WO2006045225A1 - Embrayage antirecul du type à contact de surface amélioré - Google Patents

Embrayage antirecul du type à contact de surface amélioré Download PDF

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Publication number
WO2006045225A1
WO2006045225A1 PCT/CN2004/001240 CN2004001240W WO2006045225A1 WO 2006045225 A1 WO2006045225 A1 WO 2006045225A1 CN 2004001240 W CN2004001240 W CN 2004001240W WO 2006045225 A1 WO2006045225 A1 WO 2006045225A1
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WO
WIPO (PCT)
Prior art keywords
clutch
drum
friction plate
disc
driven
Prior art date
Application number
PCT/CN2004/001240
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English (en)
Chinese (zh)
Inventor
Wenming Han
Original Assignee
Beijing Wujitong Automotive Systems Technology Co., Ltd.
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 Beijing Wujitong Automotive Systems Technology Co., Ltd. filed Critical Beijing Wujitong Automotive Systems Technology Co., Ltd.
Priority to PCT/CN2004/001240 priority Critical patent/WO2006045225A1/fr
Publication of WO2006045225A1 publication Critical patent/WO2006045225A1/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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/04—Freewheels or freewheel clutches combined with a clutch for locking the driving and driven members

Definitions

  • the invention relates to a one-way overrunning clutch for transmitting torque in one direction, and particularly relates to a surface contact type one-way clutch capable of transmitting large torque in applications such as idle speed and high frequency.
  • the one-way overrunning clutch has various structural types, including a ratchet type, a roller chute type, a wedge type, and a link type, but the one-way clutch of these structures has many disadvantages:
  • the ratchet one-way overrunning clutch is mainly composed of an outer wheel, a ratchet, a pawl and a leaf spring.
  • the pawl catches the ratchet, the outer wheel and the ratchet are integrally connected and rotate synchronously, and the clutch is in a locked state;
  • the outer wheel rotates in the other direction with respect to the ratchet, between the pawl and the ratchet Relative slip occurs, the outer wheel becomes the free wheel, and the clutch is in a free state.
  • the engagement position of the ratchet and the pawl of the clutch is limited (the ratchet rotates at least - the angle of the ratchet with respect to the outer wheel at a time to ensure that the pawl cooperates with the ratchet), and a large impact and P noise is generated during the engagement. Not sensitive enough, 'only for low speed, low frequency transmission.
  • the Chinese Utility Model Patent No. CN2594533 authorized by the State Intellectual Property Office on December 24, 2003, discloses a ratchet type one-way clutch, which has the disadvantage of going back.
  • the roller chute type one-way overrunning clutch is composed of an outer ring, an inner ring, a roller, a roller return spring and the like.
  • a wedge groove for accommodating the roller is formed on the inner surface of the outer ring or the outer surface of the inner ring, and the roller groove and the return spring are arranged in the wedge groove, and the elastic force of the spring pushes each roller toward the narrow end of the wedge groove.
  • the one-way overrunning clutch is in the locked state; when the outer ring rotates in the other direction with respect to the inner ring, the roller overcomes the spring force of the spring under the action of the friction force, rolling toward the wedge shape At the wider end of Cao, slipping occurs, and the outer ring is free to slip relative to the F3 ⁇ 4 ring. At this time, the one-way overrunning clutch is released from the lock and is in a free state. Since the roller is always in line contact with the inner and outer rings, the clutch is only suitable for medium-speed and ⁇ -frequency applications. The highest frequency is not more than 150 times/min. In addition, the wedge groove processing is complicated and the process is poor. Request to make The high hardness and high wear resistance of the material also requires the core of the roller to have toughness and can withstand the ⁇ r load to avoid chipping. Therefore, the production cost is high.
  • the structural phase 4 of the wedge type one-way overrunning clutch and the roller chute type one-way overrunning clutch is also composed of an outer ring, an inner ring and a roller between the outer ring and the inner ring.
  • the shape of the wedge is similar to a parallelogram.
