a sixteen schematic views of an embodiment of the controllable overrunning clutch, wherein (a) is an axial cross-sectional view of a simplified structure, and (b) is a partially expanded schematic view of an outer cylindrical surface of a split ring in (a).

Fig. 48 is a schematic view of a seventeenth embodiment of the controllable overrunning clutch, wherein (a) is an axial sectional view of a simplified structure, and (b) is a partially developed schematic view of a first sleeve in (a) along a T-T cylindrical section.

Detailed Description

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

The simplest embodiment of the one-way overrunning clutch of the present invention is shown in fig. 1-4 and is in the form of a wheel-axle transmission. The first engaging element 50 is rigidly integrated with the first sleeve 187, and the second engaging element 60 is fitted around the first sleeve 187 with its fitting end faces facing each other, and constitutes a working fitting mechanism with the first engaging element 50. Gear teeth 206 are integrally formed on an outer cylindrical surface of second coupling member 60. The compression spring 182 is mounted between the non-engagement end face of the second engaging element 60 and a spring seat 184 in the form of a snap ring, the spring seat 184 being axially fixed in a snap ring groove of the first sleeve 187. The blocking ring 70 is a split elastic ring which is fitted in an annular conical recess on the inner ring side of the face tooth of the first engaging element 50 and, with the latter as its reference ring, has its sliding end face abutting against the blocking reference end face 128 and its engaging end facing towards the second engaging element 60.

The structure of the second engaging element 60 is shown in fig. 2. The outer ring surface of the embedding end is evenly distributed with second force transmission teeth 62, the inner ring surface is evenly distributed with auxiliary blocking teeth 102, and the two are radially connected into a whole. The auxiliary blocking tooth flanks 108, 66 and the tooth root face 110 are completely coplanar with the second force-transmitting tooth flanks 136, 66 and the tooth root face 138, respectively, and the blocking working face 104 thereof is a helicoid with a lead angle λ, | δ | < λ ≦ ρ. The second force-transmitting tooth 62 is a combination of a force-transmitting tooth and an auxiliary separating tooth, and the angle of inclination of the separating side 136 is significantly larger than the friction angle, so as to ensure that the two engaging elements can generate a large enough axial separating force when rotating relatively, and overcome the constraint of the pressing spring 182 to realize axial separation; the angle of inclination of the force-transmitting flank 66 is small, zero or negative (root retraction), preferably negative, to meet the requirements of a helical engagement. Correspondingly, the first engaging element 50 and the second engaging element 60 have a completely identical force transmission toothing and layout.

The stop ring 70 is constructed as shown in figure 3 as an open elastomeric ring having a cross-section 74. The blocking teeth 72 are rigidly and integrally distributed on the outer ring side of the annular base body 71, and each tooth surface is a spiral face type blocking working surface 76 with a lead angle lambda, a tooth flank surface 78c and 78d, a top surface 84 of a tooth top middle limiting bulge 82 and a spiral face type limiting flank surface 86 with a lead angle beta, wherein | delta | is more than or equal to beta and less than 180 degrees. The blocker tooth slot width is sufficient to accommodate the secondary blocker tooth 102. The bottom end face of the barrier ring is its circumferential sliding end face 90, and the top end face is its fitting end face. The outer circumferential surface of the blocking ring 70 and the mating inner bore surface of the first engaging element 50 are both conical surfaces with a small outside and a large inside.

As shown in fig. 4 (a), (b) and (e), the first engaging element 50 and the second engaging element 60 axially constitute both force transmissionThe embedding mechanism is also a one-way working embedding mechanism of the separation embedding mechanism, the blocking ring 70 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 circumferential freedom degree of the two embedding mechanisms can be zero. In the state of being embedded, the first and second bodies are,

wherein the content of the first and second substances,

representing the initial separation height of the separation/engagement mechanism in the non-designed separation/engagement direction (the horizontal line symbol represents the axial distance, the same applies hereinafter), the initial separation height in the designed separation/engagement direction is constant zero, and D _c Substitute for Chinese traditional medicineThe full-tooth embedding depth of the watch working embedding mechanism or the separating embedding mechanism,representing the minimum blocking height of the blocking engagement means,

the maximum limit embedding depth of the limit embedding mechanism is represented. The interrelationship of the engagement mechanism in the overrun condition is shown in fig. 4 (c) and (d).

It will be understood that the arrangement of three uniformly distributed, diametrically identical radial teeth on each of the blocking ring 70 and the secondary blocking ring, and the radial extension of the secondary blocking tooth 102 circumferentially exactly to the second force-transmitting tooth 62, is not essential, but purely for the sake of simplicity of construction and process, 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.

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

In the engaged condition, torque from the first shaft is transmitted through the first bushing 187 to the first coupling member 50, through the operative engagement mechanism to the second coupling member 60 and out through its upper gear teeth 206, or in reverse. Because of the absence of asymmetric rotating members and the fact that the circumferential pressure on the force-transmitting tooth flanks can be 100% for torque transmission, or, in terms of both surface compressive stress and bending strength, the effective utilization of the mechanical potential of the material can be made 100%, at a level much higher than the prior art by about 10% (about 90% being spent on normal compressive stress not directly related to torque), it has the advantages of not only a relatively higher operating speed, but also greater transmission and impact resistance, and a smaller volume. For example, the maximum torque would be much greater than the highest parameter 949,200 nm of the company formspers, usa, and the diameter would also be significantly less than its corresponding 965 mm, with a rotational speed that is many times greater than 75 revolutions per minute.

Referring to fig. 1 and 4, when the relative rotation speed of the two engagement elements in the designed direction of mutual separation is greater than zero, the overrunning clutch starts to separate and overrun, and the two separation flanks 136 and 126 in the disengaging and engaging mechanism slide and climb each other against the elastic force of the compression spring 182 until the axial separation distance D of the second engagement element 60 from the first engagement element 50 is reached _c . Due to the existence of parameters

Thus, the lowest point a of the secondary blocking tooth blocking running surface 104 of the control engagement mechanism already axially passes the lowest point G of the blocking tooth blocking running surface 76. Since the blocking ring 70 is still on the first engagement element 50 due to the self-restraint action of its radial elasticity, the process of exceeding the disengagement is sufficient to ensure that D is reached in the first synchronization of the axial disengagement distance of the control engagement, as long as the inlet margin K of the blocking engagement is not far from its lower limit value _c When the auxiliary blocking tooth stops working face 104 is already reliably raised from the blocking tooth stopping working face 76, the auxiliary blocking tooth stops working face 104 is mutually abutted to establish a stable self-locking static friction relationship, and the blocking ring 70 is driven to circumferentially slide on the reference end face 128 of the first joint element 50, so that the axial separation process between the two joint elements is stoppedStopping at the maximum separation distance. Therefore, the axial distance between the second engaging element 60 and the first engaging element 50 is constantly zero, and the two are in a zero-contact overrunning sliding friction condition without any impact and collision, which can remarkably reduce the wear speed of the two, eliminate noise and prolong the service life. In addition, the top surfaces of the first force transmission teeth or the second force transmission teeth can be made into a step shape with a high inner end, so that the average sliding friction radius and the residual torque under the exceeding working condition are obviously reduced. Meanwhile, the thrust sliding bearing technology is applied to divide the sliding end surface 90 into a plurality of wedge-shaped arranged fan-shaped areas in the circumferential direction so as to reduce the friction coefficient and the friction coefficientAnd (4) abrasion. Compared with a friction type overrunning clutch, the friction type overrunning clutch has smaller friction radius, sliding linear speed, residual torque and abrasion consumption.

It should be emphasized that in the control engagement mechanism of the present embodiment, the spirally rising surface characteristic of the blocking working surface is a prerequisite for ensuring zero collision of the force-transmitting teeth in the blocking operating condition, i.e., λ > 0 is required. And the lambda which is more than or equal to the lambda is a necessary condition for blocking friction self-locking between working surfaces in a blocking working condition, and is also a necessary condition for enabling the blocking and 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, so that the overall performance, the reliability and the service life of the overrunning clutch are greatly improved, and the compensation amount can be set as required during manufacturing. Particularly, when delta is more than 0 and lambda is more than 0 and less than delta, the auxiliary blocking teeth 102 can slide, rotate and climb relatively because the two blocking working faces which are contacted in opposite directions can not be self-locked, and the axial separation distance of the blocking embedding mechanism is larger than D _c Until the stop lug 82 is encountered. That is, with proper design, an over-running condition is obtained in which there is no contact between the two engagement elements. In addition, the self-locking relationship between the blocking faces only exists in the corresponding overrun rotation, that is, in the relative rotation in which the lift angle of the blocking face in the butt contact is made positive, but never exists in the relative rotation in which it is made negative, because the lift angle λ '= - λ < - δ | in the latter rotation, λ' completely falls within the self-locking requirement λ |, λ' > delta is not less than the lower limit. Thus, by changing the relative rotational direction of the two engagement members in the blocking condition, the original self-locking relationship between the blocking faces will be immediately lost, and the blocking ring 70 will no longer rotate integrally with the secondary blocking tooth 102, but will rest on the reference ring reference end face 128.

Therefore, the engagement reset of the overrunning clutch is very simple and natural, and the overrunning clutch can be used for reverse overrunning. That is, as long as the relative rotational speed of the two engagement elements in the designed direction of mutual disengagement is less than zero, the overrunning clutch is immediately engaged and reset. Or, whatever the extreme, at most one tooth in the above mentioned relative direction of rotation, i.e. one tooth rotated by the second coupling element 60 in a direction opposite to the arrow in the figure with respect to the first coupling element 50, the auxiliary blocking tooth 102 can slide off the blocking tooth blocking face 76, being reset in synchronism with the second force transmission tooth 62. See fig. 4 (c) and 4 (d). Only in the case that the second force transmission tooth 62 circumferentially misses the tooth notch of the first force transmission tooth before the point a of the lowest point of the auxiliary blocking tooth blocking working surface 104 has not slipped off the point G of the lowest point of the blocking tooth blocking working surface 76, the fitting reset process needs to be rotated by one tooth, but the phenomenon of seizure or tooth breakage never occurs. Because of the existence of

Namely, the limit of the initial separation height, the point I is axially separated from the point T, so that the relative rotation of the two force transmission teeth cannot cause the conditions of the axial overlap and extrusion of the tooth flank, but only can be the result of reverse overrunning separation; and point E and point H are axially equal in height enough to ensure that the blocking tooth notches rotate synchronously with the accompanying blocking tooth 102. Therefore, the two processes of the separation blocking and the embedding resetting of the overrunning clutch are simple in mechanism and reliable in process.

