WO2009036595A1 - Mécanisme de maintien de séparation pour embrayage à contrôle automatique axial de type à contrainte par ressort - Google Patents

Mécanisme de maintien de séparation pour embrayage à contrôle automatique axial de type à contrainte par ressort Download PDF

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Publication number
WO2009036595A1
WO2009036595A1 PCT/CN2007/002752 CN2007002752W WO2009036595A1 WO 2009036595 A1 WO2009036595 A1 WO 2009036595A1 CN 2007002752 W CN2007002752 W CN 2007002752W WO 2009036595 A1 WO2009036595 A1 WO 2009036595A1
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WO
WIPO (PCT)
Prior art keywords
blocking
ring
axial
fitting
auxiliary
Prior art date
Application number
PCT/CN2007/002752
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English (en)
Chinese (zh)
Inventor
Tao Hong
Original Assignee
Tao Hong
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tao Hong filed Critical Tao Hong
Priority to PCT/CN2007/002752 priority Critical patent/WO2009036595A1/fr
Publication of WO2009036595A1 publication Critical patent/WO2009036595A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/06—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with intermediate balls or rollers
    • F16D7/08—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with intermediate balls or rollers moving axially between engagement and disengagement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/042—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement
    • F16D7/044—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth

Definitions

  • the invention relates to an axial compression type self-control clutch in the field of mechanical transmission, in particular to a holding mechanism for maintaining a separation state of a spring-pressure self-control clutch after axial separation, which belongs to the field of mechanical transmission.
  • Prior art axial spring compression type self-controlled clutches except for the jaw-mounted self-locking differential, the jaw-mounted overrunning clutch and the safety clutch, and the spring steel ball type safety clutch do not have the state retention function after axial separation. .
  • the relative rotation of the two will cause impact, collision, noise and excessive wear of the face teeth.
  • the jaw-mounted safety clutch with large axial elastic engagement force may even be severely broken.
  • the extent of the face teeth Therefore, in both the theoretical and engineering circles, the long-term general view in the transmission field is that the axial spring compression type self-controlled clutch is not suitable for the shaft drive with large relative speed or large load inertia of the main and driven joint elements after separation. Part.
  • the working speed of the jaw clutch is generally not more than 315 rpm, the load is not more than 400N*m.
  • the maximum working speed is generally not exceeded at a load level of 1,000 ⁇ . 400 rpm. Therefore, their application is greatly limited, so that their transferable torque is large, the structure is simple, and there is no slip and heat generation after joining, which is difficult to obtain due use.
  • the technology of the separation and retention mechanism in the jaw-type self-locking differential due to the special layout of the mechanism, the mechanism imposes too strict requirements on the compression spring stiffness, spring length and assembly. As well as being affected by the inability to adjust the spring pressure and not compensate for the limiting factors such as wear, the technology has not been extended to other related clutches to date. Summary of the invention
  • the object of the present invention is to provide a separation state of all axial spring compression type self-control clutches which is simple in structure, reliable in operation, and is not affected by the stability of the compression spring parameters, adapts to different axial engagement forces, and assembles a single cylinder.
  • the holding mechanism that is, the blocking mechanism, eliminates the harmful impact of the clutch after separation, and eliminates or substantially eliminates the collision phenomenon therein.
  • Owner ring A rotating member attached to an attached blocking ring or an attached retaining ring.
  • Reference ring A rotating member that acts as a reference object for the blocking ring to be relatively stationary in a fitting working state; an end face whose axial direction directly faces the blocking ring is referred to as a reference end face, and a cylindrical surface directly facing the blocking ring in the radial direction is called For the reference cylindrical surface, the two are collectively referred to as the reference plane.
  • Blocking the working surface After blocking the axial separation of the fitting mechanism, the radial direction of both sides of the ring that constitutes the mechanism
  • the top surface portion of the tooth used for the top contact between the teeth is represented by ⁇ .
  • the blocking teeth of both sides of the blocking engagement mechanism are in top-to-top contact, preventing the axial engagement or fitting of the other axially engaging or fitting mechanisms from reengaging or fitting.
  • the blocking ring is formed on the one hand by the sliding end surface or the cylindrical surface and the reference end surface of the reference ring or the reference cylindrical surface to form a sliding friction pair (for the double clutch, there is no end sliding friction Case), on the other hand, the blocking working surface of the blocking tooth is in axial contact with the blocking working surface of the auxiliary blocking tooth to form a static friction pair, and when the static friction pair is used to define the circumferential position of the blocking ring relative to the auxiliary blocking ring,
  • the static friction pair must be self-locking, wherein the minimum angle of lift that can ensure that the static friction pair is self-locking is defined as ⁇ , and the maximum angle of elevation is defined as ⁇ .
  • Limiting face A surface that is limited to the circumferential relative position of the blocking ring.
  • Minimum barrier height The transition from a non-blocking condition (ie, a stable fitted state) to a blocking condition that blocks the minimum axial distance that the mating mechanism must separate.
  • Maximum limit fitting depth Ensure that the circumferential restraint of the limit fitting mechanism is present, blocking the maximum distance that the fitting mechanism can be separated in the axial direction.
  • the depth is the axial direction between the highest points in the upper boundary of the limiting working faces of the fitting sides in the fully fitted state.
  • Distance when the components of the limit fitting mechanism are not axially moved together with the blocking fitting mechanism, the depth is infinite.
  • Full tooth joint depth The axis between the first joint element and the second joint element when the axial joint or the component of the fitting mechanism is rotated one turn relative to each other while maintaining the axial contact regardless of the initial separation height. The magnitude of the change in distance. It can also be referred to as full tooth fitting depth.
  • the entrance margin of the blocking fitting mechanism ⁇ When the influence of other fitting mechanisms and the circumferential freedom of the blocking ring are not considered, from the minimum blocking height, both sides of the ring gear constituting the blocking fitting mechanism do not affect the axial embedding of the mechanism The maximum circumferential angle that can be continuously offset from each other under the premise of the combination.
  • Crest blocking angle ⁇ Under the action of the pressing spring, the self-control clutch in the axially separated state avoids the blocking of the internal related top surface and achieves the axial engagement without considering the influence of the blocking fitting mechanism. , the maximum circumferential angle at which the two sides must be continuously offset from each other.
  • Separation angle Y a critical state between the engagement state of the working engagement mechanism and the engagement state and the stable separation state, which belongs to a minimum circumferential angle of relative rotation between the two engagement elements; in the present invention, a fitting mechanism When both sides of the composition are axially supported by the two components of the other fitting mechanism, the former fitting mechanism is said to be axially located inside the latter fitting mechanism, and vice versa.
  • the "engagement" and “fitting” of the present invention have a clear distinction only when the axial self-control clutch is specifically a spring steel ball safety clutch, and the axial self-control clutch is specifically When there are other clutches with radial face gears, there is no substantial difference.
  • a separate holding mechanism for an axial self-control clutch of the present invention includes a first engaging element, a second engaging element, a spring, and a spring mount, and both are arranged based on the same rotary axis;
  • the first engaging element and the second engaging element form an axially opposite working engagement mechanism.