  • the diagonal direction of the parallelogram is slightly larger than the S large distance between the inner and outer rings, and the other diagonal direction is slightly smaller than the inner and outer ring branches 1.
  • a ⁇ 5 radial contact one-way clutch - a link type one-way overrunning clutch has appeared.
  • China National Intellectual Property discloses a "chain-ring single- and double-way overrunning clutch", which is composed of a jacket, an inner core, a control key and a link.
  • the link is placed between the outer sleeve and the inner core, and is composed of a chain head, a plurality of links and a chain tail which are connected in sequence; one end of the control key is simultaneously inserted into the rectangular d-hole of the chain end and the end of the chain, so that the chain is chained.
  • the tail is overlapped, and the other end is inserted into the trapezoidal groove of the outer casing. Adjustments are provided at the hooks between the links.
  • a pretensioning spring is fixed on the outer sleeve, and the other end of the pretensioning spring is fixed to the link. Toggle the control button through the jacket to make the chain ring tightly hug the inner core to achieve self-locking.
  • the clutch has surface contact, the reverse swaying force is small and it is not easy to wear.
  • the joint effect of the link and the inner core is susceptible to the rotation speed of the clutch. For example, when the clutch is running at a high speed, the link is too large due to centrifugal force. With the inner core loosened, the one-way clutch is not suitable for high-speed transmission, and cannot be applied to applications where high-speed operation is required, such as a steam transmission.
  • the technical problem of the present invention is to overcome the above-mentioned deficiencies of the prior art, and to provide an improved face horned type one-way clutch, which is not only responsive, high in reliability, but also capable of effectively transmitting large power and high torque.
  • Power 'Therefore, it can be used in high-speed, high-frequency, heavy-duty and other harsh conditions.
  • the engaging elements are smoothly engaged during locking, and no impact is generated.
  • the joint elements have good wear resistance and long service life.
  • the application of the clutch to components or products such as automotive transmissions can also extend the life of the entire component or product.
  • An improved surface contact type one-way clutch includes an active portion and a driven portion, the active portion being driven to rotate by an input torque, the active portion and the driven portion being axially disposed, and both The rotation axis coincides; the active portion includes at least one active piece, and the driven portion includes at least one driven piece, and the engaging surface of the active piece and the driven piece are closely attached when locked. And the moment is transmitted by the friction between each other.
  • the active or active portion has a helically clamped configuration.
  • the clutch includes a clutch drum and first and second clutch discs parallel to each other in the clutch drum, and at least one drum friction plate 3; at least one spring;
  • the clutch disc clamps the friction plate under the action of the spring,
  • the drum friction plate is sleeved on the sleeve and coupled to the clutch drum in a torqueable manner;
  • the sleeve has an internal thread, a transmission shaft extends into the sleeve, and the extension end is formed There is an external thread that is engaged with the internal thread.
  • a plurality of the drum friction plates are disposed, and a disk friction plate is sandwiched between each adjacent two drum friction plates; the disk friction plate is sleeved on the sleeve and is They can be coupled together in a torque transfer manner.
  • the clutch drum, the first and second clutch discs, the drum friction plate, the sleeve and the rotating shaft of the disk friction plate are coincident; the drum friction plate and the clutch drum are coupled by a spline, and the disk friction The sheet and the sleeve are also coupled by a spline.
  • the end of the clutch drum is formed with an outwardly extending hollow shaft at the middle of the other end; the first clutch disc is fixed to the transmission shaft and is mounted to the opening of the clutch drum by means of a first elastic snap ring The second clutch disc is integrally formed with the sleeve and is mounted on the transmission shaft by a second elastic snap ring.
  • the clutch drum is provided with only one magazine, and the spring is a sheet-shaped compression spring sleeved on the transmission shaft, and is disposed between the second elastic ring and the second clutch disc.
  • the projecting end of the transmission shaft is supported by the bearing in the hollow shaft.
  • the active and driven blades are compressed by means of a four-bar linkage.