It should be noted that the constraint on the blocker ring 70 in this embodiment is only to ensure the desired reliability and performance and is therefore not necessary. The constraint mode is a self-constraint mode of the elastic open ring and also has another constraint mode of the complete ring. The stop ring 70, the restraining method, the stopping and engaging mechanism, the limiting and engaging mechanism, their relationships with other members, and the descriptions regarding δ and ρ are described in more detail in the chinese patent No. 200720146912.5 and the patent of the same invention filed by the applicant of this patent, which are incorporated by reference in their entirety and will not be described in detail herein. In addition, regarding the radial type position limiting scheme for the stop ring, the present applicant's chinese patent No. 200720146909.3 and its patent of the same name are described in more detail, and both patents are incorporated by reference in their entirety and will not be described in detail herein.

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

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

Fig. 6 to 8 show a configuration having an axial fitting locking function. A second splined hub-like sleeve 189, which is the center of rotation of the overall clutch, is in circumferentially fixed relation to internally splined teeth on the inner bore surface of second engagement element 60, all of which are constrained to second sleeve 189 by two snap rings 190. Between the blocking ring 70 and the external splines of the second sleeve 189 is a wave-shaped restraining spring 92, whereby the blocking ring 70 is always in abutment against the blocking reference end surface 128. The bearings 192 serve to reduce residual torque during overrunning.

The hook-shaped toothed ring 196 is a key feature of this embodiment, and as shown in fig. 7, there are "L" shaped hook-shaped teeth 200 that completely correspond to the first power transmission teeth at one end of its annular base body, and there are circumferential teeth protrusions 198 on the upper half of the teeth. The ring gear is circumferentially fixed (by a screw or by making the inner shoulder into a fitting tooth shape) to the outer circumferential surface of the first engaging element 50, the inner shoulder 274 can bear unidirectional tensile force, the tooth crest 202 of the "L" -shaped hook-shaped tooth is not higher than the starting point of the reverse parting curved surface of the first power transmission tooth 52 in the axial direction, i.e., the point T in fig. 4 (c), and only the circumferential tooth projection 198 projects from the power transmission side surface of the first power transmission tooth. Correspondingly, as shown in fig. 8, the outer end face of the second force transfer tooth 62 is formed with a circumferential groove 69 having a width and depth to accommodate the circumferential tooth projection 198. Thus, the fitting relationship can lock the axial relationship after the clutch is fitted. Of course, the thickness of the force transmitting teeth is reduced by the presence of the circumferential teeth 198, which loses little torque transmission capability.

It is understood that the present embodiment can be easily modified into the overrunning coupler, and the specific structure and description thereof can refer to the detailed description of the chinese patent with application number 200720146910.6 and the patent of the same name invention proposed by the present applicant, which are incorporated by reference in their entirety and will not be described in detail herein.

Fig. 9 shows an embodiment with the first coupling element 50 as secondary blocking ring and the second coupling element 60 as blocking reference ring. The blocking ring 70 is arranged in an end surface annular groove on the inner side of the second force transmission tooth 62, and is restrained on a blocking reference end surface 128 by a restrained spring 92 and a clamping ring 94, and the restrained clamping ring 94 is fixed in a clamping ring groove on the outer cylindrical surface of the notch of the annular groove; a stop shoulder is formed on one end of the second bushing 189 to be spaced apart from the first engagement member 50 by a washer 204.

Fig. 10 shows an example of an application in the form of a wheel-to-wheel transmission as an overrunning clutch, or brake, that controls rotational overrunning on distinct shafts. The ring gear 212 (not shown) coupled by a screw to the first coupling member 50 and the gear teeth 206 on the second coupling member 60 mesh with two gears on different shafts, respectively, for the purpose of limiting the overrunning of the different shafts. Here the second collar 189 is a complete optical collar and the ball and washer assembly 96 is added between the restraining spring 92 and the blocker ring 70 to reduce wear, and the inner diameter end of the second force transmitting tooth top surface 64 is formed with an axial step 65 to reduce the slip radius of the residual frictional resistance in the overrunning condition to reduce the frictional torque.

Fig. 11 shows a first package form of the present invention. The key to fig. 11, in comparison to fig. 6, is that the sealing ring 210 only assists, by securing the bowl-shaped housing 214 on the outer circumferential surface of the first engagement element 50, to achieve an integral encapsulation beyond the clutch. The ring gear 212 may be fixed to the outer cylindrical surface of the first engaging member 50 by a flat key, not by the bolt 208, or may be formed directly thereon.

The second package form of the present invention is shown in fig. 12. Is a direct encapsulation to the embodiment of fig. 1. In contrast to fig. 11, the bowl-shaped housing 214 of the present packaging has a function of transmitting torque by the engagement of the spline teeth 220 on its inner circumferential surface with the external spline teeth on the outer circumferential surface of the second engagement element 60, the key slots on its outer circumferential surface or the threaded holes 216 on the end surface being used for coupling a separate force transmission member. Of course, the force transfer member may also be formed directly on the bowl-shaped housing 214, such as a gear ring or belt groove. An annular end cap 222 is secured to the open end face of the bowl-shaped housing 214 by screws 224. The other end of the support ring 98 of the restraining spring 92 presses against the outer ring of the bearing 192 to provide simultaneous support of the blocker ring 70. Obviously, if the blocking ring 70 is in the form of a self-restraining resilient split ring, then the restraining spring 92 and support ring 98 would not be required.

It will be readily appreciated that the bearings 192 in both the first and second packs have a good radial positioning of the pack housing and reduce residual torque during overrunning. And both can be in the form of a shaftless sleeve without the sleeve 189 or 187, and mounted directly on the shaft.

Fig. 13-18 illustrate six application examples of the one-way overrunning clutch in a two-axle assembly of a loader. Fig. 13 is a simplest structural scheme thereof, and has the overall structural form of the embodiment of fig. 6. In which gear teeth 206 are formed directly on the outer circumferential surfaces of both engaging elements, with the first engaging element 50 being integral with the large gear 234 and the second engaging element 60 being integral with the small gear 232. The second shaft 188, which is fixed circumferentially with the second engaging element 60 by splines, is the common center of rotation of the assembly. Compression spring 182, in the form of a disc or diaphragm, is axially supported by washer 204, and washer 204 is axially retained by base bearing 192. Two bearings 228 separated by a spacer ring 230 are installed between the first engaging element 50 and the second rotating shaft 188, and the two bearings 228 and the same side base bearing 192 are axially limited by the spacer ring 226.

Fig. 14 is a modification of the arrangement of fig. 13, except that the second engaging element 60 is separated from the pinion 232, the mass is reduced to increase the speed of the fitting return of the second engaging element 60, and the pressing spring 182 is changed into a set of cylindrical helical compression springs which are uniformly distributed in the circumferential direction. Obviously, a single helical compression spring or the like is also possible.

Fig. 15 is again a variation on the fig. 14 arrangement, except that pinion 232 is subjected to a significant shaft plane bending moment. One bearing 228 is omitted and one bearing 236 is added, so that the small gear 232 and the large gear 234 are connected into an axially fixed body by the bearing 236, thereby realizing the mutual enhancement of the bending resistance. Of course, the bearing 236 may be in the form of a thrust bearing axially therebetween.

Fig. 16 is a modification of the arrangement of fig. 15. In this example, the pinion 232 is rigidly integrated with the second shaft 188, all other members including spline teeth are axially reversed by 180 degrees, the entire overrunning clutch is enclosed between the bearings 228 and 236, and the spring seat 184 is used as a fixed shaft of the bearing 236.

Fig. 17 shows a two-shaft assembly corresponding to the second assembly type, which has the disadvantage that the installation of a rolling bearing between the large gear 234 and the rotating shaft will necessarily increase the diameter of the blocking ring 70 and thus the residual torque during overrunning. Alternatively, spline coupling teeth may be formed in the inner bore of the second engaging element 60 as shown in fig. 18.

Fig. 19 shows an example of the application of the one-way overrunning clutch to the electric starting clutch of the engine. It can be regarded as a modification of the pinion 232 in the embodiment of fig. 15 in exchange for the spring seat 184 fixed to the end surface of the second rotating shaft 188 by the screw 240. The compression spring 182 presses against a shoulder on the outer cylindrical surface of the second engagement member 60. The first engagement element 50 is axially restrained by a gearbox bearing seat 238 (between which rolling bearings may also be mounted). The captive snap ring 94 is mounted on a second rotatable shaft 188 having externally splined teeth formed on the shaft end.

Fig. 20 shows an axial duplex embodiment of package one. This example is a back-to-back dual clutch of the two clutches shown in fig. 11, with the two first engagement elements merging into a first engagement element 50 having double-ended force-transmitting teeth with strictly identical circumferential positions. By controlling the circumferential positions of the spline teeth on the two second engaging elements 60, the circumferential staggering of the force transmission teeth 62 of the two second engaging elements is ensured by half a pitch, so that the maximum nominal circumferential angle of the clutch engagement reset is reduced by half, and the clutch engagement reset is conveniently applied to indexing occasions. Additionally, the second bushing 189 and the cinching collar 242 with the V-shaped circumferential groove are both common.

The two twin clutches shown in fig. 20 may also be radially twin into the embodiment shown in fig. 21. The second engagement elements 60a and 60b on the same end side thereof are circumferentially fixed by splines. All of the stop rings 70 are split elastomeric rings, split cross-sections 74. The circumferential positions of the four turns of force-transmitting teeth on the two end faces of the first engagement element 50 are exactly the same, and the force-transmitting teeth 62 on the four second engagement elements are staggered by 1/4 of a revolution in the manner described in fig. 20, so that the maximum nominal circumferential angle of the clutch engagement reset is reduced to 1/4 of the original nominal circumferential angle.

Fig. 22 shows an axial quad embodiment of package two. This example is a re-doublet of two back-to-back doublet schemes of the clutch shown in fig. 12. In order to facilitate manufacture and simplify the structure, the first sleeve 187 is divided into two parts, the circumferential positions of the force transmission teeth and the flat key grooves are strictly identical, and an end face seal ring 210 is additionally arranged between the two parts. Likewise, the circumferential positions of the force transmission teeth 62 between the four second engagement elements are each staggered by 1/4 of a revolution.

