CN110701210A - Controllable inclined strut clutch and bidirectional overrunning clutch applied by same - Google Patents

Controllable inclined strut clutch and bidirectional overrunning clutch applied by same Download PDF

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Publication number
CN110701210A
CN110701210A CN201911011275.4A CN201911011275A CN110701210A CN 110701210 A CN110701210 A CN 110701210A CN 201911011275 A CN201911011275 A CN 201911011275A CN 110701210 A CN110701210 A CN 110701210A
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CN
China
Prior art keywords
wedge
clutch
controllable
inner ring
wedge block
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
CN201911011275.4A
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Chinese (zh)
Inventor
严宏志
王志标
田山林
陈昊旻
蔡孟凯
胡旋
李炎军
王蓉
潘代锋
黎佳
吴江明
曹煜明
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Central South University
AECC Sichuan Gas Turbine Research Institute
Original Assignee
Central South University
AECC Sichuan Gas Turbine Research Institute
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Filing date
Publication date
Application filed by Central South University, AECC Sichuan Gas Turbine Research Institute filed Critical Central South University
Priority to CN201911011275.4A priority Critical patent/CN110701210A/en
Publication of CN110701210A publication Critical patent/CN110701210A/en
Pending legal-status Critical Current

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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
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/069—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags
    • F16D41/07—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags between two cylindrical surfaces
    • 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
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/084—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate coupling members wedging by pivoting or rocking
    • 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
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/10—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action with self-actuated reversing

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

Abstract

The invention discloses a controllable diagonal bracing clutch and a bidirectional overrunning clutch applied by the same, wherein the controllable diagonal bracing clutch comprises an outer ring and an inner ring which are coaxially assembled and a plurality of wedge blocks which are arranged between the outer ring and the inner ring and unidirectionally transmit power along a uniform direction, two ends of each wedge block are respectively provided with a cam structure which is abutted with the outer ring and the inner ring, the outer ring or the inner ring is provided with a positioning groove which is used for embedding and positioning a wedge block cam at one end corresponding to the abutment position of the wedge block, the wedge block swings around the cam at the end part, and the wedge block is pressed into the positioning groove through an elastic piece; and the control frame is used for shifting all the wedge blocks to synchronously swing towards the same direction. The controllable inclined strut clutch can realize the engaging and overrunning functions of the traditional inclined strut clutch, and can lift the wedge block actively to ensure that the wedge block is not engaged when the wedge block is in an engaging condition, thereby realizing a third working state and providing conditions for the application of a multi-clutch combined bidirectional overrunning clutch.

Description

Controllable inclined strut clutch and bidirectional overrunning clutch applied by same
Technical Field
The invention belongs to an overrunning clutch, and particularly relates to a controllable inclined strut clutch and a bidirectional overrunning clutch applied by the same.
Background
The overrunning clutch is used as a coordination component, and can ensure that any engine can work independently and coordinately with a transmission system without mutual influence. Compared with a roller type overrunning clutch, the inclined strut clutch adopting the wedge block has the characteristics of light weight, large bearing capacity and reliable clutching, and is suitable for application of a medium-high speed and heavy-load working condition transmission system. At present, no mature high-speed and large-torque inclined strut clutch design and manufacture technology exists in China, and only inclined strut clutch products with individual specifications are produced and applied.
The common inclined strut clutch can only realize two working modes depending on the wedge block structure of the inclined strut: wedging and overrunning. The torque is transmitted when the inner and outer rings are integrated by wedging the wedges and supporting the inner and outer rings, and the torque is not transmitted when the inner and outer rings rotate relatively to cause the wedges to slide relatively to the inner and outer rings.