  • the clutch includes a housing composed of a clutch disc and a clutch cover that are respectively covered with each other, and the housing is provided with a clutch, a plurality of hub friction plates, and at least one set of disc friction plates. And at least one set of four-link pressing mechanism; a middle portion of the clutch cover is formed with a through hole, one end of the clutch hub is exposed from the through hole; the hub friction plate is annular, and the sleeve is placed The clutch hub and the torque transferable therewith: grounded together; the disk friction plate and the four-link pressing mechanism have the same number of sets, each set of the disk friction plate comprises a plurality of partial annular rings a friction plate disposed opposite to the hub friction plate; each of the four-link pressing mechanisms has a cross bar, and each set of the disk friction plates has a through hole at the same position of each of the disk friction plates, the cross bar is worn Passing through the through hole; the four-link pressing mechanism each of the disk friction plate and the hub friction plate to the friction surface of the clutch
  • each of the four-link pressing mechanisms includes two supporting arms parallel to each other and the cross bar connecting the two supporting walls; one end of the two supporting arms respectively a coupling pin is hinged to the housing, and the other end is hinged with a coupling block by a coupling pin, and two ends of the crossbar are respectively fixed on the two connecting blocks; the crossbar has a spring at one end thereof, One end is provided with a pressing block, and the pressing block is hinged to the coupling pin.
  • the hub friction plate and the clutch hub are coupled to each other by a spline; a center of the clutch disc is mounted with a transmission shaft, one end of the transmission shaft extends outward, and the other end is supported by the clutch hub by bearings Inside the center hole.
  • the casing is provided with three four-bar linkage pressing mechanisms, and three sets of the disk friction plates are correspondingly disposed in the casing, and three sets of four-bar linkage devices and the disk friction plates are circumferentially Evenly distributed.
  • the prior art has the following points: Since the main cloud force portion and the driven portion are axially arranged, 'through the friction between the main and follower pieces The torque is transmitted, not only the joint position between the main and follower is not limited, the joint is stable, the impact is first, ⁇ ⁇ noise and responsive, high reliability, 'can effectively transmit: ⁇ big twist ⁇ and large torque
  • the power can meet the needs of high-speed, high-frequency, heavy-duty and other harsh working conditions; in addition, the wear resistance of the composite components is good, and the life of the car is long.
  • the one-way clutch is mounted on a component or product such as a vehicle transmission, which also improves the operational reliability of the product or component and prolongs its service life.
  • Figure 1 is a perspective cross-sectional view of a preferred embodiment of an improved surface contact type one-way clutch provided in accordance with the present invention
  • Figure 1B is an exploded perspective view of the single-question clutch of Figure 1A;
  • FIGS. 1A and 1B are structural views showing a specific application of the one-way clutch shown in FIGS. 1A and 1B, which is installed at the rear of an eccentric torque-changing mechanism, and together with the torque-changing mechanism constitutes an automobile transmission.
  • Figure 1D is the working principle and force analysis of the one-way clutch shown in Figures 1A and IB;
  • 2A is a perspective, cross-sectional view of another preferred embodiment of an improved face-contact one-way clutch provided in accordance with the present invention;
  • Figure 2B is an exploded perspective view of the one-way clutch of Figure 2A;
  • FIGS. 2A and 2B are structural schematic views of a specific application of the one-way clutch shown in FIGS. 2A and 2B, which is mounted on the rear of the eccentric torque-changing mechanism, and together with the torque-changing mechanism constitutes an automobile transmission device;
  • Figure 2D is a schematic view of the working principle and force analysis of the one-way clutch shown in Figures 2A and 2B.
  • an improved surface contact type one-way clutch provided in accordance with the present invention, comprising an active portion 1 and a driven portion 2, the torque being input from the left, the active portion, as shown 1 is on the left and the driven portion 2 is on the right, and the active portion 1 is driven to rotate by input torque.
  • the active portion 1 and the driven portion 2 are arranged in the axial direction, and the rotational axes of the two coincide.
  • the active portion 1 includes at least one active sheet 11, and the driven portion 2 includes at least one driven piece 21.