  • the method comprises: a blocking and fitting mechanism including axial engagement of the working engagement mechanism in a state of preventing separation, wherein the blocking ring and the auxiliary blocking ring are axially fitted, A radial type blocking tooth having an axial blocking effect is disposed on both rings; the minimum blocking height of the blocking fitting mechanism is greater than the initial separation height of the working engagement mechanism in two rotational directions, less than the working engagement The full tooth engagement depth of the mechanism; (b) includes restrictions on the circumferential relative position of the blocking ring in the blocking engagement mechanism
  • the limiting fitting mechanism is composed of a blocking ring and an auxiliary limiting ring; the auxiliary limiting ring is integrated with the main ring, and the auxiliary limiting ring and the auxiliary blocking ring are circumferentially fixed; the axis of the blocking fitting mechanism When the separation distance is greater than the minimum blocking height, the circumferential degree of freedom of the limiting fitting mechanism is greater
  • the blocking and fitting mechanism is axially located within the working engagement mechanism; the auxiliary blocking ring is integral with the main ring thereof, and the main ring is one of the engaging elements of the working engagement mechanism, and the blocking ring is referenced by the reference ring
  • the unidirectional support of the end surface, the sliding end surface and the reference end surface constitute a circumferential free sliding friction pair; the reference ring is a coupling element opposite to the main ring of the auxiliary blocking ring.
  • the disengagement and holding mechanism of the double-connected axial self-control clutch of the present invention is characterized in that: the first engaging member has two engaging end faces facing each other and being circumferentially fixed to the first rotating shaft, and has two a second engaging element that axially slidably axially displaces with the second rotating shaft, each of the two elements being axially engaged with a first engaging element, respectively forming two functions of transmitting torque and overload separation on the same axis and stabilizing
  • the working engagement mechanism has the same working condition, and the stable working condition is an axial engagement force transmission state or an axial separation overload state; when the first rotation shaft rotates synchronously with the second rotation shaft, the two working engagement mechanisms are all engaged, and each composition The axial spacing between the two sides is minimized.
  • the two working engagement mechanisms are separated, and the respective groups are respectively The axial distance between the two sides is maximized; at least one spring acts on the non-engaging end faces of the two second engaging elements, respectively, to provide an axial engaging force for the two i-joining mechanisms; at least one spring bearing to Finally forming a direct or indirect axial restraint and support of the spring; two blocking engagement mechanisms arranged to prevent axial engagement of the two working engagement mechanisms in an axially separated overload state, consisting of a blocking ring and two attachments
  • the blocking ring is axially respectively fitted, and all of the constituent members of the two blocking and fitting mechanisms are provided with a radial blocking type tooth having an axial blocking effect; a minimum blocking height of the two blocking and fitting mechanisms
  • the initial separation heights in the two rotational directions respectively greater than the respective corresponding working engagement mechanisms are respectively smaller than the full tooth fitting depths of the respective corresponding working engagement mechanisms; and the circumferential direction of the blocking ring in the blocking engagement mechanism
  • the two blocking rings may be integrally formed in the axial direction, and the respective blocking teeth are respectively formed on the same annular base body in such a manner that the tooth tips are opposite to each other, and the two auxiliary blocking rings are respectively formed integrally with one of the first members.
  • the blocking teeth of the two blocking rings are respectively formed on the respective independent annular bases in such a manner that the crests face away from each other; the circumferential relative position between the two blocking rings is restricted by the circumferential linkage mechanism, and the mechanism is An axial fitting mechanism between the two that is always in a fitted state; the two auxiliary blocking rings are each formed integrally with a second engaging element.
  • the two double first engaging elements may be integrally formed in a non-joining end face.
  • the initial separation height of the working engagement mechanism in both relative rotational directions should be zero, and the two sides of the tooth top surface of the blocking tooth and the auxiliary blocking tooth are respectively formed with two blocking working surfaces. And the inlet margin of the blocking fitting mechanism is greater than the tip blocking angle of the self-controlled clutch.
  • the auxiliary blocking ring can be attached to the second engaging element, and the auxiliary limiting ring can be attached to the second rotating shaft fixed circumferentially with the second engaging element to directly face One surface of the blocking ring; and a pin-slot radial or axial fitting mechanism is disposed between the two rings.
  • the blocking engagement mechanism In order to make the blocking engagement mechanism work perfectly and reliably, it is preferable to restrain the blocking ring to force it to be relatively stationary on the reference end face or the reference cylindrical surface of the reference ring in the fitted state.
  • the blocking working surface of the tooth top of the blocking tooth and the auxiliary blocking tooth is a spiral surface with an angle of rise not greater than p, and a finite protrusion is formed at least in the middle of one of the top surfaces, objectively blocking
  • the teeth act as limiting teeth and the auxiliary blocking teeth act as auxiliary limiting teeth.
  • the auxiliary limit ring and the auxiliary blocking ring are the same ring, so that the limit fitting mechanism and the blocking fitting mechanism are combined into one control.
  • the fitting mechanism can realize the purpose of stepless change and self-adaptation of the self-limiting position and the axial blocking height of the blocking fitting mechanism, and at the same time, the maximum fitting fitting depth of the limiting fitting machine is larger than the working engagement mechanism Full tooth ⁇ depth.
  • the side surface of the limiting projection in the control fitting mechanism and the side opposite to the blocking working surface can be made into a helix surface with an angle of rise P,
  • ⁇ ⁇ ⁇ 90° - ⁇ if there is a fitting type limit mechanism between the reference ring and the blocking ring that can forcibly limit the blocking ring to a specific circumferential position relative to the reference ring, that is, The blocking ring rotation preventing mechanism, when the mechanism is fitted, the blocking ring loses the axial blocking capability, so that the forced fitting of the clutch can be easily achieved.
  • ⁇ is the friction angle of the friction pair formed by the frictional contact formed on both sides of the limiting projection by the both sides of the control fitting mechanism.
  • the blocking ring rotation preventing mechanism may be composed of an axial or radial through hole on the reference end surface of the reference ring or the reference cylindrical surface, a corresponding groove or a split ring notch on the corresponding friction surface of the blocking ring, and a rotation stop pin. Pin slot type fitting mechanism.
  • the end face radial teeth on the barrier ring can be formed on either or both of the inner and outer cylindrical faces of the ring body of the barrier ring.
  • the auxiliary blocking ring may be separately fabricated and then combined with the main ring by a welding, direct interference fit or axial pin hole interference fit.
  • the blocking ring and the auxiliary blocking ring attached to the first or second engaging member constitute a blocking fitting mechanism having an axial blocking function, the mechanism being axially located within the working engaging mechanism to block
  • the ring and the auxiliary limiting ring constitute a limit fitting mechanism capable of controlling the blocking relationship of the blocking fitting mechanism, and the two mechanisms form the core of the separating and holding mechanism in a form of being integrated or circumferentially fixed, which is good
  • the object of the invention proposed by the present invention is achieved.