In order to make the inner and outer rings capable of transmitting power mutually, two sets of sprag clutches with opposite combining directions are generally arranged between the inner and outer rings, for example, a controllable wedge type bidirectional overrunning clutch disclosed in chinese patent application No. CN201610311304.9, one of the sprag clutches combined according to power transmission requirements in any direction needs to be kept in a wedged state, after a power source is switched, the original wedged sprag clutch is disengaged due to a change of state, at the time, the wedged direction is changed from that of the inner ring driving the outer ring to that of the outer ring driving the inner ring, therefore, another set of sprag clutch with the opposite wedging direction to that of the original wedged sprag clutch is required to change the wedged direction, and only one set of sprag clutch is ensured to work, under the condition that the relative rotation speed of the inner and outer rings of the sprag clutch is required to cause the engagement of the wedge/inner and outer rings, the sprags in the sprag clutch are forcibly raised to disengage them from the inner race without transmitting torque.
The sprag clutch disclosed in CN201610311304.9 lifts or lowers the sprag by the concave-convex edge of the control panel, which requires that the precise position of the sprag is known in advance, but the sprag is free in the circumferential direction and has no means for detecting the precise position of the sprag, so that the lifting and lowering of the sprag cannot be accurately controlled by the control panel, and the engagement and disengagement preset in advance cannot be realized.
Disclosure of Invention
The technical problem solved by the invention is as follows: aiming at the problem that the existing diagonal bracing overrunning clutch can not realize bidirectional power transmission switching when transmitting large torque, a novel controllable diagonal bracing clutch and a bidirectional overrunning clutch applied by the same are provided.
The invention is realized by adopting the following technical scheme:
the controllable sprag clutch comprises an outer ring 1 and an inner ring 2 which are coaxially assembled and a plurality of wedges 31 which are arranged between the outer ring 1 and the inner ring 2 and unidirectionally transmit power along a uniform direction, wherein two ends of each wedge 31 are respectively provided with a cam structure which is abutted against the outer ring 1 and the inner ring 2, the outer ring 1 or the inner ring 2 is provided with a positioning groove 11 for embedding and positioning a wedge cam at one end corresponding to the abutment position of the wedge, the wedge 31 is arranged in a swinging manner around the wedge cam at the end, and the wedge 31 is pressed into the positioning groove 11 through an elastic piece 32;
the automatic control device also comprises a control frame 5 which can be used for shifting all the wedge blocks 31 to synchronously swing towards the same direction, and the wedge blocks 31 always rotate along with the outer ring in any state.
Furthermore, the positioning groove 11 is an arc groove, the cam structure of the wedge 31 correspondingly embedded into the positioning groove is an arc cam, and when the wedge swings, the wedge plays a role in supporting and positioning through the mutual profile matching, so that the wedge swings and lifts around the arc center of the wedge cam. At the same time, the relative position of the wedge 31 to the outer ring is fixed.
Furthermore, the radian of the arc groove of the positioning groove 11 is larger than 180 degrees, the wedge block is prevented from sliding out of the groove when being lifted, and transition guide angles are respectively arranged at two ends of the positioning groove so as to increase the maximum swing angle of the wedge block.
Furthermore, the wedge angle of the wedge cam at the other end of the wedge 31 acting on the contact surface does not exceed 3 degrees, and the performance of the wedge is kept even better than that of the wedge of the common sprag clutch.
Further, the control frame 5 comprises an outer disc 51 and a plurality of shifting blocks 53 arranged on the outer disc 51 and distributed along a circular ring, wherein the shifting blocks 53 are inserted between adjacent wedge blocks one by one, and all the shifting blocks 53 on the outer disc 51 are enabled to shift all the wedge blocks 31 to synchronously swing by rotating the outer disc 51.
Further, the shifting block 53 is in contact with the wedge block far away from the positioning groove, and the contact point is far away from the swinging circle center to easily push the wedge block.
Further, when the wedge 31 needs to be lifted, the control frame 5 acts on the cam side of the wedge 31 with a constant torque in advance, so that the wedge 31 can be lifted immediately when the clutch is in an overrunning state, and the effects that the clutch is not engaged and does not transmit torque under the subsequent engaging trend working condition (the inner ring and the outer ring are in a relative motion state for engaging the clutch) are achieved.