  • the active portion 1 and the driven portion 2 are opposite each other, and when the mounting direction of the dispenser is opposite to the illustrated direction, the active portion 1 and the movable portion 2 are interchanged.
  • the active split 1 or the secondary split 2 has a helically clamped configuration.
  • the drum friction plate 54 is sleeved on a sleeve 56, and
  • the clutch drum 51 is torque-coupled together; the sleeve 56 has an inner crepe, and a transmission shaft 57 extends into the sleeve 56, and its projecting end is formed with a mating outer thread. Thread.
  • a plurality of the drum friction plates 54 are provided, and a disk friction plate 5S is sandwiched between each adjacent two drum friction plates 54;
  • the disk friction plate 58 is sleeved on the sleeve 56 and coupled to it in a torque-free manner.
  • the "offer drum 51 and the drum friction plate 54 are the active portion 1
  • the second clutch discs 52, 53 and the transmission shaft 57 are the driven portions 2
  • the drum friction plates 54 and the disk friction plates 58 are engaging elements 11, 21 respectively corresponding to the main and driven portions.
  • the first and second clutch plates 52, 53 are aligned with the engaging member 21 of the driven portion 2, i.e., the disk friction plate, since the disk friction plate 58 is not required to be provided.
  • the rotation axes of the clutch drum 51, the first and second clutches 52:53, 3 ⁇ 4, the friction plate 54, the sleeve 56, and the disk friction plate 58 are coincident;
  • the drum friction plate 4 is coupled to the clutch drum 51 by a spline, and the disk friction plate 58 and the sleeve 56 are also spline-coupled.
  • Huade connection not only ensures that the input choke can be 'effectively' and is easy to process, reducing the cost of sitting.
  • One end of the universal drum 51 is open (the right side of the figure), and the other end is formed with an outwardly extending hollow shaft 511.
  • the end bearing 50 of the transmission shaft 5 is supported by the hollow shaft 511. Therefore, it is convenient to ensure that the transmission shaft 5 is mounted ⁇ , and that the transmission shaft 57 coincides with the axis of the disc drum 51.
  • the bearing 50 is a needle bearing, thereby facilitating the accuracy of the positioning of the transmission by 57.
  • the first release disc 52 is fixed to the transmission shaft 57, and is mounted in the open end of the clutch drum 51 by means of a first elastic snap ring 59A;
  • the sleeve 56 is integrally formed with the yoke 53 and is attached to the transfer 57 by means of a second elastic snap ring 59.
  • the clutch drum is a single spring 55, and the spring 55 is a set of sheet springs on the transmission shaft 57.
  • the second elastic snap ring 59B is between the second clutch disc 53 and the second clutch disc 53. Using a sheet spring The preload force can be effectively applied, and the axial dimension is small, thereby reducing the amount of the bomb charge 55 in the clutch drum 51, thereby reducing the entire body of the one-way clutch.
  • Fig. 1C as a specific application of the one-way clutch described above, it is mounted to the rear of an eccentric torque-changing mechanism 3, which constitutes a transmission for a vehicle shifting.
  • the torque is input from the left end, and the driving gear 31 of the eccentric torque changing mechanism 3 is driven to rotate from the force gear 32, and the driven gear 32 and the eccentric mass 33 are rotated.
  • the centrifugal force generated when the eccentric mass 33 rotates causes the output shaft 35 in the middle of the bracket 34 to output a torque outward.
  • the hollow shaft 51 1 of the clutch drum 51 and the output shaft 35 of the torque converter mechanism 3 are coupled by a key during use, and the transmission shaft 57 and the outer side are also coupled by a key.
  • the working principle and process of the surface contact type one-way clutch are as follows: ⁇ When the output shaft 35 of the household office rotates in the L1 direction of the figure (the locking direction of the clutch), the load is now The resistance direction is the opposite direction of L1, and the output shaft 35 drives the clutch drums 51 and 3b to rotate in the L1 direction; due to the preload force of the compression spring 55, the drum friction plate 4 disc friction plate 5 ⁇ There is friction, the drum friction plate 54 relies on friction to drive the disk friction plate 58 to also rotate in the direction of 3 ⁇ 4, and the disk friction plate 58 is rotated by the spline to rotate the sleeve in the L1 direction.