Fig. 23 shows an axial-radial quad embodiment of package two. The substance is exactly the same as above. And are not repeated. It should be noted in particular that the double coupling is not a requirement for an increased torque transmission capacity, but only an increased indexing capacity. In the multiple arrangement of fig. 21 to 23, only one fitting mechanism is in the fitting state at most, and it is only necessary to draw all the fitting mechanisms in the fitting state for the sake of convenience of drawing.

Fig. 24 shows a first embodiment of the controllable overrunning clutch, which is a bidirectional overrunning clutch with a first packaging form. In comparison with fig. 11, a separating ring 120 between the first engaging element 50 and the blocking ring 70 in the radial and axial directions is added, which positions the locking mechanism and the positioning operation mechanism. The split ring positioning locking mechanism is composed of three pairs of axial direction through holes 154a and 154b of the first engagement element 50, three pairs of axial direction pin holes 152a and 152b of the split ring 120, and three pairs of locking pins 150a and 150b which are slidably fitted in the above-mentioned direction holes, respectively. Two groups of components with tail numbers a and b respectively form two sub-locking mechanisms, and each sub-locking mechanism corresponds to one working direction. The positioning and manipulating mechanism is composed of a snap ring 190, a manipulating ring 140, and a plate-like locking pin spring 156. The outer diameter end of the plate-shaped locking bolt spring 156 projects into an axially perpendicular recess in the outer cylindrical surface of the locking bolt 150, the radial middle of which is pressed against the non-engaging end face of the first coupling element 50 by the angularly rotatable actuating ring 140, the radial lugs 157 of which for circumferential positioning engage in the end-face recesses 59 of the first coupling element 50. Snap ring 190 axially constrains manipulation ring 140 from the outer end to first engagement element 50. See fig. 25 and 29. In this and subsequent embodiments, the blocking reference ring is acted upon by the separating ring 120, which is acted upon by the first engaging element 50. And the end face force transmission tooth number and the end face separation tooth number of all the components are completely the same and are strictly and uniformly distributed in the circumferential direction.

For the purpose of distinction and understanding, the present specification provides that the separating ring is fixed circumferentially by the first sub locking mechanism in a first relative position with respect to the separating reference ring corresponding to the first direction, the separating ring is fixed circumferentially by the second sub locking mechanism in a second relative position with respect to the separating reference ring corresponding to the second direction, and the numbering of all the components corresponding to the first sub locking mechanism is affixed with a tail number a, and the numbering of all the components corresponding to the second sub locking mechanism is affixed with a tail number b. The circumferential angle between two opposite positions is uniformly designated as epsilon. When only one direction of operation or general direction is indicated, no distinction is made and no tail numbers a or b are added.

As shown in fig. 25, on the outer ring side of the fitting end surface of the first engaging element 50, there is uniformly provided a circle of power transmission teeth 52, both side tooth surfaces of which have a small inclination angle, are zero or have a negative value (i.e., the tooth root is retracted), and are only used for transmitting torque; in an annular region of the non-fitting end surface corresponding to the separation reference end surface 58, three pairs of axial direction through holes 154a and 154b each having an inner interval circumferential angle E are arranged. In addition, a threaded bore 248 for fastening the force-transmitting toothed ring and a recess 59 in the end face are arranged on this end face.

As shown in fig. 26, a circle of separating teeth 122 is formed on the fitting end surface of the separating ring 120, and both side tooth surfaces of the teeth have a circumferential separating function, similar to the auxiliary separating tooth side surface 136 described above, and the cross section of the teeth is trapezoidal, crowned trapezoidal or the like. The inner bore shoulder end surface of the separating ring 120 is a stop datum end surface 128. On the non-fitting end face of the ring, three pairs of axial direction pin holes 152a and 152b each having an inner interval circumferential angle of E-epsilon are correspondingly arranged on a revolution circumference having the same diameter as the center of the direction through hole 154. E is a free amount, and can be arbitrarily chosen, but it should be avoided that the direction pin holes 152a and 152b overlap.

The structure of the second engaging element 60 is shown in fig. 27. The second force transmission tooth 62, the auxiliary separating tooth 132 and the auxiliary blocking tooth 102 are sequentially formed in three annular areas on the embedded end face from outside to inside. The tooth profiles of the second force transmission teeth 62 and the satellite disengagement teeth 132 are identical to the first force transmission teeth 52 and the disengagement teeth 122, respectively. The subsidiary blocker tooth 102 is symmetrically formed with a blocker working surface 104 at both sides of the tooth crest. For ease of machining, the three face teeth are joined together in a radially integral manner with the effect that, after cutting away part of the entities of the satellite separating tooth 132 and the satellite blocking tooth 102, bounded by the radially extending surface of the second force-transmitting tooth sheave profile, the circumferential clearance of the separating-engaging mechanism remains unchanged and the blocking running surface 104 of the satellite blocking tooth remains intact. Therefore, the corresponding tooth body portion of the middle tooth top 106 of the auxiliary blocking tooth 102 and the root of the auxiliary separating tooth flank 136 are cut off, the auxiliary blocking tooth flank 86 is coplanar with the second force-transmitting tooth flank 66, and the tooth root surfaces 110, 138 and 68 of the auxiliary blocking tooth 102, the auxiliary separating tooth 132 and the second force-transmitting tooth 62 are coplanar.

As shown in fig. 28, the blocking tooth 72 is integrally formed on the same end face of the ring-shaped base body 71, i.e., the blocking tooth root face 80. Two sides of the top surface of the blocking tooth are symmetrically provided with two identical spiral surface type blocking working surfaces 76, the lead angle is lambda, | delta | < lambda ≦ rho. The middle part of the tooth top is provided with a limit bulge 82, both side surfaces 86 of the limit bulge are helical surfaces with the lead angles of beta, and beta is more than or equal to | delta | and less than 180 degrees.

Fig. 29 shows the structure of the plate-like lock pin spring 156. The radial spring strips 156a and 156b of the same pair have a circumferential angle E, and for ease of installation and control, the three pairs are all formed on the same annular base, with the detent lugs 157 of the base engaging the notches 59 of the first engagement element to ensure that the spring strips 156a and 156b are aligned with the directional through holes 154a and 154b, respectively, of the first engagement element. In addition, the radially outer end portions of the spring pieces 156 each have a tilted shape as shown in fig. 29 (a).

Fig. 30 shows the structure of the manipulation ring 140. The ring end face 141 has an annular step 276 formed on an inner ring region and three pairs of cylindrical cam projections 142 and 144 formed on an outer ring region. Wherein the rotation stop restricting protrusion 142 is disposed in the middle of the groove between the cam protrusions 144a and 144b, dividing the groove into two grooves 145a and 145b. The circumferential angle between any point in the two grooves is less than E, so that one of the spring pieces 156a and 156b must circumferentially overlap the protrusion 144a or 144b. In addition, to facilitate circumferential pressing of the spring plate 156 by the projection 144, the respective sides thereof are machined with ramp surfaces 143.

Fig. 31 shows the relationship between the tooth profiles of the respective interlocking mechanisms of fig. 24. The first engaging element 50 and the second engaging element 60 form a force-transmitting engagement mechanism having a circumferential degree of freedom θ _t The mechanism can be separated smoothly without any contact or collision when the separating and embedding mechanism surpasses and separates in two directions; the separating ring 120 and the auxiliary separating ring form a separating and embedding mechanism with zero two-way initial separation height; the stop ring 70 and the auxiliary stop ring form a control embedding mechanism, and the inlet margin K of the mechanism is

(the correlation symbol indicates the circumferential angle between the corresponding points), where K > θ _c +θ _f + γ + η; in the state that the clutch is engaged with the clutch,

here, D _t Representing the full-tooth embedding depth of the force-transferring embedding mechanism, and other parameters are described as before. All possible abutting contact conditions of the blocking engagement with various tooth profiles in the blocking mode can be seen in fig. 5.

The present embodiment will be further described with reference to fig. 24 to 31 in conjunction with the working process. Since the processes of force transmission, overrunning, separation blocking and mosaic resetting are completely the same as or similar to the one-way overrunning clutch, the description is not repeated here, and only the reversing mechanism and mosaic resetting process are mainly described.

Fig. 24 and fig. 31 (a) to (f) correspond to the first direction, and the release ring is fixed at a first relative position in the circumferential direction by the first sub lock mechanism. That is, the lock pin 150a is stably fitted into both the direction through hole 154a of the first engaging element 50 and the direction pin hole 152a of the split ring 120 by elastic pressing of the outer diameter end of the spring piece 156a against the tail end groove thereof; the pressing force of the spring plate 156a comes from the pressing of the cam protrusion 144a of the handle ring 140 to the radial middle thereof. At this time, the spring piece 156b is just positioned in the cam groove 145b of the operating ring 140 to maintain its original tilted state, and drives the lock pin 150 to be fitted into only one hole of the direction through hole 154b of the first engaging element 50. Fig. 31 (a) - (c) show the force transfer conditions in the first direction, and fig. 31 (d) - (f) show the overrun conditions in the first direction.

During the embedding reset process, although the blocking tooth notch in the one-way overrunning clutch does not have the possibility of synchronously rotating along with the auxiliary blocking tooth 102, the K is more than theta _c +θ _f The parameter + γ + η ensures that, as well as the preceding description, it is also possible to ensure that the synchronous engagement reset of the entire clutch is achieved after at most one force transmission tooth has been rotated, without the reverse blocking situation occurring, as long as K is not far from its lower limit.