Furthermore, the outer discs 51 are two sets of outer discs arranged coaxially, two ends of each shifting block 53 are fixedly connected with the two sets of outer discs 51 respectively, pockets 52 for accommodating the wedges 31 are formed between the adjacent shifting blocks 53, and the outer discs 51 can limit the wedges axially.
In the controllable inclined strut clutch, a transmission pin 54 connected with an external control executive component is arranged on the outer disc 51.
Furthermore, the wedge 31 is provided with a slot 312, the slots 312 on all the wedges 31 form a circular through slot, the elastic member 32 is an annular elastic member embedded in the circular through slot, and all the wedges 31 are pressed into the corresponding positioning slots 11 together by the elastic force of the annular elastic member.
The invention also discloses a bidirectional overrunning clutch, which is characterized in that: the controllable inclined strut clutch comprises an outer ring 1, an inner ring 2 and two groups of wedge blocks 31 arranged between the outer ring 1 and the inner ring 2, inclined strut directions of the two groups of wedge blocks 31 are opposite, at least one group of wedge blocks 31, the outer ring 1 and the inner ring form the controllable inclined strut clutch, and three states of driving the outer ring, driving the inner ring by the outer ring and disengaging (without mutual interference) the inner ring and the outer ring can be realized by controlling the controllable inclined strut clutch.
The invention has the following beneficial effects:
1) the invention adopts the arc positioning groove arranged on the outer ring of the corresponding wedge block to realize the positioning and installation of the wedge block, and simultaneously can play the role of a retainer of a common sprag clutch, and the wedge block cam is matched with the positioning groove through the molded surface, so that the wedge block can rotate around the circle center of the wedge block cam to realize the lifting of the wedge block relative to the inner ring, and the active control of the sprag clutch is realized.
2) The invention adopts a control mode that a control frame applies torque, all wedge blocks are rotated and swung by stirring, the control frame is contacted with the wedge blocks, the wedge blocks rotate around the arc circle center of a wedge block cam in a positioning groove, and when the control frame is stirred reversely, the wedge blocks can rotate to a normal inclined strut position under the action of an elastic part.
In summary, the controllable diagonal bracing clutch disclosed by the invention realizes the third function of the diagonal bracing clutch, namely that the clutch is lifted and does not transmit torque under the working condition of engagement trend (the inner ring and the outer ring are in a relative motion state which enables the clutch to be engaged), by lifting the wedge block through the control frame on the basis of the engagement and overrunning functions of the common diagonal bracing clutch, so that the wedge block is separated from the wedged roller path; when the clutch needs to be jointed, the control frame applies torque reversely, the auxiliary wedge block is normally jointed according to the working principle of a common inclined strut clutch, and wedging and jointing can be further guaranteed; under the working condition of jointing trend, if jointing is not needed, the control frame acts to lift the wedge block, so that torque is not transmitted between the inner ring and the outer ring. This new clutch structure is with in the voussoir embedding outer loop constant head tank, simultaneously through exerting the constant torque effect on the voussoir at the control panel, ensured that the control panel can lift up the voussoir, can avoid relying on the problem that control panel rotational position mode detected voussoir, control panel position accuracy. The structural space of the novel inclined strut clutch is not greatly changed, and redundant parts do not need to be additionally arranged on the clutch, so that the design and application of the novel inclined strut clutch are facilitated, and conditions are provided for the application of a bidirectional clutch with a multi-overrunning clutch structure.
The invention is further described with reference to the following figures and detailed description.
Drawings
Fig. 1 is a schematic structural diagram of two sets of sprag clutches in a bidirectional overrunning clutch arrangement in an embodiment.
Fig. 2 is a schematic structural diagram of a controllable sprag clutch in an embodiment.