  • the sleeve 56 and the second clutch disc 53 are moved to the right along the transmission shaft 57 to further press the drum friction plate 54 and the disk friction. Slice 58.
  • the one-way clutch is in the locked state, and the transmission shaft 57 is also actuated in the L1 direction.
  • the provision of the plurality of drum friction plates 54 and the disk friction plates 58 can effectively increase the coefficient of friction. In the case where the drum friction plate 54 and the disk friction plate 58 are predetermined, by properly designing the helix angle (the size of 3, that is, the input torque can be ensured in the L1 direction, the self-locking between the main and driven portions 1, 2 can be realized.
  • the clutch when the input torque is in the L2 direction opposite to L1, the clutch is in the overrun state and does not function as a transmission torque.
  • the transmission shaft 57 and the sleeve 56 are provided with a left-handed thread, the lock is locked.
  • the direction of the stop is opposite to the above.
  • I ll D is a schematic diagram of the working principle of the helically clamped one-way clutch shown in Fig. 1A.
  • the basic principle of the helical clamping is the same as the basic principle of the inclined clamping.
  • the thread is equivalent to a right triangle.
  • a right-angled side is perpendicular to the axis of rotation of the cylinder, and the oblique side is wound around the cylindrical surface I ⁇ .)
  • the inclination angle ⁇ of the oblique side is the helix angle of the thread; the helically clamped one-way clutch
  • Figure ID (b) The principle of the operation is shown in Figure ID (b).
  • the fit of the wedge to the ramp is equivalent to the fit between the internal thread of the sleeve 56 and the external thread of the transmission shaft 57.
  • the wedge corresponds to the second clutch.
  • the combination of the disc 53 and the sleeve 56, the inclined surface and the portion connected thereto are equivalent to the combination of the transmission shaft 57 and the first clutch disc 52; as shown in the ID (c), the one-way clutch locks the wedge.
  • the force of the block is small, i D id ) is small, the force diagram of the wedge when the one-way clutch is unlocked, f is the friction between the drum friction plate 54 and the disk friction plate 58, f ' is the thread pair
  • the motor force n is the number of drum friction plates 54
  • N is the positive pressure between the drum friction plate 54 and the second clutch disk 53
  • S is the positive pressure between the screw mating surfaces.
  • the active sheet 11 and the moving body are pressed by the four-bar linkage mechanism, and the hub friction plate 65 is equivalent to the active sheet 11, and the disk friction plate is
  • the specific structure of the driven piece is: a clutch disc 61 including a cymbal cover and a clutch cover 6 g : a housing 60 as shown in the drawing; 'The preferred embodiment given by the present invention ;
  • the clutch clutch 62 is coupled by bolts.
  • the housing ft is provided with a clutch hub 63, a plurality of friction plates 65, at least one set of disk friction plates 64 and at least one set of four-link pressing mechanisms 66.
  • the clutch hub 63 is located at the center of the housing 60, and a portion of the clutch cover 62 is formed with a through hole 622 from which one end (the right end in the drawing) passes. ? L 622 is exposed so as to be coupled to an external input shaft or an output shaft.
  • the hub friction plate 65 is annular and sleeved over the clutch hub 63 and torqueably coupled thereto. In the preferred embodiment shown, the clutch valley 63 and hub The friction plates 65 are coupled together by splines.
  • a transmission shaft 612 is mounted at the center of the clutch disc 61.
  • One end of the transmission shaft 612 extends outwardly to be coupled to an external input or output shaft; the other end is supported by a center hole of the clutch hub 63 via a bearing 67. Inside, the bearing 67 is a needle bearing. Thus, the transmission shaft 612 is not only radially accurate but also flexible in rotation.