  • auxiliary limiting ring when the auxiliary limiting ring is integrated with the auxiliary blocking ring, the limiting protrusion or the self-locking blocking working surface in the middle of the blocking top is utilized, and the auxiliary limiting ring and the auxiliary blocking ring are only fixed in the circumferential direction.
  • Blocking the separately formed limit working face that is, using the control fitting mechanism and the separate radial or axial pin slot type limit fitting mechanism, respectively, or comprehensively utilizing, all well maintain the blocking working condition
  • the lower circumferential relative position of the lowering of the fitting mechanism is such that the blocking relationship is well maintained, the working engagement mechanism in the disengaged state is prevented from engaging and resetting, and the purpose of completely eliminating or substantially eliminating the clutch separation shock or collision is prevented.
  • the mechanism has the characteristics of simple structure, reliable operation, no influence on the stability of the spring parameters of the working joint mechanism, adaptation to different axial joint forces, and assembly of the single.
  • the present invention is relative to the prior art separation and retention mechanism in terms of the working mechanism and reliability of the separation barrier and the fitting reset, the process requirements of the mechanism assembly, the adaptability of the mechanism to the fitting spring, the mechanical working life, and the applicable field and scope. Has a very significant or unparalleled advantage.
  • FIG. 1 is an axial sectional view showing a two-way safety clutch according to a first embodiment of the present invention.
  • Figure 2 is a schematic view of the second engaging element of Figure 1, (a) is an axial half-sectional view of the right side view of (b), (b) is a front view, (c) is an enlarged (b) part of the T direction Schematic diagram of the radial projection of the tooth profile.
  • Figure 3 is a schematic view of the barrier ring of Figure 1, (a) is a front view, (b) is a left view, and (c) is an enlarged schematic view of a partial radial projection in the T direction in (a).
  • FIG. 4 is a partial development view of the radial projection of the respective outer cylindrical surfaces of the respective fitting mechanisms of FIG. 1 in a relative relationship between the tooth profiles, (a) the working engagement mechanism in the fitting state; (b) is a schematic diagram of the tooth profile relationship of the control fitting mechanism corresponding to (a), and (c) is a schematic diagram of the tooth profile relationship of the working engagement mechanism under the blocking condition, (d) is with (c) a schematic diagram of the tooth profile relationship of the corresponding control fitting mechanism, (e) is a schematic diagram of the tooth profile relationship of the one-way control fitting mechanism corresponding to (c), (f) is
  • a partial enlarged view of (a), the arrow represents the direction of relative overload rotation.
  • Figure 5 is a schematic view showing all possible top-to-top contact relationships of the blocking and fitting mechanism having various tooth shapes in the form of a radial projection expansion, in which all the left side corridor lines belong to the blocking ring. , all right contour lines belong to the auxiliary blocking ring;
  • (a) ⁇ (i) shows the various situations of controlling the fitting mechanism, where (a) ⁇ (c) represent three special tooth shapes, (d ) ⁇ (i) represents the total tooth shape of
  • ⁇ ⁇ ⁇ ,, and (e) ⁇ (i) is the special tooth shape in which P ⁇ and coplanar; G) indicates that it is suitable for The tooth profile of the radial type limiting fitting mechanism.
  • Figure 6 is an axial sectional view of a two-way safety clutch in accordance with a second embodiment of the present invention.
  • Figure 7 is an axial cross-sectional view of the safety clutch of the most simplified embodiment of the present invention.
  • Figure 8 is an axial cross-sectional view of a jaw-type self-locking differential according to a fourth embodiment of the present invention.
  • Figure 9 is a schematic view of the second engaging member of Figure 8, (a) is an axial sectional view of the right side view, (b) is a front view, (c) is an enlarged (b) radial projection of a local tooth profile in the T direction Schematic diagram of the expansion.
  • FIG. 10 is a partial development view of the radial projection of the relative relationship of the tooth profiles of the respective groups on the same outer cylindrical surface when the left half of the differential is in the fitting force transmission and the right half is in the separation blocking condition.
  • (a) is a schematic diagram of the tooth profile relationship corresponding to the control fitting mechanism
  • (b) is a schematic diagram of the tooth profile relationship of the corresponding force-fitting mechanism
  • (c) is a schematic diagram of the tooth profile relationship corresponding to the working engagement mechanism
  • (d) is a mosaic Schematic diagram of the parameters of the transmission teeth in the combined state
  • (e) is a schematic diagram of the separation teeth in the fitted state.
  • Figure 11 is an axial sectional view of a spring steel ball safety clutch in accordance with a fifth embodiment of the present invention.
  • Figure 12 is a schematic view of the second element of Figure 11, (a) is an axial half-section of the right side view, and (b) is a front view of a simplified drawing.
  • Figure 13 is an axial sectional view showing a radial limit type one-way overrunning clutch according to a sixth embodiment of the present invention.
  • Figure 14 is a schematic view of the second element of Figure 13, and (a) is an axial half-sectional view of the right side view of (b),
  • Figure 15 is a schematic view of the barrier ring of Figure 13, (a) is a front view, and (b) is an axial half-section of the left side view.
  • Figure 16 is a diagram showing the relative relationship between the tooth profiles of the respective fitting mechanisms of Figure 13 under different operating conditions, A partial development view of the radial projection on the same outer cylindrical surface, (a) is a schematic diagram of the tooth profile relationship of the working engagement mechanism in the fitting state, and (b) is a schematic diagram of the tooth profile relationship corresponding to the (a) corresponding blocking mechanism. (c) is a schematic diagram of the tooth profile relationship of the working engagement mechanism under the blocking condition, (d) is a schematic diagram of the tooth profile relationship of the blocking fitting mechanism corresponding to (c), and (e) is a partially enlarged schematic view of (a), The arrows represent the relative direction of rotation.
  • Figure 17 (a) is an axial sectional view of the double safety clutch of the seventh embodiment of the present invention, (b) is an axial sectional view of the blocking ring in (a), and (c) is an axially symmetrical surface in (b) A simplified cross-sectional view of T-T.
  • Figure 18 is an axial sectional view of a double spring steel ball safety clutch in accordance with an eighth embodiment of the present invention. detailed description
  • first engagement element 50 is the reference ring of the barrier ring 100 and the second engagement element 80 is the owner ring of the accessory barrier ring.
  • the first end member 50 and the second joint member 80 are joined to each other to form a working engagement mechanism, and have a function of bidirectional transmission torque and axial separation.
  • the first shaft and the second shaft are respectively fixed to the first member 50 and the second sleeve 206 by flat keys (not shown).
  • the second engaging member 80 is sleeved on the second sleeve 206 and is circumferentially fixed by the spline teeth.
  • the engaging spring 160 is mounted between the non-fitting end face of the second engaging member 80 and the spring seat 162, and the adjusting nut 164 is threadedly coupled to the outer end side of the second bushing 206, indirectly in axially with the first member 50.
  • the axial support and adjustment of the engagement spring 160 is effected by the spring seat 162.
  • the blocking ring 100 is located radially within the working engagement mechanism and forms a blocking engagement mechanism with the auxiliary blocking ring, the sliding end surface 124 of which abuts against the reference end face 70 of the first engaging element 50.