Fig. 3 is a front view of the control frame in the embodiment.
Fig. 4 is a side view of the control rack in an embodiment.
FIG. 5 is a schematic illustration of a sprag of the controllable sprag clutch in an embodiment in an engaged state.
FIG. 6 is a schematic diagram of a sprag of the controllable sprag clutch in an overrunning state in an embodiment.
Fig. 7 is a schematic diagram of a wedge of a controllable sprag clutch in an embodiment in a raised state.
Reference numbers in the figures: 1-outer ring, 11-positioning groove, 2-inner ring, 3-controllable inclined strut clutch, 31-wedge block, 311-upper cam, 312-clamping groove, 313-lower cam, 32-elastic part, 4-common inclined strut clutch, 5-control frame, 51-outer disc, 52-pocket, 53-shifting block and 54-drive pin.
Detailed Description
Examples
Referring to fig. 1, a bidirectional overrunning clutch is shown, two groups of sprag clutches are arranged in the bidirectional overrunning clutch as a combined overrunning clutch structure, and can transmit rotary power from an outer ring 1 to an inner ring 2 and transmit rotary power from the inner ring 2 to the outer ring 1, and in addition, the bidirectional overrunning clutch can realize a disengagement function (the clutches 3 and 4 do not transmit torque) when the controllable sprag clutches are in a working condition of engagement trend.
Specifically, the bidirectional overrunning clutch in fig. 1 includes an outer ring 1, an inner ring 2, a controllable sprag clutch 3, a common sprag clutch 4 and a control frame 5, wherein the outer ring 1 and the inner ring 2 are coaxially assembled, the outer ring 1 is sleeved on the inner ring 2, sprags of the controllable sprag clutch 3 and the common sprag clutch 4 are respectively assembled at two axial positions of an annular space between the outer ring 1 and the inner ring 2, the sprags of the controllable sprag clutch 3 and two groups of sprags of the common sprag clutch 4 are arranged in opposite sprag directions and are respectively used for engaging power transmission of routes from the outer ring 1 to the inner ring 2 and from the inner ring 2 to the outer ring 1, and the control frame 5 is used for actively controlling the sprags of the controllable sprag clutch 3 to disengage under a condition that the sprags are in an engagement trend, so as to realize full disengagement of the bidirectional overrunning clutch. The outer ring 1 and the inner ring 2 can be integrated with external parts, and can also be used as a connecting structure for connecting the external parts by an overrunning clutch.
The common sprag clutch 4 adopts the prior art, the structure and the working process of the common sprag clutch are not described in detail in this embodiment, and two groups of controllable sprag clutches can be respectively and independently controlled in practical application. The controllable sprag clutch 3 in fig. 1 is explained in detail below.
Referring to fig. 2, similar to the common sprag clutch 4, the controllable sprag clutch 3 of this embodiment includes a plurality of sprags 31, the sprags 31 are arranged between the outer ring 1 and the inner ring 2 according to a uniform direction, the sprags refer to radial direction inclined arrangement of the sprags 31 relative to the contact position of the inner ring and the outer ring, so as to realize that the inner ring 2 transmits power to the outer ring 1, when the rotation speed of the inner ring 2 exceeds the outer ring 1, two ends of the sprags 31 respectively abut against and are wedged with the inner ring outer circumferential raceway and the outer ring inner circumferential raceway, power is transmitted to the outer ring 1 through the inner ring 2 to drive the outer ring 1 to rotate, and when the rotation speed of the outer ring 1 exceeds the inner ring 2. The wedge angle of the wedge 31 in this embodiment, in which the lower cam 313 acts on the outer periphery of the inner ring 2, is not more than 3 °, and the wedge angle is the angle between the direction of the pressure transmitted by the inner ring 2 to the wedge lower cam and the radial direction of the inner ring 2.