  • the disc friction plate 64 and the four-link pressing mechanism 66 have the same number of sleeves, as shown in FIG. 2A, 2 ⁇ '
  • each of the disk friction plates 64 includes a plurality of partially annular friction plates disposed between the hub friction plates 65; each of the four-link pressing mechanisms 66. Having a cross 661, the same position of each of the disc friction plates 64 has a through hole 641 through which the cross bar 661 passes; the four-link pressing mechanism 6 ⁇ will rub the disc The 64 and valley friction plates 65 are pressed against the friction surface of the clutch disc 61. Referring to FIG.
  • each of the four-bar linkage mechanisms 66 has a body structure including: two support arms 662, 663 parallel to each other and the cross bar 661 connecting the two arms 3662, 663; the two support arms 662, 663 are equal in length, and one end thereof is hinged to the housing 60 by a coupling pin 664, respectively, and the support arms 662, 663 are hinged to the clutch disc 61 and the clutch, respectively.
  • the other end portion iJ is hinged with a connecting block 665, 668 by a connecting pin 665, 666, and two ends of the cross bar 661 are respectively fixed to the two connecting blocks 667, 668.
  • the housing 60, the two support arms 662, 663: the crossbar 66 ⁇ constitutes a parallel four-bar linkage.
  • the end of the yoke 661 is sleeved with a spring 660, and the other end is provided with: 3 ⁇ 4 669, the clamp 669 is hinged to the coupling pin 66'3 ⁇ 4ifc?
  • the spring 660 is a compression spring, and the pressure 660 and the block 669 ⁇ 3 ⁇ 4
  • the pre-tightening force of the hub friction plate 65 and the hub friction plate 65 are such that the disk friction plates 64 and the hub blade 65 are attached to each other.
  • each of the disk friction plates 64 is further provided with two through holes 642, and two cylindrical pins 68 and 69 pass through the two through holes 642 and 643 respectively.
  • the disc friction plates are connected in series; the clutch disc 61 and the clutch cover 62 are correspondingly formed with two K slots 61 1 and 621 extending in the circumferential direction; both ends of the cylindrical pins 68, 69 are inserted into the long slots 611 , 621, : .
  • Each set of the disc friction plates 64 is rotatably mounted on the clutch cover 61 and the clutch disc 62 by the two cylindrical shafts 68, 69.
  • the two cylindrical pins 68, 69 are generated when the disc friction plates 64 are rotated. Centrifugal force.
  • the cabinet 2C as a specific one of the above-described one-way clutches, it is mounted at the rear of an eccentric torque-changing mechanism 3, which constitutes a transmission for the automobile shifting.
  • an eccentric torque-changing mechanism 3 which constitutes a transmission for the automobile shifting.
  • the left end of the torque mountain is input, and the driving gear 31 of the eccentric torque changing mechanism 3 drives the driven gear 32 to rotate, and the driven gear 32 and the eccentric mass 33 rotate together.
  • the centrifugal force generated when the eccentric mass 33 rotates causes the output shaft 35 in the middle of the bracket 34 to output a torque outward.
  • the clutch hub 63 is coupled to the output shaft 35 of the torque converter mechanism 3 during use, and the transmission shaft 612 is also coupled to the outside by a key.
  • 2A, 2B shows the operation and principle of the four-bar linkage type one-way clutch as follows:
  • the clutch valley 63 and the hub friction plate 65 are active ⁇ 1;
  • the disc friction plate 64 and the housing 60 and the transmission shaft 612 are the moving portions 2.
  • the clutch hub 63 rotates in the L1 direction
  • the clutch hub 63 rotates the hub friction plate 65 in the Lr direction by the spline
  • the hub friction plate 65 drives the friction plate 64 to the L1 direction by friction.
  • the hub friction plate 65 rotates the housing 60 in the L1 direction by the parallel four-bar linkage 66.
  • the support arm 663 and the pressing block 669 further press the hub friction plate 65 and the disk friction plate 64, thereby The self-locking is realized; the transmission shaft 612 also rotates in the L1 direction to output a torque outward.