The reversing operation for changing the operating direction of the overrunning clutch from the first direction to the second direction is very simple. As shown in fig. 24, the operating ring 140 is rotated in the second direction until the limit protrusions 142 thereof abut on the spring pieces 156 a. The clockwise direction in the left view of fig. 24 is the second direction. After the rotation, the spring piece 156a just falls into the groove 145a of the operating ring 140, and immediately restores the original tilted shape and drives the locking pin 150a to move out of the separating ring direction pin hole 152a, so that the locking of the separating ring 120 is released, and the first sub-locking mechanism of the a-series temporarily stands by. At the same time, the spring plate 156b is bent axially by the projection 144b and its radially outer end is continuously pressed elastically against the locking pin 150b, so that as long as the clutch rotates in the second direction, the first coupling member 50 must rotate relative to the release ring 120 through the circumferential angle epsilon, and the pin head of the locking pin 150b is naturally inserted into the direction pin hole 152b, thereby finally completing the entire reversing operation. That is, the separating ring 120 is fixed at the second relative position by the second sub-lock mechanism of the b-series (fig. 31 (g)). In this relative position, the overrunning clutch has full functionality similar to that in the first direction. Fig. 31 (g) to (i) show the overrun condition in the second direction. The reverse operation of the above operation is performed to change the working direction of the overrunning clutch from the second direction to the first direction. I.e. the reversing operation, is simply a swinging movement of the operating ring 140 back and forth between two circumferential positions. It is understood that the reversing operation is a switching operation of the operating states of the first and second sub lock mechanisms whose stable states are opposite to each other by the circumferential or axial reciprocating motion of the operating ring 140 or the like. The result is necessarily a reciprocal oscillation of the separating ring 120 between the first and second relative positions.

It must be emphasized that: the commutation can only be performed in the engaged state, no matter whether there is rotation or not; the direction of rotation of the handle ring 140 when reversed relative to the desired operational direction of rotation may be the same or opposite, depending only on the layout of whether the protrusions 144 or recesses 145 are disposed between a pair of directional through holes. It should be noted that, in this embodiment and all the following embodiments, all the control rings for operating the retaining ring locking mechanism and the like to control the operating direction or the operating state of the overrunning clutch, such as the operating ring 140 in this embodiment, and the rotation stop ring 162, the unlocking ring 173 or the link ring 170 in the subsequent embodiments, have their annular base and the two mating surfaces between the inner and outer cylindrical surfaces of the annular operating groove 55 on the first engaging element 50, which are all smooth cylindrical surfaces that can be slid. In addition, it can be understood that if the corresponding separating ring control mechanism is removed, and the axial duplex embodiment is implemented in a back-to-back rigid integrated manner, i.e. the working directions of the two opposite sides are mutually controlled, the patent scheme of the basic jaw self-locking differential proposed by the applicant (utility model with application number 200720146912.5 and patent of the same name) can be obtained. Alternatively, the prior art dog-type self-locking differential is only one specific example of an application of the present invention.

The second embodiment of the invention is a bidirectional overrunning clutch with a second packaging form. As shown in fig. 32, it is essentially the result of the following major improvements to the embodiment of fig. 24: the locking pin 150 of the separating ring positioning locking mechanism is divided into two parts, namely the locking pin 150 and the reversing unlocking pin 146 belonging to the positioning control mechanism; the mode that the locking pin 150 exits the locking station is changed from elasticity to rigidity; the split ring orientation pin hole 152 is changed from a semi-circular hole to a complete circular hole; the locking pin spring 156 is deformed into a cylindrical shape in the separating ring direction pin hole 152 by a plate shape in the operation groove 55, but still acts on the rear end of the locking pin 150. The length of the reverse unlocking pin 146 is equal to the depth of the directional through hole 154, see fig. 32 (b). The operating ring 140 still takes the form of an end-type cylindrical cam similar to that of figure 25 and also adopts an anti-reciprocal arrangement for facilitating automatic control by locating the recesses 145 between the same pair of directional through holes. The overrunning clutch in fig. 32 operates in a first direction. At this time, the operation of switching the working direction from the first direction to the second direction can be completed by only driving the operation ring 140 to rotate in the second direction, i.e., to rotate downward in fig. 32 (b) (the rotation stop point is not shown). Because rotation forces the reversing release pin 146a to push the locking pin 150a back into the release ring direction pin opening 152a and aligns the notch 145b of the operating ring 140 with the reversing release pin 146b, the locking pin 150b will engage the direction through opening 154b to lock the release ring 120 in the second relative position when the locking pin spring 156b is axially biased, thereby ending the full reversing motion. The process is completely as before and is not repeated.

In contrast to the release ring positioning lock mechanism and the positioning operation mechanism in the embodiment shown in fig. 24 and 32, it is apparent that they are structurally related only to the first engagement element 50 as the release reference ring, the release ring 120 as the blocking reference ring, and the blocker ring 70, and are not related to the clutch structure, the packing form, and other components. The essential differences and variations between the two embodiments are only shown in the working mechanism and the specific structure of the two mechanisms, in particular the positioning and manipulating mechanism, that is, the part for controlling the working state and the working direction. Therefore, in order to not repeat the explanation and highlight the essential features of the embodiments, all the following embodiments are illustrated and described in the form of a simplified structure diagram of a package type two, and only relate to the control part, and do not relate to the already-described contents related to torque transmission, separation override, blocking limit, package type and the like.

The embodiment of fig. 33 is a direct modification of the embodiment of fig. 32 in that the positioning and manipulating mechanism directly utilizes the reciprocating motion in the axial direction to control the locking pin 150. Three locking pins 150a are still disposed in the direction pin holes 152a of the separating ring, but three locking pins 150b are disposed in three axial through holes of the annular base 71 of the operating ring 140, respectively, at the same end as the three axial direction-changing unlocking pins 146 formed on the ring, see fig. 34. The locking pins 150b are each formed with a radial through hole at the trailing end thereof, through which passes a locking pin spring 156b, specifically a spring wire snap ring. The spring is also axially constrained to the operating ring 140 by six rivets 158 which pass through the trailing radial through holes. Riveting one of the rivets 158 circumferentially secures the spring 156b (see fig. 37 (g)). The height of the end surface of the direction switching release pin 146 is equal to the depth of the direction through hole 154 but less than the height of the top surface of the locking pin 150 b. The inner bore surface 148 of the operating ring 140 and the cylindrical surface of the reverse trip detent 146 are the guide surfaces for its axial movement.

The manipulation ring 140 of fig. 33 corresponds to a first direction first relative position. If the ring is axially pressed toward the first coupling member 50, the reverse unlocking pin 146 immediately pushes the locking pin 150a back into the unlocking ring direction pin hole 152a, and the locking in the first direction is released. Meanwhile, the locking pin 150b is in a charged state ready to be inserted into the direction pin hole 152b and locked in the second direction by the elastic pressure of the locking pin spring 156b. The whole process is completely as before and is not repeated. The reverse operation of the above operation is performed to change the working direction of the overrunning clutch from the second direction to the first direction.

Modifying the embodiment of fig. 32, a conventional cylindrical cam pin slot control scheme, as shown in fig. 35, may also be achieved. In this embodiment, the split ring positioning lock mechanism and the positioning operation mechanism are combined into one link mechanism by sharing the link ring 170. Wherein the link ring 170b is rigidly integrated with three evenly distributed locking pins 150 b. The link ring 170a is rigidly integral with three equispaced locking pins 150a, and three corresponding through holes are formed in the ring for axial passage of the locking pins 150 b. Three radial protrusions 254a and 254b are uniformly distributed on the inner circular surfaces of the two interlocking rings, and the two protrusions are respectively inserted into three circumferential guide grooves 176a and 176b on the outer cylindrical cam surface 266a of the operating ring 140, as shown in fig. 35 (b). The operating ring 140 is fitted over the outer cylindrical surface of the operating slot 55 and rotation of the ring relative to the first engagement element will cause reciprocal axial movement of both link rings 170a and 170 b. The equal height surfaces of the locking pins 150a and 150b at the time of axial displacement of the both square pillar top surfaces are not higher but are preferably flush with the separation reference end surface 58. The screw 224 secures the operating slot cover 246 to the first engaging element 50. The cylindrical surfaces between the operating ring 140 and the operating slot 55 and the operating slot cover 246 are sealing surfaces. The wave return spring 250 and washer 204 fit between the operating slot cover 246 and the outer shoulder of the operating ring 140 to provide the latter with space for retraction and resilient compression.

As shown in fig. 35 (b), there is no axial overlap between the guide grooves 176a and 176b. When the two linkage rings are assembled, the radial protrusions 254a and 254b of the two linkage rings are respectively inserted into the respective grooves from the inlet A, C in sequence or simultaneously.

Fig. 36 shows a fifth embodiment of the controllable overrunning clutch, modified from the embodiment of fig. 32 by the addition of a blocker ring rotation prevention mechanism that positively locks the blocker ring 70. The embodiment is a bidirectional overrunning clutch which can be successfully reversed at any time and under any condition, and can also be used as a controllable bidirectional sliding device of a motor vehicle. In comparison with fig. 32, the length of the reversing unlocking pin 146 is still equal to the depth of the direction through hole 154, and the side surface of the unlocking pin is composed of incomplete inner and outer cylindrical surfaces, the cross section of the reversing unlocking pin is crescent-shaped, the outer cylindrical surface of the reversing unlocking pin is in sliding fit with the cylindrical hole part of the direction through hole 154 and the inner cylindrical surface of the direction pin hole 152, and the inner cylindrical surface of the reversing unlocking pin is in sliding fit with the outer cylindrical surface of the unlocking convex tooth 149 in the axial direction and the circumferential direction. The unlocking protrusion 149 defines the unlocking pin 146 from the inner diameter direction, and is an axial annular protrusion inserted into an annular portion of the direction through hole 154, and an outer annular surface thereof is a portion of a rotating cylindrical surface on which the axial center of the direction pin hole 152 is located, as shown in fig. 36 (a) to 36 (e). The anti-rotation pin 160 is inserted into the anti-rotation through hole 172 of the release ring through the annular limit through hole 174 of the first engagement element 50. For integral control, three pairs of unlocking lugs 149 and four rotation stop pins 160 are integrally formed on a rotation stop ring 162, which is axially confined in the operating groove 55 by a snap ring 190. The return spring 250 is installed between the rotation stop ring 162 and the operating ring 140, and axially presses the operating ring 140 against the sidewall of the operating groove 55, and presses the rotation stop ring 162 against the snap ring 190 at the standby position. In the standby station, the top surface of the unlocking convex tooth 149 is not higher than the top surface of any unlocking pin 146, and the pin top surface of the rotation stopping pin 160 is positioned in the rotation stopping through hole 172; in the detent position where the detent ring 162 presses the return spring 250 to the extreme, the top of the unlocking lobe 149 can be inserted into the corresponding annular groove 167 of the release ring, and the top of the detent pin 160 can pass over the stop ring reference end face 128 on the release ring 120.