Referring to fig. 5 in combination, the two ends of the wedge 31 are respectively provided with an upper cam 311 and a lower cam 313 as cam structures abutted to the outer ring 1 and the inner ring 2, which are arc cams, wherein the upper cam 311 is correspondingly contacted to the inner periphery of the outer ring 1, the lower cam 313 is correspondingly contacted to the outer periphery of the inner ring 2, wherein the inner periphery of the outer ring 1 is provided with a plurality of positioning grooves 11 one-to-one corresponding to the wedge 31, the upper cam 311 of the wedge 31 is embedded into the positioning groove 11 and abutted to the outer ring 1, the wedge 31 is pressed into the positioning groove 11 through the elastic member 32, the lower cam 313 of the wedge 31 is directly contacted to the outer periphery of the inner ring 2, the positioning groove 11 realizes the holding arrangement of the wedge 31 in the annular region between the outer ring 1 and the inner ring.
In addition, the positioning slot 11 of this embodiment is an arc slot, the wedge 31 is an arc cam corresponding to the cam structure embedded in the positioning slot, the wedge can be completely installed and embedded in the positioning slot 11, when the wedge 31 swings and lifts, the profile of the upper cam 311 is matched to play a role in positioning and supporting, and the wedge is made to swing approximately around the arc center of the upper cam 311. The radian of the arc groove of the positioning groove 11 is larger than 180 degrees, the wedge block is prevented from sliding out of the groove when being lifted, and two transition guide angles are respectively arranged at two ends of the positioning groove so as to increase the maximum swing angle of the wedge block. And the radian of the arc groove is larger than 180 degrees, so that the wedge block can not slide out of the groove when being lifted, the maximum swinging angle of the wedge block 31 in the positioning groove 11 is increased while the stress concentration is reduced, and the lifting distance of the wedge block from the inner raceway is favorably improved.
The control frame 5 is used for controlling all wedges 31 in the controllable sprag clutch 3 to swing towards the same direction so as to control the lower cam 313 of each wedge 31 to swing and lift relative to the outer peripheral surface of the inner ring 2, so that the wedged state of the wedges of the sprag clutch and the inner ring 2 is eliminated.
Referring to fig. 2, 3 and 4 in combination, the control frame 5 includes an outer disc 51 and a plurality of shifting blocks 53 disposed on the outer disc 51 and distributed along a ring, the outer disc 51 is two sets of ring discs coaxially disposed, the shifting blocks 53 are arranged along a ring portion of the outer disc, two ends of each shifting block are respectively fixedly connected with the two sets of outer discs 51, pockets 52 for accommodating the wedges 31 are formed between adjacent shifting blocks 53, the wedges 31 are disposed in the pockets 52 in a one-to-one correspondence and then assembled between the outer ring 1 and the inner ring 2, the outer discs 51 disposed at two ends of the wedges 31 can also axially limit the wedges, the shifting blocks 53 are disposed between adjacent wedges 31, and when the outer disc 51 of the control frame 5 is rotated in one direction, all the wedges 31 of all the shifting blocks 53 on the outer disc 51 can synchronously swing in the same direction by taking respective upper cam arc center as a shifting point.
The middle of the shifting block 53 on the control frame 5 is protruded to directly contact with one side of the lower cam 313 of the wedge 31, so that the wedge 31 is more easily pushed to swing.
A plurality of transmission pins 54 are arranged on the outer side of one group of outer discs 51 along the circumference, and the control frame 5 is connected with an external control execution device through the transmission pins 54 and transmits the control power for rotating the control frame 5. The external control executive device is a hydraulic actuator cylinder or a servo motor, and drives the control frame 5 and the turning wedge block through constant torque output.