  • the restraining spring 120 is placed between the blocking ring 100 and the end face of the outer spline teeth of the second bushing 206.
  • the pinned pin linkage ring 180 is disposed on a cylindrical surface outside the non-fitting end face of the first engaging member 50, and is axially spaced to reset the spring 186 and is axially restrained by the snap ring 210.
  • One end of the anti-rotation pin linkage ring 180 is uniformly distributed with three axial rotation preventing pin 182, which are respectively embedded in the three rotation preventing pin mounting through holes 188 of the first engaging element 50.
  • the top surface of the pin is close to but not in contact with the blocking ring 100.
  • the specific structure of the second joining element 80 is as shown in FIG.
  • the second engaging teeth 82 are radial teeth having a trapezoidal cross section, the teeth are evenly distributed on the outer ring side of the fitting end surface thereof, and the auxiliary blocking teeth 142 are evenly distributed on the inner ring side of the fitting end surface thereof.
  • the auxiliary blocking teeth 142 and the second engaging teeth 82 are radially connected integrally, and the tooth top surface 144 is higher than the second engaging tooth top surface 84, and the blocking working surface 148 is a spiral surface with an angle of increase ⁇ ,
  • the auxiliary blocking tooth side 150 and the root surface 146 are completely coplanar with the second engaging tooth side 88 and the root surface 86, respectively, and the auxiliary blocking tooth 142 is thus divided into two parts, corresponding to the The tooth top surface 144 of the second engaging tooth groove and a part of the intermediate tooth body are not stored In.
  • the layout and tooth profile of the mating end faces of the first member 50 are identical to the second engaging members 80 except that there are no subsidiary blocking teeth and the top surface of the first engaging teeth 52 has a certain curvature.
  • a shoulder 128 that receives the spring force is formed in the annular base 112.
  • the blocking teeth 102 of the blocking ring 100 are uniformly distributed on the outer ring side of the annular base 112, and a finite projection 114 is formed in the middle of the tooth tip.
  • Each of the blocking teeth 102 is symmetrically formed with two spiral working faces 108 having an angle of elevation ⁇ , two flank surfaces 110, and two limiting convex spiral sides 118 having an elevation angle of ,,
  • One end having a blocking working surface 108 is a fitting end surface of the blocking ring, and the other end is a circumferential sliding end surface 124 of the blocking ring.
  • the blocking ring stop groove 126 is acted upon by the blocking tooth groove.
  • the circumferential position of the rotation preventing pin mounting through hole 188, the circumferential width, and the circumferential width of the rotation preventing pin 182 are determined, that is, when the rotation preventing pin 182 is fitted into the rotation preventing groove 126, the blocking ring
  • the position of the 100 dwell must cause the blocking engagement mechanism to not successfully block the axial engagement of the working engagement mechanism.
  • the first engaging element 50 and the second engaging element 80 constitute a two-way working engagement mechanism
  • the blocking ring 100 and the auxiliary blocking ring are both a blocking and a limiting mechanism.
  • the degree of freedom is naturally greater than the inlet margin.
  • the rotating pin 182 and its mounting through hole 188 are uniformly distributed three times in the circumferential direction, and the blocking ring 100 and the auxiliary blocking ring each have three uniformly uniform radial teeth, and the auxiliary blocking teeth 142 are just in the circumferential direction.
  • Arrangement across the two second engaging teeth 82, and with the blocking tooth slots acting as the anti-rotation grooves 126, is not necessary, purely for the sake of simplifying the structure and process.
  • the auxiliary blocking ring cannot be integrally formed with its main ring, it can be separately manufactured in advance, and then it can be processed by rigidly combining it with the main ring or by welding or interference fit.
  • the restraining spring 120 and the return spring 186 are both wave springs, but may be any other form of elastomer.
  • the working torque is transmitted to the second engaging element 80 via the first component 50, and then transmitted to the second bushing 206 via the spline to complete the transmission of the torque inside the clutch.
  • the route can also be reversed.
  • the overload is applied in any direction, that is, the transmitted torque generates an axial reaction force on the flank contact surface of the first engaging tooth 52 and the second engaging tooth 82 is greater than the engaging pressure provided by the spring 160, see the figure. 4(a) or 4(f)
  • the second engaging teeth 82 are necessarily axially separated against the elastic pressure, and are withdrawn from the engaged position.
  • the engagement relationship of the entire working engagement mechanism no longer exists, the torque transmission path between the two elements is disconnected, and the mechanism enters the overload separation operation state.
  • the auxiliary blocking tooth blocking working surface 148 When the axial separation distance of the mechanism reaches the first synchronization, the auxiliary blocking tooth blocking working surface 148 has reliably leaped onto the blocking tooth blocking working surface 108, and mutually resists and establishes a stable self-locking static friction relationship, thereby driving the blocking.
  • the ring 100 is circumferentially slid over the reference end face 70 of the first member 50 to stop the axial separation process between the two engaging elements at a maximum separation distance.
  • the axial spacing between the second engagement element 80 and the first engagement element 50 is constant at zero, both in a zero contact over sliding friction condition without any impact and impact, especially at the moment of separation. This will significantly reduce the wear rate of both, eliminating noise and extending life.
  • the first engaging tooth or the second engaging tooth top surface may be formed in a stepped shape with an inner end to significantly reduce the average sliding friction radius and residual torque under an overload condition. Its residual torque coefficient will be much smaller than the sliding friction coefficient.
  • the safety clutch of the present embodiment has the characteristics of no impact and collision in the overload separation in both directions. It should be emphasized that controlling the spiral rising surface of the blocking working surface in the fitting mechanism is a prerequisite for ensuring zero collision of the engaging teeth in the blocking condition, that is, ⁇ > 0 is required. And
  • the ring is referenced to the end face 70.
  • one method of the embodiment is the inversion method, and the precondition of the implementation is that ⁇ > e c + e f + ⁇ .
  • the active component of the safety clutch is reversely rotated through one tooth, that is, the first engagement element 50 is rotated relative to the second engagement element 80 opposite to the relative rotation of the overload.
  • the auxiliary blocking teeth 142 can slide away from the blocking working surface 108 of the blocking tooth 102, and the second engaging tooth 82 can be synchronously fitted and reset without reverse separation blocking, especially when used.
  • the blocking tooth slot is rotated synchronously with the auxiliary blocking tooth 142, see Fig.
  • Another method of fitting reset in this embodiment is the stall method. That is, while maintaining the overload rotation condition, the rotation preventing pin interlocking ring 180 is axially pressed to overcome the axial reaction force of the spring 186, and then the rotation preventing pin 182 is axially pressed into the sliding end surface 124 of the blocking ring.
  • the blocking ring 100 is circumferentially stopped at a specific relative position which causes it to lose its axial blocking ability, and thus, the auxiliary blocking teeth 142 are slid and climbed by the blocking teeth 102, and are passed over the middle portion thereof.
  • the limit projection 114 is then embedded in the next slot of the blocking ring 100, thereby achieving the purpose of controlled clutch resetting of the clutch.