  • the clutch hub .63 rotates in the opposite direction
  • the hub friction plate 65 rotates along 3 ⁇ 43 ⁇ 4, at which time the parallel four-bar linkage chair 66. is automatically unlocked, and the pressing block 9 is facing the hub.
  • the pressure of the friction plate 65 is reduced.
  • the active portion 1 and the driven portion 2 are relatively rotatable, and the clutch is in a state of exceeding the state.
  • the friction coefficient between the disk friction plate 64 and the hub friction plate 65 is parallel.
  • n is the number of disc friction plates or the hub friction plates 65
  • condition of the one-way clutch self-locking is:

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

L'invention concerne un embrayage antirecul du type à contact de surface amélioré, qui se compose d'une partie menante mue par un couple et d'une partie menée. La partie menante et la partie menée sont disposées autour d'un axe et les deux parties sont coaxiales. La partie menante comprend au moins une pièce menante et la partie menée comprend au moins une pièce menée. Les surfaces d'accouplement des dites pièce menante et pièce menée s'engagent en serrant fort au moment du verrouillage pour transmettre le couple même quand cela ne met en jeu qu'une partie de celles-ci. Le produit selon la présente invention a une sensibilité et une fiabilité importantes pour transmettre efficacement une puissance et un couple élevés et par conséquent on peut l'employer même quand il est en mauvais état. Les composants de cette invention peuvent s'assembler au repos sans impulsion. Autrement, les composants pour l'accouplement ont des propriétés anti-fractionnement qui peuvent prolonger la durée de vie du produit. La durée de vie de l'unité ou du produit tout entier peut aussi être prolongée quand on utilise cette invention dans des unités comme une transmission automobile.
PCT/CN2004/001240 2004-10-29 2004-10-29 Embrayage antirecul du type à contact de surface amélioré WO2006045225A1 (fr)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010028654A1 (de) * 2010-05-06 2011-11-10 Robert Bosch Gmbh Rücktrittgetriebe für Elektrofahrräder und Verfahren zur gesteuerten Kopplung von Abtrieb und Motor eines Elektrofahrrads
CN108266503A (zh) * 2017-01-04 2018-07-10 李激初 基于行星轮系的传动装置及内变速器和变速控制方法
CN108869571A (zh) * 2017-05-13 2018-11-23 潘国陶 一种离合器及使用该离合器的变速器

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US4474274A (en) * 1980-12-13 1984-10-02 Sachs-Systemtechnik Gmbh Motor vehicle clutch with an inductive signal transmission between a sensor on the clutch and a stationary indicator
US4515256A (en) * 1981-01-20 1985-05-07 Kabushiki Kaisha Daikin Seisakusho Clutch and brake unit
JPH08261253A (ja) * 1995-03-23 1996-10-08 Nsk Warner Kk ワンウェイクラッチ
US5937980A (en) * 1997-02-24 1999-08-17 Dana Corporation Bi-directional one-way clutch
CN2425234Y (zh) * 1999-02-01 2001-03-28 傅元竹 双自动超越离合器
CN2621238Y (zh) * 2003-06-17 2004-06-23 宋战修 一种单双向可控离合器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4474274A (en) * 1980-12-13 1984-10-02 Sachs-Systemtechnik Gmbh Motor vehicle clutch with an inductive signal transmission between a sensor on the clutch and a stationary indicator
US4515256A (en) * 1981-01-20 1985-05-07 Kabushiki Kaisha Daikin Seisakusho Clutch and brake unit
JPH08261253A (ja) * 1995-03-23 1996-10-08 Nsk Warner Kk ワンウェイクラッチ
US5937980A (en) * 1997-02-24 1999-08-17 Dana Corporation Bi-directional one-way clutch
CN2425234Y (zh) * 1999-02-01 2001-03-28 傅元竹 双自动超越离合器
CN2621238Y (zh) * 2003-06-17 2004-06-23 宋战修 一种单双向可控离合器

Cited By (4)

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CN108266503B (zh) * 2017-01-04 2023-11-24 广东洛梵狄智能科技有限公司 基于行星轮系的传动装置及内变速器和变速控制方法
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