As shown in fig. 36 (a) to 36 (E), the circumferential angles between the same pair of through holes 154a and 154b and the same pair of unlocking lugs 149a and 149b are all E, and the circumferential angle between the same pair of pin holes 152a and 152b is E-epsilon. The orientation through holes 154, orientation pin holes 152, and anti-rotation pins 160 are not required to be evenly spaced. Since the detent pin 160 is always fitted in the detent through hole 172 of the release ring, the detent ring 162 is fixed to the release ring 120 in the circumferential direction by the detent pin 160. Therefore, the release ring 120 constitutes a release ring stopper mechanism by the rotation stopper pin 160 and the annular stopper through hole 174 on the first engaging element 50. The circumferential degree of freedom of the limiting mechanism is theta _d ，θ _d Not less than epsilon, but not so much as to cause the breakaway ring teeth to begin to have the ability to completely prevent axial engagement of the clutch. That is, the separating ring separating teeth 122 must not intrude too much into the first power transmission tooth space in the circumferential direction. Optimum value theta _d And = epsilon. Further, the degree of freedom in the circumferential direction between the unlocking protrusion 149 and the annular portion of the directional through-hole 154 must not be less than θ _d . And the circumferential positions of the annular limiting through hole 174 and the annular part of the direction through hole 154 are determined with the effect that when the rotation stopping pin 160 is located at the circumferential center of the annular limiting through hole 174, the unlocking lobe 149 is also located at the circumferential center of the annular part of the direction through hole 154, and the unlocking lobe 149 at the circumferential extreme position must also confine the unlocking pin 146 from the inner diameter direction; with this effect, the stop on the sliding end face 90 of the blocking ring is determinedThe circumferential position of the turning grooves 91 or the two open sections 74, i.e. the positions in which the blocking rings 70 stay when the rotation stop pins 160 are inserted into them, is such that the axial engagement resetting of the overrunning clutch is possible, preferably with a positioning which results in the peripheral centering of the secondary blocking teeth in the tooth spaces of the blocking teeth after engagement. The detent recess 91 or the two open sections 74 of the blocking ring, the detent through-hole 172 of the release ring, the limit through-hole 174 of the first engagement element, and the detent pin 160 of the detent ring 162 together form a detent mechanism for the blocking ring.

The operating condition shown in fig. 36 corresponds to a first orientation, the separating ring 120 being held in a first relative position by the first sub locking mechanism. The reversing process is completely the same as the embodiment shown in fig. 32, and the operating state of the a-series and b-series sub-locking mechanisms can be switched by rotating the operating ring 140. In the process, if the overrunning clutch is in a jogged state, the locking process of the separating ring 120 is completely the same as the previous process, and the reversing operation is ended and is not repeated; if the overrunning clutch is in the blocking working condition, the reversing rotation enables the forward overrunning blocking working condition to be changed into the reverse overrunning blocking working condition, and although the work rotation after reversing can ensure that the separating ring is successfully locked at the second relative position, the purposes of embedding, resetting and torque transmission of the overrunning clutch can not be achieved by breaking away from the reverse blocking working condition. In this case, the second operation is required, that is, the energy-accumulating spring 252 is pressed by external force during the rotation in the second direction, and the clutch is released immediately after the clutch is reset, which can be accomplished in a moment. Here, the elastic force of the charge spring 252 is greater than the sum of the elastic forces of the return spring 250 and the latch pin spring 156 and is less than the elastic force of the compression spring 182. The process is followed by applying sufficient axial force to the energy storage spring 252 to force the unlocking lobe 149 integral with the anti-rotation ring 162 to eject the locking pin 150 back into the directional pin aperture 152, releasing all directional locking, and simultaneously engaging the unlocking lobe 149 into the annular recess 167 in the release ring, the anti-rotation pin 160 also simultaneously abuts the stop ring sliding face 90 and engages the anti-rotation recess 91 or the two open sections 74 on that face during relative rotation, thereby stopping the blocking ring 70 circumferentially on the release ring 120. Then, the separating ring 120 is rotated integrally with the auxiliary blocking tooth 102 in the circumferential direction by the blocking ring 70 until being blocked by the separating ring stopper mechanism. Thereafter, the auxiliary blocking tooth 102 slides and climbs relative to the blocking tooth 72, after turning over the projection 82 in the middle, the auxiliary blocking tooth is embedded into the next tooth socket of the blocking ring, other embedding mechanisms are synchronously embedded and reset, and the force transmission embedding mechanism is in a correct force transmission state. At this time, the external force applied to the energy storage spring 252 is removed, the return spring 250 forces the rotation stop ring 162 to synchronously return to the standby position, and the locking pin 150b is then inserted into the direction through hole 154b again, and finally the second direction is locked. It will be appreciated that this function can also be used to force engagement to transmit torque regardless of whether the clutch is in an overrunning condition.

The above is a rotation-stopping embedding resetting method, and the precondition for use is that the lift angle beta of the two side surfaces 86 of the limit bulge at the middle part of the tooth crest of the blocking tooth must satisfy the inequality: | δ | ≦ β < 90 ° - φ, and it is best for the side surface 86 to be coplanar with the barrier working surface 76, i.e., β = λ.

To prevent the release pin 146 from being mistakenly inserted into the direction pin hole 152, a retaining shoulder or radial protrusion may be disposed at the rear end thereof, and a corresponding groove may be disposed outside the direction through hole 154.

In this embodiment, the controlled nature is that the function of the release ring and blocker ring can be manually eliminated simultaneously, making the clutch immediately equivalent to a dog clutch. And the overrunning clutch will immediately resume all the functions of the controllable runner in the direction determined by the circumferential position of the operating ring 140 after the above-mentioned forced external force is removed. When the two-way controllable sliding device is used as a two-way controllable sliding device of a motor vehicle, the sliding working condition can be forcibly ended only by inching by forced external force or pressing the energy storage spring 252 for a long time, and the transmission connection between the engine and the wheels is recovered.

Referring to fig. 37, there is shown a modification of the embodiment of fig. 32 to which is added a strong deterrent swivel 162 having a configuration similar to that of fig. 34, a two-way overrunning clutch or two-way glider that does not require special enforcement but can be successfully reversed at any time and in any situation. As shown in fig. 37 (a), a screw 224 fixes the operation groove cover 246 to the first engagement element 50, instead of the snap ring 190 axially restricting the operation ring 140 in fig. 32 (a). The anti-rotation rings 162 are radially located within the steering ring 140, independent of and in communication with each other. The operation principle of the operation ring 140 is completely the same as that of the embodiment of fig. 32 and 36, and the operation principle of the rotation stopping ring 162 is completely the same as that of the embodiment of fig. 36, which are not repeated.

The technical key of the present embodiment is that a spring steel ball mechanism for axial limiting is arranged between the radial joint surfaces of the operating ring 140 and the rotation stop ring 162. Wherein the springs and balls that make up the mechanism are disposed in radial holes 179 in the axially projecting inner circular surface of the operating ring 140 where the cam groove 145 is located, as shown in fig. 37 (d), (e). A circumferential shoulder on the cylindrical surface constituting the mechanism is formed in the axial middle of the cylindrical surface in the circumferential notch 165 of the detent ring 162, as shown in fig. 37 (f), (g). When assembled, the axial projection of the cam groove 145 on the handling ring 140 is located just inside the circumferential notch 165. The overall construction of the anti-rotation ring 162 is identical to that of fig. 34, except that the anti-rotation leader pin 164 replaces the reverse unlocking pin 146, the anti-rotation pin 160 replaces the locking pin 150b, and the anti-rotation pin spring 161 replaces the locking pin spring 156b. Wherein the rotation stop guide pin 164 is inserted into the rotation stop guide pin hole 166 of the release ring through the annular rotation stop guide post hole 168 on the first engagement element, and the rotation stop pin 160 is inserted into the rotation stop through hole 172 of the release ring through the annular limit through hole 174 on the first engagement element 50.Γ in fig. 37 (b), (c), and (g) takes an arbitrary value. The pin top surface height of the rotation stop pilot pin 164 must not be higher than the separation ring separation tooth root surface 129 when the rotation stop ring 162 is axially in the standby position, and must be higher than the tooth root surface 129 when the rotation stop ring 162 is axially in the rotation stop position after the right shift; the pin top surface height of the anti-rotation pin 160 must not be higher than the blocking reference end surface 128 on the separating ring 120. As shown in FIGS. 37 (a) to (c) and (f). In addition, the detent pin spring 161, which is still a spring wire split ring, is formed with three axial spring cocked bends 163 at the midpoint of the commutation rotation interval of the three pulse protrusions 147 on the end surface of the operating ring 140 in the circumferential direction. The relative geometric and performance parameters of the spring warp 163 and the spring steel ball mechanism are determined by the effect that the axial reaction force on the spring warp 163 is not greater than the axial resistance generated by the spring steel ball mechanism during the non-reversing process, and the elastic reaction force generated by the spring warp 163 due to the pulse compression of the three pulse protrusions 147 during the reversing process of the circumferential rotation is greater than the axial resistance generated by the spring steel ball mechanism but less than the elastic reaction force generated by the compression spring 182.

The embodiment is characterized in that the forced rotation stopping operation is merged in the reversing operation without special operation. Regardless of whether the clutch is in the blocking condition, the operating ring 140 will apply a pulse-like axial elastic compression to the rotation stop ring 162 by the pulse contact of the pulse protrusions 147 with the spring bends 163 during each circumferential rotation of the reversing operation. In this process, if the clutch is in the blocking condition, the rotation stop ring 162 is moved to the right to the blocking position and stops the rotation of the blocking ring to force the clutch to be successfully reversed, and then immediately returns axially to its standby position by pressing the rotation stop pilot pin 164 with the satellite release teeth 132 during the fitting reset. If the clutch is in the non-blocking condition, the rotation stop ring 162 will only stay in the standby position due to the blocking of the rotation stop pilot pin 164 by the auxiliary release teeth 132 and the lack of elastic reaction force on the spring cocking curve 163.

It should be noted that when the present embodiment is used as a skid, a reversing mode should be adopted to forcibly end the skid condition. Additionally, it is contemplated that the spring cocking 163 may be replaced with a ring of convex spring steel, or that the convex spring steel may be axially interchanged with the impulse relief 147, with the impulse relief 147 being disposed on the anti-rotation ring 162, or that the impulse relief may be directly replaced by the tail end of the rivet 158 on the anti-rotation ring 162.