  • the safety reset of the safety clutch of the present invention has a simple mechanism and a reliable process. It is easy to realize automation and remote control through reversal or electric, liquid and mechanical, and the performance of the jaw-type safety clutch is greatly improved, and the performance thereof is greatly increased. Operating speed, torque and adaptable over-carrying frequency, as well as mountable parts. Significantly expand its application area and scope to become a universal safety clutch.
  • both the blocking ring stop mechanism and the controlled locking reset stop method are optional structures or methods that are not required.
  • the rising angle P of the flank 118 of the central limiting projection of the tooth tip must satisfy the inequality:
  • the embodiment is a pure one-way safety clutch, a blocking and fitting mechanism having only a one-way blocking function can be adopted, as shown in FIG. 4(e). At this time, the circumferential degree of freedom of the fitting mechanism can be zero.
  • the constraint on the barrier ring 100 in this embodiment is not necessary, and the purpose of this is only to absolutely ensure that the blocking fitting mechanism can establish an axial blocking relationship in the first time.
  • the manner of restraining is not limited to one type of spring compression, and may be a method of making all or part of the first engaging element 50 or the blocking ring 100 with a magnetic material to cause magnetic attraction of the two, or forming the blocking ring 100 into a belt.
  • the elastic split ring of the shoulder or the elastic split ring with a tapered rotating surface, or a radial elastic force acting on the partial conical surface of the blocking ring 100, such as a spring ball and an elastic snap ring Radial compression method.
  • the barrier ring 100 and its restraining method, the blocking fitting mechanism, the limit fitting mechanism, and the retaining ring rotation preventing mechanism, their relationship with other members, including the blocking ring 100 with the second engaging member 80 as a reference ring and following The scheme of the axial movement, and the description of ⁇ and ⁇ , the Chinese patents and the names of the applicants in the patent applications 200720076912.5, 200720146908.9, 200720146910.6, 200720146911.0 and 200720146909.3
  • 200720076912.5, 200720146908.9, 200720146910.6, 200720146911.0 and 200720146909.3 There are more detailed descriptions of the invention patents, and the above-mentioned nine patents are hereby incorporated by reference in their entirety herein in their entirety.
  • Figure 5 illustrates all possible top contact situations for a blocking engagement mechanism having various tooth profiles in a blocking condition.
  • ⁇ ⁇ ⁇ ⁇ ⁇ which shows all the tooth profile relationships of the control fitting mechanism that can achieve zero contact friction of the split tooth tip and wear compensation function.
  • Fig. 5(d) shows the case of 3 ⁇ ;
  • Figures 5(a), 5(b) and 5G) correspond to various tooth profile relationships with collisional wear after overload separation.
  • Figure 6 illustrates an embodiment in which the blocking engagement mechanism is radially external to the working mechanism of the axially-controlled clutch.
  • the clutch is still specifically a jaw-mounted safety clutch.
  • the blocking ring 100 is sleeved on the outer cylindrical surface of the first engaging member 50 and is restrained on the reference end face 70 by the restraining spring 120 and the restraining snap ring 122. With respect to the first embodiment shown in Fig. 1, the residual torque of this embodiment is large.
  • FIG. 7 An embodiment of the most cylindrical structure of the present invention is shown in Fig. 7, which is a safety clutch having an independent assembly form.
  • the layout of the working engagement mechanism and the blocking engagement mechanism is completely as shown in FIG.
  • the blocking ring 100 is an open elastic ring having an open section 130 having a tapered outer surface which is stationary by the elastic reaction force with the reference cylindrical surface 72 and abuts against the reference end face 70.
  • the first member 50 is rigidly integrated with the first sleeve 204, and the adjusting nut 164 directly connects the first " ⁇ member 50 and the spring 160. All the structures of the second engaging member 80 are almost completely as shown in FIG. 2, the only difference being that The characteristic curved surface on which the torque is transmitted is changed from the inner cylindrical surface to the outer cylindrical surface, that is, the tooth surface of the tooth 214.
  • FIG. 8 to 10 show a fourth embodiment of the present invention, that is, a jaw-mounted self-locking differential.
  • the first component 50 is embedded in the inner hole of the active ring 230 and axially fixed by the snap ring 210.
  • the two second engaging elements 80 are mounted on both ends of the active ring 230, and the four rings are fitted.
  • the end faces are oppositely formed to form two force transmitting fitting mechanisms and two working engaging mechanisms.
  • Two engaging springs 160 press the second member 80 from both ends to ensure the continued presence of the engaging pressure, and the outer ends of the two springs 160 are supported by the two spring seats 162.
  • the two spring seats 162 are respectively axially constrained by the outer shoulders of the two second shafts 206 fitted in their bores.
  • the two second rotating shafts 206 are respectively circumferentially fixed with the inner holes of the two second components 80 in a splined manner, and the inner rotating shaft of the second rotating shaft 206 is processed with a transmission torque to the output half shaft (not shown).
  • Spline teeth are respectively mounted in the circular groove of the end face of the first component 50 with the fitting end face facing the second engaging member 80, with the inner wall of the groove being the reference end face 70, with the first engaging member 50 As the reference ring.
  • Two restraining springs 120 are respectively installed between the blocking ring 100 and the inner end faces of the outer spline teeth of the second rotating shaft 206, and the blocking ring 100 is pressed against the reference end face 70.
  • the first element is radially machined in the four radial lugs of the active ring 230
  • the hole 234 is removed.
  • the entire differential has a completely symmetrical layout and structure in the axial direction.
  • the number of the rectangular teeth and the engaging teeth on all the members are completely the same, and the circumferential direction is evenly distributed.
  • the active ring 230 and the end faces of the first " ⁇ element 50 are circumferentially oriented. Strictly in place.
  • the structure of the second engaging element 80 is as shown in FIG. 9.
  • the driven force transmitting teeth 92 having an inverted trapezoidal cross section are uniformly arranged from the outside to the inside, and the cross section is trapezoidal.
  • Figures 9(a) and 9(b) show the radial relationship of the three
  • Figure 9(c) shows the tooth surface relationship between the three.
  • the driven force tooth top surface 94, the second joint tooth top surface 844 ⁇ is easily and accurately formed at one time; for the structural tube single and facilitate machining, the driven force tooth root surface 96, the second joint tooth root surface 86
  • the auxiliary blocking tooth root surface 146 is coplanar; after cutting off the partial teeth of the second engaging teeth 82 and the auxiliary blocking teeth 142 with the radially extending surface of the driven force transmitting tooth side 98, the second The engaging tooth side surface 88 is partially retained, and the auxiliary blocking tooth 142 is divided into two, each retaining a blocking working surface 148, the tooth top surface 144 is no longer present, and the tooth side surface 150 is coplanar with the driven force transmitting tooth side surface 98. .
  • the blocking working faces 148 of all the auxiliary blocking teeth 142 are spiral faces with an angle of increase ⁇ ,
  • the tooth profile of the active force transmitting teeth 232 is exactly the same as the driven force transmitting teeth 92, and the second engaging teeth 82 are the trapezoidal trapezoids, see Fig. 10(d) and Fig. 10(e).
  • the basic structure of the blocking ring 100 is as shown in Fig. 3, and the description will not be repeated.