Fig. 38 shows a variation of the embodiment of fig. 36. The change of this embodiment from the embodiment of fig. 36 is that the rotation stop ring 162 is divided into two rotation stop rings 162 and an unlocking ring 173, and the stored energy spring 252 is installed between the two rings, and when the rotation stop ring 162 is in the standby position, the pin top surface of the rotation stop pin 160 is required to be close to or flush with the stopper ring reference end surface 128, and when the rotation stop ring 162 is in the rotation stop position, the top of the unlocking protrusion 149 is required to be flush with the separation reference end surface 58, that is, flush with the non-fitting end surface of the separation ring. The unlocking ring 173 connects six semicircular unlocking pins 149 into a rigid body, and a semicircular cone 169 is arranged in the middle of each locking pin 149. The rotation stop ring 162 rigidly connects the four rotation stop pins 160 together, and the annular base body thereof has a conical outer circular surface, which is circumferentially provided with six semicircular notches 262 correspondingly, and is located outside the relative circumferential rotation interval between the rotation stop pins 160 and the release pins 149. The rotation stopping ring 162 axially passes over the half cone frustum of the six half locking pins 149 of the unlocking ring 173 by means of the six half circular notches 262, then relatively rotates for a certain angle, and the conical surfaces of the two sides are mutually pressed by the energy storage spring 252. The other description is completely the same as that of FIG. 36. Advantageously, the separating ring 120 is not pushed up axially during the forced rotation stop, but the disadvantage is that the blocking ring 70 may be stopped before the direction lock is released, and the separating teeth may slip.

The direct addition of the axial blocker ring anti-rotation mechanism to the embodiment of fig. 32 results in a bi-directional overrunning clutch as shown in fig. 39 that can be successfully reversed at any time and under any circumstances. The anti-rotation ring 162 is located radially within the operating ring 140, with a return spring 250 in the form of a diaphragm mounted axially between the two rings. The anti-rotation ring 162 is axially blocked by a snap ring 190. The four anti-rotation pins 160 are rigidly integrated with the anti-rotation ring 162, and the pin top height requirement is completely the same as in the embodiment shown in fig. 38. After reversing under the blocking working condition, the reversing success can be ensured only by axially pressing a lower stop ring 162 under the rotating condition. The process is the same as before and is not repeated.

By adding the axial blocker ring anti-rotation mechanism directly to the embodiment of fig. 33, a bi-directional overrunning clutch as shown in fig. 40 can be achieved that can be successfully reversed at any time and under any circumstances. Wherein a return spring 250 formed with a circular hole escaping the detent pin 160 is installed between the detent ring 162 and the first engagement element 50. The four anti-rotation pins 160 are rigidly integrated with the anti-rotation ring 162, and the pin top height requirement is completely the same as in the embodiment of fig. 38. The operation and structure of the reversing control mechanism of this embodiment are completely the same as the embodiment shown in fig. 33, except that the specific components are changed. That is, the three lock pins 150b are rigidly connected to each other by the annular base 71; a wave spring is used as the locking pin spring 156b instead of a spring wire split ring to apply axial pressure to the locking pin 150b and is restrained to the operating ring 140 by a snap ring 190b, see fig. 34 and 40. The rotation stop ring 162 and the operation ring 140 are completely independent from each other and do not affect each other.

This embodiment can also be used as a glider, simply being unidirectional, which is relatively difficult.

Fig. 41 shows eleven embodiments of controllable overrunning clutches, namely motor vehicle one-way gliders. Functionally, it is a simplification of the embodiment shown in fig. 36, i.e. its override in the second direction is only eliminated, i.e. the second sub-locking mechanism is eliminated. It can transmit torque in both directions but can only be controllably overridden in the first direction. In this embodiment, the detent pin 160 and the detent pin 150 are served by different portions of the same axial cylinder formed on the end face of the link ring 170. The link ring 170 combines the separating ring positioning locking mechanism, the stop ring rotation stopping mechanism and the separating ring limiting mechanism into a link mechanism, and forms a state control mechanism together with a positioning control mechanism formed by other components. As shown in fig. 41 (c) and (d), in the space with the height h on the end face of the link ring 170, the revolving cylindrical surface corresponding to the axis of the cylinder is used as a boundary, and after a part of the cylinder located outside is cut off, the part corresponding to the incomplete cylindrical surface is the main body of the rotation stopping pin 160, and the part corresponding to the complete cylindrical surface is the locking pin 150. Where h is greater than the depth of the directional via 154. A circumferential groove 171 is formed on an outer cylindrical surface of the link ring 170. An operating ring 140 in the form of an operating slot cover is slidably fitted between the inner and outer cylindrical surfaces of the slot opening of the operating slot 55 and is axially blocked by a snap ring 190. The operating ring 140 has an "L" shaped cross-section, and a radial through hole for mounting the energy storage spring 252 is formed on the tubular base body, and the energy storage spring 252 may be a spring steel wire or a spring steel plate, etc. During assembly, the energy storage spring 252 is first inserted into the radial through hole of the operating ring 140 from the outside to the inside (the insertion should be tight) and then reaches the circumferential groove 171 of the linking ring 170, and the two rings are elastically linked in the axial direction. The two rings, the return spring 250 and the snap ring 190 are then sequentially positioned to complete the installation of the entire state control mechanism. Wherein the return spring 250 is axially between the operating ring 140 and the first engagement element 50.

This effect must be achieved after installation, i.e., naturally, the locking pins 150 and the rotation stop pins 160 should be located in both the direction through holes 154 and the direction pin holes 152, circumferentially locking the separating ring 120; at the instant the locking pin 150 moves out of the directional through hole 154 and completely sinks into the directional pin hole 152, the pin top face of the locking pin 150 or the anti-rotation pin 160 should not pass over the blocking reference end face 128 on the split ring 120, and the link ring 170 should not axially interfere with the first engagement element 50 when it starts to pass over this end face. In the circumferential direction, the rotation stop pin 160 and the annular portion of the directional through hole 154 constitute a separation ring stopper mechanism having a degree of freedom θ in the circumferential direction _d The circumferential degree of freedom theta of the force transmission embedding mechanism is realized without being influenced by small amount _t The degree of freedom is not so large that the release ring starts to have the ability to completely prevent the clutch from being axially fitted, and the space of freedom is completely located on the side of the lock position in the direction beyond the release direction, see fig. 41 (b).

As previously mentioned, to ensure that the secondary blocking tooth 102 rides over the projection 82 in the middle of the blocking tooth, the angle of rise β of the side of the projection on the same side as the blocking land 76 should satisfy the inequality: beta is more than or equal to | delta | and less than 90 degrees to phi, the side face and the blocking working face 76 are preferably coplanar, namely, beta = lambda, and all blocking teeth are preferably uniformly distributed in the circumferential direction. In addition, since the reverse override function is eliminated, the separable fitting mechanism and the block fitting mechanism may be of a bidirectional type in the embodiment of fig. 24 or of a unidirectional type in the embodiment of fig. 1.

The mechanism of the working process of this embodiment is substantially the same as that of the embodiment shown in fig. 36. Only the reversing process is omitted. The glider shown in figure 41 (a) is in the normal torque transfer position and can now enter the normal overrunning disengagement state. After the sliding state is entered, the sliding device can be immediately embedded and reset to start transmitting torque due to reverse overrunning as long as the motor vehicle accelerates. If the overrunning state needs to be ended manually and forcibly, the one-way slider can immediately enter the working condition of the jaw coupling only by a simple operation of axially pressing the operating ring 140 to the limit by external force and then loosening the operating ring. The process description is as before and is not repeated. If the motor vehicle recovers power driving at the moment, the second force transmission gear ring which is rotated to the normal station returns the synchronous belt of the separating ring 120 to the normal one-way force transmission and separating station through the separating and embedding mechanism, so that the direction locking action of the separating ring is naturally completed, and the next working cycle starts from this.

The embodiment of fig. 42 is the result of applying the pin and hole configuration of the pin and hole locking and detent mechanism of the embodiment of fig. 41 directly to the embodiment of fig. 35 with appropriate adjustment of the other mechanisms. To obtain a positive two-way overrunning clutch or two-way glider, the link ring of this embodiment is divided into two parts 170a and 170b, for the first and second directions, respectively. Further, the positional relationship between the detent pin 160a and the lock pin 150a is reversed in the radial direction with respect to the positional relationship between the detent pin 160b and the lock pin 150 b. Correspondingly, the two sets of directional through holes 154a and 154b on the first engaging element 50 have a layout form in which the radial directions are mutually reversed, see fig. 42 (b). The annular base of the link ring 170b has three outer radial protrusions 254b, the annular base of the link ring 170a has three inner radial protrusions 254a, and the outer circumferential surface thereof is correspondingly formed with three semicircular notches 262 for allowing the rotation stopping pin 160b to pass axially when assembled. The radial protrusions 254a and 254b of the interlocking rings 170a and 170b are fitted into the three hole-type circumferential guide grooves 176a on the outer cylindrical cam surface 266a and the three circumferential guide grooves 176b on the inner cylindrical cam surface 266b of the operating ring 140, respectively, and the axial movements of the two rings are not affected by each other. The circumferential guide groove 176b of the outer ring body may be machined by penetrating the circumferential guide groove 176b of the inner ring body in the radial direction, or may be machined directly into a radial hole-type guide groove at the outer diameter, as shown in fig. 42 (c). The equal height surfaces of the rotation stop pins 160a and 160b at the time of the axial displacement of the both square pillar top surfaces are not higher but are preferably flush with the separation reference end surface 58. Other dimensional features are as described for the embodiment of fig. 41. In addition, the return spring 250 in this example is an annular spring plate that is secured to the outer end surface of the operating ring 140 by a clamp ring and screw assembly 258. The radially outer edges of the return springs 250 are movably embedded in the circumferential inner grooves of the six annular positioning seats 260. The socket head cap screw fixes the positioning seat 260 on the end surface of the first engaging element 50 corresponding to the threaded hole 248 through the fabrication hole of the return spring 250.

The return spring 250 in the present embodiment is equivalent to the sum of both the return spring 250 and the energy storage spring 252 in the embodiment of fig. 41. The device has the functions of axial avoidance, energy storage, positioning and resetting. Reversing lock is achieved by rotating the operating ring 140 circumferentially relative to the first engagement element 50, and at any time in either direction, axial compression of the operating ring 140 stops the rotation of the blocker ring 70, ensuring successful reversing or end of coasting. Upon removal of the external force, the operating ring 140 is immediately returned to its normal position as determined by the circumferential positioning.

Figure 43 shows a further axially controlled one-way slider modified from that of figure 41. The change is mainly that the packaging form is changed into the form of the embodiment of fig. 37; and the operating ring 140 is located radially inside the link ring 170, and is axially sleeved in the inner hole of the link ring by the rotation stopping pin 160 until the corresponding inner and outer conical surfaces of the two parts are in contact with each other. Accordingly, the outer conical surface edge of the manipulation ring 140 is formed with three semicircular notches 262 to avoid the rotation preventing pin 160. The other end of the wave energy storage spring 252 is sleeved on the operation ring 140, the linkage ring 170 is pressed on the outer conical surface of the operation ring 140, the snap ring 190 is embedded in the snap ring groove on the operation ring 140, and the wave energy storage spring 252 is supported and connected into a whole. The return spring 250 is still mounted between the operating ring 140 and the end face of the first engagement element 50. As described above, since the radial positional relationship of the detent pin 150 and the detent pin 160 on the interlocking ring is opposite to that shown in fig. 41 (d), the radial layout of the direction through holes 154 on the first engaging element 50 thereof is also opposite to that shown in fig. 41 (b), see fig. 43 (b).

The one-way glider shown in figure 44 is actually the result of the embodiment of figure 38 with the control ring 140 removed in its entirety. Overrun and glide in only one direction. In this embodiment, the unlocking ring 173, the return spring 250, and the energy storage spring 252 form the operating mechanism. As shown in fig. 44 (b), (c), the arrangement of the upper half-truncated cone 169 of the rotation-preventing pin 160 on the unlocking ring 173 is such that it does not overlap with a member radially outward of the rotation-preventing pin 160, such as a return spring 250, as in the embodiment of fig. 38.

If the link ring 170a in the embodiment of figure 42 is eliminated and the three outer radial projections 254 of the link ring 170 are replaced by three energy storing springs 252 in the form of straight spring wires, the steering ring 140 is simplified and axially captured by the snap ring 190 to provide the simplest circumferentially controlled one-way glider as shown in figure 45. The coasting state can be terminated forcibly by rotating the operating ring 140 relative to the first engagement element, for example by braking it. The inner diameter end of the energy storage spring 252 is inserted into a radial hole on the annular base body of the link ring 170, and the outer diameter end thereof is movably inserted into a radial cam hole arranged in the circumferential direction on the annular base body of the operating ring 140, and the circumferential direction of the through hole is similar to the circumferential guide groove 176b in fig. 42 (c). The relevant parameter requirements are the same as for the fig. 42 embodiment.

Fig. 46 shows a simple modification to the embodiment shown in fig. 44. Namely, the axial control type is changed into the circumferential control type, and the automatic circumferential resetting function is provided. The radial and axial relationship between the unlocking ring 173 and the rotation stop ring 162 is unchanged, but the outer end faces of the annular base bodies of the unlocking ring and the rotation stop ring are axially flush, and the operating ring 140 is additionally arranged between the outer end face and the snap ring 190. As shown in fig. 46 (b) and (c), three sets of end cylindrical cam protrusions 144a and 144b are circumferentially distributed on one end surface of the operating ring 140, and a guide slope surface 143 and a protrusion 142 for limiting a circumferential rotation angle are respectively formed thereon. The three sets of protrusions are normally located in corresponding circumferential notches in the radially outer edges of both the unlocking ring 173 and the anti-rotation ring 162. When relative rotation occurs, the corresponding protrusions apply axial pressure to the corresponding circular rings in sequence, the direction locking is released, and then the rotation stopping stop ring 70 stops to finally forcibly stop the sliding working condition. The return spring 250 in this example is three radial spring wires, the inner radial ends of which are clamped in three circumferentially spaced radial slots 268 in the respective end face of the first sleeve 187 and at the same time in three loose notches 272 in the end face of the inner ring of the actuating ring 140, which are axially blocked by a snap ring 190. The outer diameter end of the return spring 250 is movably inserted in three radial holes 270 on the outer ring of the operating ring 140. When the operating ring 140 rotates relative to the first bushing 187, the return spring 250 deforms and produces a circumferential reaction torque on the operating ring 140. When the external force is removed, the operating ring 140 can return to the normal position under the action of the return spring 250, and the slider can also return to the normal state immediately.

It will be readily appreciated that the one-way and two-way controllable runners are applicable to all motor vehicles, and all other transmission areas where override functions need to be controlled. If the two gliders are arranged on a transmission shaft system with changeable torque direction, the forcing mechanism of the one-way glider and the reversing mechanism of the two-way glider are linked with the torque direction changing mechanism. If the two kinds of gliders are used for a transmission shaft system with fixed torque direction, only the forced control mechanisms of the two kinds of gliders need to be linked with a motor vehicle brake operating mechanism or a single operating mechanism or the two kinds of gliders are connected in parallel, and the use is very simple. Obviously, the one-way controllable glider is superior to the two-way glider, the overtaking function can be cancelled by the linkage of the reversing operation mechanism when reversing, and the one-way controllable glider is simpler to be used in front of motorcycles, electric mopeds and gearboxes without reversing functions. The glider has the advantages of remarkable performance, service life, reliability, structure, process, use and maintenance compared with various gliders in the prior art.

The release ring positioning and locking mechanism for fixing the release ring 120 at two different specific circumferential positions with respect to the first engagement element 50 may be a cylindrical cam type radial pin groove positioning mechanism, such as the bidirectional overrunning clutch shown in fig. 47 and 48. Wherein, the radial guide projection 254 at the top end of the locking pin 150 with a semi-cylindrical section and the spiral guide groove 153 on the outer circular surface of the separating ring 120 form a cylindrical cam type radial pin slot positioning mechanism. When the guide protrusions 254 are located at the parallel sections at the two axial ends of the spiral guide groove 153, the clutch is located at the working position of either forward or reverse direction, and when the guide protrusions 254 are located at the circumferential position change section in the middle of the spiral guide groove 153, the clutch is located at the non-locking working position (unless the two are self-locked by friction). It is apparent that the spring 252 is not essential and the spiral guide groove 153 in fig. 47 (b) is not essential for restraining the guide projection 254 at both axial ends, and may be entirely in the longitudinal sectional shape of a bottle such as a bottle having a small belly, for example, when used as a one-way slider. The cylindrical cam type radial pin slot positioning mechanism may be in the form of a cylindrical screw, a screw mechanism, or the like.

The split ring detent lock mechanism can also be a geneva wheel (maltese) mechanism as shown in fig. 49. Wherein a revolving cylindrical section 282 of a cylindrical dial 280 is rotatably received in the axial through bore 154 of the first engagement member 50 and a cylindrical dial pin 278 on an end face thereof is slidably received in the radial guide slot 155 on the non-toothed end face of the separating ring 120. As shown in fig. 49 (b) and (c), the other end of the cylindrical dial 280 is formed with gear teeth 206 having an outer diameter larger than the rotating cylindrical section 282, and the gear teeth 206 mesh with the gear teeth on the operating ring 140 to transmit the rotating power to the cylindrical dial 280. Left and right rotation of the cylindrical dial 280 will, through the mating relationship of the cylindrical dial 278 with the radial guide 155, cause the disengagement ring 120 to rotate through an angle of ± e/2 with respect to the axis of rotation of the cylindrical dial 280, i.e., to sequentially rest at two opposing positions spaced at a circumferential angle of e with respect to the first engagement member 50, thereby effecting reversal of direction. The friction between the cylindrical pin 278 and the side of the radial guide groove 155 at the two stop positions is self-locking, or the pin is abutted against the top of the radial guide groove 155, so that the stop positions can be stabilized. The steering ring 140 may be simply positioned by a ball spring mechanism (not shown). It is envisioned that standard geneva mechanisms, cam combinations, etc. can be used as the reversing mechanism in this embodiment, and bi-directional or unidirectional over-running positioning is readily achieved.

Obviously, with reference to the previous examples, it is easy to modify the above three examples into more or simpler implementations of forced two-way overrunning, two-way sliding and one-way sliding. And will not be described in detail herein.

The foregoing description and drawings are given for the purpose of illustrating the invention only in limited embodiments thereof with a certain degree of particularity, it should be understood that the embodiments described are illustrative and that various changes, equivalents, substitutions and alterations in the structure or arrangement of parts may be made without departing from the spirit and scope of the inventive concept.

Claims (10)

1. A press-fit type jaw one-way overrunning clutch comprises a first joint element, a second joint element, a stop ring, an auxiliary limiting ring, a spring and a spring seat, wherein the first joint element, the second joint element, the stop ring, the auxiliary limiting ring, the spring and the spring seat are all arranged on the basis of the same rotating axis; the first jointing element and the second jointing element are axially oppositely embedded to form a working embedding mechanism which is a force transmission embedding mechanism and a separation embedding mechanism; the method is characterized in that:

(a) The blocking and embedding mechanism is used for preventing the working embedding mechanism from being embedded in an overrunning separation state and is formed by axially embedding a blocking ring and an auxiliary blocking ring, and radial blocking teeth with axial blocking effects are arranged on the two rings; the minimum blocking height of the blocking embedding mechanism is larger than the initial separation height of the working embedding mechanism in two rotation directions and smaller than the full-tooth embedding depth of the working embedding mechanism;

(b) The limiting embedding mechanism is arranged for limiting the circumferential relative position of the blocking ring in the blocking embedding mechanism and consists of the blocking ring and an auxiliary limiting ring, the auxiliary limiting ring and the auxiliary main ring form 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 of the limiting embedding mechanism is larger than the entrance margin of the blocking embedding mechanism.

2. The laminated jaw one-way overrunning clutch of claim 1 further comprising: the blocking embedding mechanism is axially positioned in the working embedding mechanism and radially positioned in or out of the working embedding mechanism; the auxiliary blocking ring is integrated with an auxiliary ring which is any one of the joint elements forming the working embedding mechanism; the blocking ring is supported in a one-way mode by a blocking reference end face of the blocking reference ring, and a sliding end face of the blocking ring and the blocking reference end face form a circumferential free sliding friction pair; the stopper reference ring is a side engagement element of the operation fitting mechanism which is axially opposed to the auxiliary stopper ring.