  • the layout of the separation and holding mechanism in this embodiment is completely the same as the embodiment shown in FIG.
  • the embodiment is actually a combination of two symmetrically arranged jaw-mounted safety clutches and two symmetrically arranged jaw clutches with inverted trapezoidal force transmitting teeth, so that the one-side separation and holding mechanism, that is, the blocking inlay
  • the structural features and working processes of the engaging mechanism and the limiting fitting mechanism are completely the same as those of the embodiment shown in Fig. 1.
  • 11 to 12 show a fifth embodiment of the present invention, in which the axially self-controlled clutch is specifically the most typical spring steel ball safety clutch.
  • the first engaging member 50 is fitted by an end of the steel ball hub 90 to the outer cylindrical surface of the unthreaded end of the second bushing 206, and is axially fixed by the snap ring 210.
  • the second bushing 206 is rigidly integrated with the steel ball hub 90.
  • the barrier ring 100 is placed in a circular recess of the mating end of the first engagement element 50.
  • the restraining spring 120 is mounted between the barrier ring 100 and the steel ball hub 90, forcing the blocking ring 100 to abut against the end wall of the circular groove, i.e., the reference end face 70, to hold the latter stationary thereon.
  • the steel ball 60 is placed in the circumferentially uniform axial through hole in the steel ball hub 90, and a part of the ball is embedded in the groove on the corresponding end surface of the first member 50 in one direction, and some balls are still on the other side. It is topped up on the end face of the second engaging member 80.
  • the second engaging element 80 is sleeved by the other end of the steel ball hub 90 on the outer cylindrical surface of the threaded end of the second bushing 206.
  • the auxiliary blocking teeth 142 attached thereto pass through the axial escape through holes on the steel ball hub 90, and form a blocking fitting mechanism with the blocking ring 100.
  • Spring 160 is mounted between second engagement element 80 and adjustment nut 164.
  • the adjustment nut 164 is threadedly coupled to the external thread of the second sleeve 206.
  • the tapered bushing 208 is for fixedly coupling the second sleeve 206 and the second rotating shaft, and is axially biased by the bolt 220 and the threaded hole 222.
  • the anti-rotation pin interlocking ring 180 is uniformly distributed with three anti-rotation pin pins 182 in the circumferential direction, and the three pin-stop pin mounting holes 188 respectively embedded in the outer ends of the first member 50 are respectively inserted into the pin holes 188 of the anti-rotation pin 182
  • the face is close to but not in contact with the blocking ring 100 and is secured by a return spring 186 disposed between the pinning pin linkage ring 180 and the first member 50.
  • the second engaging element 80 acts as a main ring of the attached blocking ring in the form of an annular base that is integrally attached as the blocking tooth 142, as shown in FIG.
  • Three auxiliary blocking teeth 142 are evenly distributed on the same end surface at the inner hole of the second engaging member 80, and each of the tooth tips is symmetrically formed with two spiral working faces 148, I ⁇ having an angle of increase ⁇ . I ⁇ ⁇ ⁇ .
  • the bidirectional separation and holding mechanism that is, the control fitting mechanism that blocks the fitting mechanism and the limit fitting mechanism, is located radially in the first engaging element 50, the steel ball 60, the steel ball hub 90, and the second Within the working engagement mechanism formed by the engagement elements 80.
  • the structural features and working processes of the separation and holding mechanism, as well as the structural features, the circumferential relative relationship, the working process and the implementation conditions of the blocking ring rotation preventing mechanism are completely the same as those of the embodiment shown in FIG. 1 , the only difference being that this embodiment
  • Related parameters and nouns are as follows:
  • Steel ball equivalent tooth top surface In the clutch, a friction pair is formed between the steel ball 60 and the surface of the steel ball groove on the end surface of the first engaging element 50, and the friction coefficient of the friction pair must correspond to a fixed friction angle, if The double angle of the friction angle is the cone angle, and the steel ball center is the cone apex, and the surface of the steel ball included in the cone surface whose axis is parallel to the rotation axis of the clutch is defined as the steel ball equivalent tooth top surface. Only when the position of the axial-to-top contact between the first engaging element 50 and the steel ball falls within the equivalent top surface, the friction pair between them can be ensured to be in a self-locking state.
  • the angle between the intersection of the rotating cylindrical surface of the spherical center of the steel ball 60 and the upper edge of the groove of the two adjacent steel balls on the joint end surface of the first element 50 is the angle corresponding to the circumference.
  • the ⁇ in this embodiment is substantially identical to the above embodiment.
  • the axial self-control clutch is specifically a one-way overrunning clutch in the form of a wheel-shaft transmission.
  • the limit fitting mechanism in the separation and holding mechanism is fixed in the circumferential direction of the blocking and fitting mechanism, and is a pin-slot type radial insertion.
  • the first one The mating element 50 is the reference ring of the blocking ring 100
  • the second engaging element 80 is the main ring of the auxiliary blocking ring
  • the second bushing 206 is the main ring of the auxiliary limiting ring.
  • the first engaging element 50 is fitted over the smooth section of the second sleeve 206, and the bearing 216 therebetween unidirectionally constrains the first element 50, which in turn is unidirectionally restrained by the snap ring 210a on the second sleeve 206.
  • the second engagement element 80 fits over the spline tooth segments of the second sleeve 206 and is circumferentially fixed by the spline teeth.
  • the first engagement element 50 and the second engagement element 80 form a working engagement mechanism.
  • the engagement spring 160 is mounted between the non-fitting end face of the second engagement element 80 and the spring seat 162.
  • the spring seat 162 is axially defined by the snap ring 210b on the outer end side of the second sleeve 206.
  • the blocking ring 100 is located radially in the working engagement mechanism, and the sliding end surface 124 abuts against the reference end surface 70 of the first engaging element 50, and forms a blocking engagement mechanism with the auxiliary blocking ring, and a limit embedded in the second sleeve 206.
  • the pin 134 constitutes a limit fitting mechanism.
  • the wave constraining spring 120 is placed between the blocking ring 100 and the end face of the outer spline teeth of the second bushing 206.
  • the second engaging member 80 is as shown in FIG. 14, except that the second engaging teeth 82 are radial teeth having a zigzag cross section, and the auxiliary blocking teeth 142 are circumferentially aligned to be radially integrated with a second engaging tooth 82, and
  • the blocking teeth 102 are uniformly distributed on the outer ring surface of the annular base 112, and the clamping grooves 136 are uniformly distributed on the inner annular surface of the annular base 112. In the axial direction, the blocking teeth 102 are significantly higher than the annular base 112.
  • the blocking tooth top surface 104 is the blocking working surface 108, and the tooth groove formed by the blocking tooth side 110a, 110b can accommodate the auxiliary blocking tooth 142 with a circumferential degree of freedom greater than zero.
  • the top end of the blocking tooth 102 is a fitting end of the blocking ring, and the bottom end surface thereof is the circumferential sliding end surface 124 of the blocking ring 100.
  • the first component 50 and the second engaging component 80 constitute a one-way working engagement mechanism that is both a force transmitting and a working engagement mechanism, blocking
  • the ring 100 and the auxiliary blocking ring constitute a one-way blocking fitting mechanism, and the two fitting mechanisms may have a circumferential degree of freedom of zero.
  • the limiting pin 134 on the second sleeve 206 and the limiting groove 136 of the blocking ring 100 constitute a limiting fitting mechanism (the dotted line in the figure), and the circumferential degree of freedom X of the mechanism is larger than the inlet margin of the blocking fitting mechanism.
  • the circumferential relative position of the limit fitting mechanism and the blocking fitting mechanism and the circumferential dimension of the respective members are determined, that is, in the fitting state of the blocking fitting mechanism, the limit pin 134 must be able to reach the limit The limiting working face 138b of the groove 136.
  • D t ⁇ D e (the horizontal line symbol indicates the axial distance, the same below), where ⁇ represents the initial separation height of the working engagement mechanism in the non-designed separation and overrun direction, The initial separation height in the designed separation direction is always zero, and D c represents the full tooth engagement depth of the working engagement mechanism, representing the minimum blocking height of the blocking engagement mechanism.
  • the above separation and blocking process is reliable, and the blocking ring 100 passively rests on the first component 50 of the reference ring.
  • the ring Before the barrier relationship is established, the ring is not required to be circumferentially or axially. Anything, there is no problem such as motion response, air travel and driving friction, and all the separating actions are performed by the second engaging element 80 which is rigidly integrated with the auxiliary blocking ring, which causes the separating actuating action of the blocking action itself. This will be particularly beneficial for blocking the establishment of relationships, and is significantly better than the prior art.
  • arranging the barrier ring 100 within the radial direction of the working engagement mechanism also reduces residual torque and wear consumption.
  • the relative rotation between the blocking teeth of the blocking mechanism can only be a skipping slip, and it is impossible to self-lock between the tooth tips.
  • the barrier ring 100 is never able to automatically follow the second engaging member 80, but only to rest on the reference end face 70 of the first engaging member 50.
  • the fitting reset of this embodiment is very simple and natural, and can be reversely rotated. That is, as long as the second engaging element 80 is caused to rotate relative to the first element 50 in opposition to the arrows in FIGS. 16(c) and 16(d), the auxiliary blocking teeth 142 can slide away from the blocking tooth blocking working surface 108, The second engagement tooth 82 is synchronously fitted and reset. However, before the point A of the auxiliary blocking tooth blocking working surface 148 has not slipped away from the front point G of the blocking tooth blocking working surface 108, the second engaging tooth 82 has circumferentially missed the first engaging tooth notch.
  • the chisel reset needs to be rotated by one tooth to complete, but there will be no jamming or chipping. Since there is a limit of the height of the separation of D t ⁇ ⁇ , the two engaging teeth 52 and 82 necessarily reverse the separation. At the same time, when the limiting pin 134 is in contact with the limiting working surface 138b of the limiting groove 136, the auxiliary blocking tooth top surface 148 The rear point B does not miss the H point that blocks the entrance of the tooth slot, and the entire top surface 148 is still above the entrance of the blocking tooth slot.
  • the fitting resetting process of the embodiment has a simple mechanism and a reliable process, and the spring is not provided with the engagement pressure, and the size, specific performance parameters and stability of the spring are not any. relationship.
  • the influence of the engaging spring 160 on the fitting and resetting process of the blocking fitting mechanism is completely eliminated, making it possible to change the engaging pressure and adjust the spring size.
  • the manufacturing accuracy, cost, and clutch assembly requirements of the spring 160 are greatly reduced, and the service life is significantly improved.
  • This embodiment can also be modified into a two-way safety clutch as shown in FIG.
  • the blocking fitting mechanism having the two-way blocking function is almost identical to the working principle, basic structure and parameter requirements of the blocking fitting mechanism of the present embodiment.
  • the auxiliary blocking teeth 142 are preferably formed in a circumferential direction by the radially extending portions of the two second engaging teeth 82, and the middle portion of the tooth body is discontinuous, see FIG.
  • the two first engaging elements 50 are rigidly integrated with the non-fitting end faces as symmetrical faces, and are formed in the form shown in Fig. 17.
  • the second engagement element 80 changes only in that its spline teeth are moved toward the mating end.
  • Figure 17 shows a seventh embodiment of the present invention, wherein the axial self-control clutch is specifically a double safety clutch in the form of a wheel-shaft transmission.
  • the first element 50 is a reference ring of the barrier ring 100
  • the inner hole surface is the reference cylindrical surface 72
  • the second joint element 80 is the main ring of the auxiliary blocking ring. Strictly correct.
  • the two second engaging elements 80 are circumferentially fixed to the first sleeve member 206 by spline teeth and respectively form a working engagement mechanism with the first engaging member 50.
  • the two sets of disc springs 160 are respectively pressed against the second engaging element 80 by both ends, and are supported and adjusted by the shoulder of the second bushing 206-end and the adjusting nut 164 of the other end.
  • the blocking ring 100 is located radially within the working engagement mechanism and axially between the two second engagement elements 80, and each of the auxiliary blocking rings constitutes a blocking engagement mechanism.
  • the two working engagement mechanisms and the two blocking engagement mechanisms are in a fitted state or an overloaded separation state in synchronization.
  • a plurality of bolt holes 74 are formed in the first member 50.
  • the inner bore shoulder 128 of the barrier ring 100 serves to ensure the concentricity of the first engagement element 50 during over-loading, and can also be applied to the second engagement element by raising the projection 114 on the barrier ring 100. The way in the 80 annular groove is realized.
  • the pawl lever 136 and the pawl return spring 138 are disposed in radial bores on the axially symmetric faces of the reference cylindrical surface 72.
  • a circumferential ratchet 134 is formed in the central groove of the outer cylindrical surface of the blocking ring 100, and the pawl lever 136 embedded therebetween restrains the blocking ring 100 On the reference cylindrical surface 72.
  • the ratchet pawl mechanism only allows the blocking ring 100 to continue to rotate in the direction of the overload on the reference cylindrical surface 72, and the reverse direction is blocked.
  • the number of teeth and the circumferential position of the ratchet teeth 134 are determined by such an effect, that is, when the blocking ring 100 is stopped by the pawl lever 136, the position of its staying position should ensure that the working engagement mechanism can be fitted and reset.
  • the positioning of the auxiliary blocking teeth in the center of the blocking tooth groove is optimal. It is a good choice to have the same number of teeth and the same uniformity.
  • the second engaging member 80 is completely as shown in Fig. 2 except that the spline tooth portion is axially biased toward the fitting end.
  • the barrier ring 100 has the same structural features and the barrier teeth 102 formed on the both end faces of the annular body, except that the ratchet teeth are formed as compared with FIG. Feature size.
  • the blocking ring 100 does not have the support of the reference end face, the axial force acting on it must be in pairs due to the synchronism of the action of the working engagement mechanisms at both ends, so that the blocking ring 100 still has a stable axial position.