3. The laminated jaw one-way overrunning clutch of claim 1 further comprising:

(a) The auxiliary limiting ring and the auxiliary blocking ring are the same ring, the limiting embedding mechanism and the blocking embedding mechanism are overlapped to form a control embedding mechanism, in the control embedding mechanism, the blocking teeth are also limiting teeth, and the auxiliary blocking teeth are also auxiliary limiting teeth;

(b) In the control embedding mechanism, the blocking working faces of the tooth crests of the blocking tooth and the auxiliary blocking tooth are spiral faces with the lead angles not larger than rho, and a limiting bulge is formed in the middle of at least one tooth crest, wherein 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 sides to be successfully self-locked in the blocking working condition;

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

4. The compression-type jaw one-way overrunning clutch according to claim 2, wherein: the side face of the limiting bulge in the control embedding mechanism, which is on the same side with the blocking working face, is a spiral face with a lead angle beta, beta is not less than | delta | and not more than 180 degrees, wherein | delta | is the absolute value of the minimum lead angle of the blocking working face, which can ensure that a static friction pair formed by the axial contact of the blocking working face of the blocking tooth and the blocking working face of the auxiliary blocking tooth in the blocking working condition is successfully self-locked.

5. A controllable press-fit type jaw overrunning clutch comprises a first joint element, a second joint element, a separating ring, an auxiliary separating ring, a blocking ring, an auxiliary limiting ring, a spring and a spring seat, which are all arranged on the basis of the same rotating axis, wherein the first joint element and the second joint element are axially oppositely embedded to form a force transmission embedding mechanism capable of transmitting torque in two directions; the method is characterized in that:

(a) The separating and embedding mechanism is formed by axially embedding a separating ring and an auxiliary separating ring, separating teeth are arranged on the two rings, and the separating teeth are radial teeth with axial separating capacity;

(b) The blocking and embedding mechanism is used for preventing the separation and embedding mechanism from being embedded in an overrunning separation state and is formed by axially embedding a blocking ring and an auxiliary blocking ring, and radial blocking teeth with axial blocking effects are arranged 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, larger than the initial separation height of the separation embedding mechanism in two relative rotation directions and smaller than the full-tooth embedding depth of the separation embedding mechanism;

(c) The limiting embedding mechanism is arranged for limiting the circumferential relative position of the blocking ring in the blocking embedding mechanism and consists of the blocking ring and an auxiliary limiting ring, the auxiliary limiting ring and the auxiliary main ring form 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 of the limiting embedding mechanism is larger than the entrance margin of the blocking embedding mechanism;

(d) Circumferential degree of freedom theta of force transmission embedding mechanism _t The force-transmitting engaging means is designed in such a way that, when the disengaging and engaging means is moved beyond disengagement in both operating directions of rotation, no contact or collision occurs between the components of the force-transmitting engaging means;

(e) The circumferential position of the separating ring relative to the separating reference ring is controlled by a separating ring positioning and locking mechanism, the separating ring can be fixed at a specific circumferential position relative to the separating reference ring by the mechanism, when the mechanism is locked, the overrunning clutch can only transmit torque and separating overrunning in one direction, and when the mechanism is not locked, the overrunning clutch can not separate overrunning in two directions, but can transmit torque.

6. The controllable, press-fit dog overrunning clutch according to claim 5, 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 blocking ring is supported in a one-way mode by a blocking reference end face of the blocking reference ring, and a sliding end face of the blocking ring and the blocking reference end face form a circumferential free sliding friction pair; the blocking reference ring is a member axially opposed to the owner ring of the auxiliary blocking ring in the separating and fitting mechanism or the force-transmitting and fitting mechanism.

7. The controllable, press-fit, dog overrunning clutch of claim 5, further comprising:

(a) The auxiliary limiting ring and the auxiliary blocking ring are the same ring, the limiting embedding mechanism and the blocking embedding mechanism are overlapped to form a control embedding mechanism, in the control embedding mechanism, the blocking teeth are also limiting teeth, and the auxiliary blocking teeth are also auxiliary limiting teeth;

(b) In the control embedding mechanism, the blocking working surfaces of the blocking tooth and the auxiliary blocking tooth are helical surfaces with the rising angle not larger than rho, and a limiting bulge is formed in the middle of at least one tooth top surface;

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

8. The controllable, press-fit, dog overrunning clutch of claim 7, further comprising:

(a) The first engagement element is axially fixed;

(b) The auxiliary stop ring and the auxiliary limit ring both use the second joint element as the auxiliary main ring, the stop reference ring is a separation ring, and the separation reference ring is a first joint element;

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

(d) 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 | < 180 ℃, and related parameters are defined as above;

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

(f) The entrance margin K of the blocking embedding mechanism conforms to the inequality: k > theta _c +θ _f + γ + η, where γ = max (γ) ₁ ，γ ₂ ) The relevant parameters are defined as follows:

θ _c : the separation ring separates the circumferential included angle corresponding to the tooth top surface,

θ _f (ii) a The auxiliary separating ring separates the circumferential included angle corresponding to the tooth top surface,

γ ₁ : a separation angle of the separation and engagement mechanism in the first direction,

γ ₂ : a separation angle of the separation and engagement mechanism in the second direction,

eta: the correction amount is caused by the fact that the lead angle, the tooth root of the force transmission tooth are contracted, the circumferential clearance of the separating and embedding mechanism and the axial separation distance of the force transmission embedding mechanism are larger than the full-tooth embedding depth of the force transmission embedding mechanism;

(g) The separating ring positioning and locking mechanism is an axial pin hole type positioning mechanism which can respectively fix the separating ring at two different specific circumferential positions relative to the first engaging element, when the separating ring positioning and locking mechanism is fixed at the first relative position, the overrunning clutch can only transmit torque and separating overrunning in a first direction, and when the separating ring positioning and locking mechanism is fixed at the second relative position, the overrunning clutch can only transmit torque and separating overrunning in a second direction, and the second direction is opposite to the first direction; the mechanism consists of two sets of axial pin holes on the toothless end surface of the separating ring, two sets of axial through holes on the separating reference end surface of the first joint element and two sets of locking pins, and the positions of all the axial holes are determined with the effect that when the first set of locking pins are simultaneously embedded into the first set of axial pin holes on the separating ring and the first joint element, the separating ring is circumferentially fixed on a first relative position of the first joint element, and when the second set of locking pins are simultaneously embedded into the second set of axial pin holes on the separating ring and the first joint element, the separating ring is circumferentially fixed on a second relative position of the first joint element;

(h) And the separating ring positioning and locking mechanism is controlled by the positioning control mechanism.

9. The controllable, press-fit, dog overrunning clutch of claim 8, further comprising:

(a) The blocking ring rotation stopping mechanism is an embedded limiting mechanism which can forcibly limit the blocking ring at a specific circumferential position relative to the separating ring, when the mechanism is embedded, the blocking ring loses axial blocking capability, the overrunning clutch can be axially embedded and reset, and when the mechanism is not embedded, the blocking ring has axial blocking capability;

(b) The circumferential limit position of the separating ring relative to the first joint element is limited by the separating ring limiting mechanism, the limiting mechanism is arranged between the separating ring and the first joint element, the circumferential freedom degree of the limiting mechanism is not less than the circumferential included angle between the first relative position and the second relative position and is not so large as to enable the separating ring to start to have the capability of completely preventing the clutch from axially embedding, and the separating ring positioning and locking mechanism can fully realize the function in the rotating range corresponding to the circumferential freedom degree;

(c) The positioning control mechanism is a mechanism for controlling the axial positions of two groups of locking pins of the separating ring positioning locking mechanism, and simultaneously has the function of controlling the stop mechanism of the stop ring;

(d) The lead angles beta of two side surfaces of the limiting bulge in the control embedding mechanism meet the inequality: beta is more than or equal to | delta | and less than 90 degrees to phi, wherein phi is a friction angle of a friction pair formed by the two sides forming the control embedding mechanism in friction contact on the side surface of the limit protrusion, and | delta | is defined as above.

10. The controllable, press-fit, dog overrunning clutch of claim 7, further comprising:

(a) The first engagement element is axially fixed;

(b) The auxiliary stop ring and the auxiliary limit ring both use the second joint element as the auxiliary main ring, the stop reference ring is a separation ring, and the separation reference ring is a first joint element;

(c) The initial separation height of the separation embedding mechanism in at least one relative rotation direction is zero;

(d) The side surface of the limiting bulge in the control embedding mechanism, which is on the same side with the blocking working surface, is a spiral surface with a rising angle beta, beta is more than or equal to | delta | and less than 90-phi, and the parameters are defined as above;

(e) The state control mechanism is formed by combining the separating ring positioning and locking mechanism, the separating ring limiting mechanism and the stop ring rotation stopping mechanism; wherein the content of the first and second substances,

the separating ring positioning and locking mechanism is a pin hole type positioning mechanism consisting of an axial pin hole on a toothless end surface of the separating ring, an axial through hole on a separating reference end surface of the first joint element and a locking pin, and the positions of the two corresponding axial holes are determined by the effect that when the locking pin is simultaneously embedded into the two axial holes to fix the separating ring at a specific circumferential position relative to the first joint element, the overrunning clutch can only transmit torque and separate overrunning in one direction;

the separating ring limiting mechanism is a mechanism which can limit the circumferential relative position between the separating ring and the first jointing element, the limiting mechanism is arranged between the separating ring and the first jointing element, the circumferential freedom degree of the limiting mechanism is not small enough to influence the force transmission embedding mechanism to realize the circumferential freedom degree theta _t The degree of (a) is not so great as to enable the separating ring to start to have the capability of completely preventing the clutch from being embedded in the axial direction, and the separating ring positioning and locking mechanism can fully realize the function in the rotating interval corresponding to the circumferential direction self-degree;

the stop ring rotation stopping mechanism is an embedded limiting mechanism which can limit the stop ring to a specific circumferential position relative to the separating ring in a forced mode, when the stop ring rotation stopping mechanism is embedded, the stop ring loses axial stopping capacity, the overrunning clutch can be embedded and reset in the axial direction, and when the stop ring rotation stopping mechanism is not embedded, the stop ring has axial stopping capacity.

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