  • the shoulder of the radially outer end of the anti-rotation pin 182 is sleeved with a spring slidably embedded in the radial through hole between the bolt holes 74 of the first component 50, and the pin top surface is close but not Resist the barrier ring 100.
  • a rotation preventing groove 126 is disposed at a corresponding position of the outer cylindrical surface of the blocking ring 100, and a rotation preventing pin interlocking ring 180 is disposed on a corresponding outer cylindrical surface of the first engaging element 50, and the inner cylindrical surface of the ring is a groove type cam The cam surface cooperates with the radially outer end of the anti-rotation pin 182 and is axially constrained by the pin.
  • the circumferential stop brake pin pin interlocks the ring 180, that is, the cam is opposite the first engaging member 50.
  • the anti-rotation pin 182 can be radially pressed into the anti-rotation groove 126 of the blocking ring 100, thereby stopping the blocking ring 100 circumferentially in a relative position that causes it to lose axial blocking capability.
  • the centrifugal force and the radial spring force will force the detent pin 182 to return to the maximum outer diameter of the cam surface again, thereby causing the pin to disengage the anti-rotation groove 126.
  • the barrier ring 100 can also be formed into a resilient split ring form to form a self-constrained.
  • the blocking fitting mechanism of the present embodiment can have a two-way blocking ability after the rotation preventing method is employed.
  • the separation and holding mechanism of the embodiment has no friction resistance torque of the end face sliding, and only the frictional resistance torque of the ratchet mechanism is after the overload.
  • the residual torque will be very small. If the blocking ring 100 is in the self-constrained form of the open elastic ring, and the fitting reset adopts the non-rotation method, the residual moment coefficient will be more nearly zero, and it is not necessary to stop after the overload. This feature is required to transmit high speed without stopping the machine. High torque drive shafts are very important, such as in wind power generation.
  • the joint tooth has a trapezoidal cross section, even if there is a circumferential positional error between the individuals, only a slight separation in the axial direction of a certain working engagement mechanism is caused in the force transmitting state, and the two working engagement mechanisms are subjected to The torque is no longer strictly equivalent, such as 49.9% vs. 50.1%, and has almost no impact on overall performance, effectiveness and reliability.
  • Figure 18 shows an eighth embodiment of the present invention, i.e., the axially self-controlled clutch is specifically a double spring ball safety clutch in the form of a wheel-to-shaft transmission. It is essentially the result of the twin-linking principle of the embodiment of Fig. 17, which doubles the core structure of the spring steel ball safety clutch of the two embodiment shown in Fig. 11.
  • the torque transmission and the separation blocking after the overload are the same as those in the embodiment shown in Fig. 11, and the fitting reset is the same as the embodiment shown in Fig. 17, and the description will not be repeated.
  • the second bushings 206a and 206b are axially centered and fixed in the manner of the flange coupling, and the fastening screw 228 also holds the first engaging member 50 and the blocking ring 100 together.
  • the end face steel ball groove or the radial tooth of each of the first member 50 and the blocking ring 100 are strictly symmetrical with respective axisymmetric faces, and the torque transmitting teeth 214 are directly formed on the outer cylindrical surface of the first member 50. on.
  • the bolt 220 for fastening the tapered bushing 208 is simultaneously penetrated through the axially through hole to simultaneously press the tapered sleeve 208 at both ends, and the working shaft and the fastening screw 228 together serve as the axial support of the engaging spring 160.
  • the other components are exactly the same as those of the embodiment shown in Fig. 11 or Fig. 17, and the description thereof will not be repeated.
  • the spring 160 and the spring seat 162 are not the only options for providing a mating force to the working engagement mechanism.
  • a solution to eliminate the two to form the first engagement element or the second engagement element from a magnetic material is an alternative.
  • An electromagnetic force scheme of the electromagnetic clutch can also be employed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

Mécanisme de maintien de séparation pour tous types d'embrayage à contrôle automatique axial de type à contrainte par ressort, comprenant: une bague de blocage (100), une bague de blocage auxiliaire (80) et une bague d'espacement auxiliaire (210). Les deux bagues (100) et (80) définissent un mécanisme de stabilisation de blocage permettant de maintenir la séparation de la connexion opérationnelle. La bague (100) et la bague d'espacement auxiliaire (210) définissent un mécanisme de stabilisation d'espacement permettant de stabiliser le blocage du mécanisme de stabilisation de blocage. Le mécanisme de stabilisation d'espacement et le mécanisme de stabilisation de blocage sont intégrés de façon rigide ou fixe en position circonférentielle. Le mécanisme de stabilisation de blocage se trouve dans la connexion opérationnelle en position axiale et à l'intérieur ou à l'intérieur de la connexion opérationnelle. Les éléments du mécanisme de stabilisation de blocage ont un angle de montée suffisant pour assurer l'auto-verrouillage une fois le contact établi et pour assurer la stabilité de blocage. Ainsi, On garantit une séparation auto-adaptable et une compensation d'usure auto-adaptable, et il est possible de maintenir le mode de rotation avec glissement. Le processus de blocage de séparation et de relance de stabilisation du mécanisme de stabilisation de l'espacement sont absolument fiables.
PCT/CN2007/002752 2007-09-18 2007-09-18 Mécanisme de maintien de séparation pour embrayage à contrôle automatique axial de type à contrainte par ressort WO2009036595A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2475941A (en) * 2009-09-21 2011-06-08 Paul Turton Motor driven display mount having a safety cut-off
EP2845834A1 (fr) * 2013-09-04 2015-03-11 EFS-Gesellschaft für Hebe- und Handhabungstechnik mbh Système de levage, limiteur de couple et procédé de fonctionnement d'un système de levage

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3923131A (en) * 1974-08-26 1975-12-02 American Challenger Corp Shift ring for a marine clutch
CN87101716A (zh) * 1986-03-07 1987-11-18 伊顿公司 阻挡式牙嵌式离合器组件
US5451070A (en) * 1993-05-26 1995-09-19 Lindsay; Stuart M. W. Treadle drive system with positive engagement clutch
JP2005106122A (ja) * 2003-09-29 2005-04-21 Ntn Corp ２ウェイクラッチユニット

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3923131A (en) * 1974-08-26 1975-12-02 American Challenger Corp Shift ring for a marine clutch
CN87101716A (zh) * 1986-03-07 1987-11-18 伊顿公司 阻挡式牙嵌式离合器组件
US5451070A (en) * 1993-05-26 1995-09-19 Lindsay; Stuart M. W. Treadle drive system with positive engagement clutch
JP2005106122A (ja) * 2003-09-29 2005-04-21 Ntn Corp ２ウェイクラッチユニット

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2475941A (en) * 2009-09-21 2011-06-08 Paul Turton Motor driven display mount having a safety cut-off
EP2845834A1 (fr) * 2013-09-04 2015-03-11 EFS-Gesellschaft für Hebe- und Handhabungstechnik mbh Système de levage, limiteur de couple et procédé de fonctionnement d'un système de levage
US9528578B2 (en) 2013-09-04 2016-12-27 Efs-Gesellschaft Fuer Hebe- Und Handhabungstechnik Mbh Lift system, overload coupling and method for operating the lift system

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