Referring to fig. 2 and 5, the end faces of all the wedges 31 on the same side are provided with slots 312, the slots 312 are arranged in a penetrating manner along the circumferential direction of the clutch, the slots 312 on all the wedges 31 form a continuous circular through groove along the circumferential direction of the clutch, an annular elastic member 32 is embedded in the circular through groove, the annular elastic member 32 can be a spiral spring or a circular elastic snap spring connected end to end, the circumference of the elastic member 32 is slightly larger than the outer diameter of the circular through groove, and all the wedges 31 are pressed and fixed into the positioning groove 11 of the outer ring 1 by the outer length of the annular elastic member. When the control frame 5 controls the wedge 31 to swing back, the elastic element 32 is twisted and deformed, and after the control frame 5 returns back, the elastic element 32 provides the power for returning back the wedge 31.
The operation of the controllable sprag clutch according to the present embodiment will be described in detail with reference to fig. 5, 6 and 7.
For the sake of understanding, the terms "left, right, clockwise, and counterclockwise" appearing below are all expressions based on fig. 2, 5, 6, and 7.
The controllable sprag clutch of the present embodiment has three kinds of operation functions, and when the controllable sprag clutch is in an engaged state, rotational power is input from the inner ring 2 to generate a counterclockwise rotational speed, as shown in fig. 5 (the direction indicated by the arrow in the figure is a positive rotational speed direction, nInner part＞nOuter cover) At this time, the elastic member 32 is wedged in the wedge 31 between the inner ring and the outer ring by the acting force, friction torque in a clockwise direction relative to the rotation center of the wedge 31 is generated between the lower cam 313 of the wedge 31 and the inner ring 2 and between the upper cam 311 of the wedge 31 and the outer ring 1, the wedge 31 gradually swings clockwise by a certain angle, the distance between the upper cam and the lower cam of the wedge 31 relative to the rotation center increases, the normal force between the wedge 31 and the inner ring and the outer ring increases simultaneously, and the friction force is enough to transmit the torque from the inner ring 2 to the outer ring 1 after the wedge 31 is wedged by rotation, at this time, the rotation speeds of the inner ring and the outer ring are synchronous, and the clutch is.
When the controllable sprag clutch is in the overrun state, the rotational power generates a clockwise rotation speed from the inner ring 2, as shown in fig. 6 (the direction indicated by the arrow in the figure is a positive rotation speed direction, nInner part＜nOuter cover) Friction torque in a counterclockwise direction relative to a wedge rotation center is generated between the lower cam 313 of the wedge 31 wedged between the inner ring and the outer ring and between the upper cam 311 and the outer ring 1, the wedge 31 gradually swings counterclockwise by a certain angle, and as the distance between the upper cam and the lower cam of the wedge 31 relative to the rotation center is reduced, normal force between the wedge 31 and the inner ring and the normal force between the wedge 31 and the outer ring are simultaneously reduced until the friction force is sufficiently reduced when the wedge 31 rotates, at the moment, the rotation speeds of the inner ring and the outer ring are asynchronous, the rotation speed of the outer ring 1 exceeds that of the inner ring 2 without interference, and the overrunning function of the clutch is realized, but at the moment, the lower cam 313 of the wedge 31 keeps contact with the periphery of the inner ring 2, and when the rotation speed of the outer ring 1 is less than that of the inner.
When the controllable inclined strut clutch is in the active control separation state, the inner ring and the outer ring are kept relatively static or in the overrunning state as shown in FIG. 7 (the direction indicated by the arrow in the figure is the positive rotating speed direction, nInner part≤nOuter cover) Constant torque drive control by means of an external control actuatorAnd the wedge 31 overcomes the torque of the elastic piece 32 and the friction force between the wedge and the inner ring and the outer ring under the pushing of the control frame 5, swings counterclockwise by taking the circular center of the upper cam arc of the wedge 31 as a rotation center, and stops until the lower cam 313 is separated from the inner ring 2 to a distance of 0.5 mm. At the moment, the rotating speeds of the inner ring and the outer ring are asynchronous and do not interfere with each other. Then, the control frame 5 is driven to rotate anticlockwise by the constant torque of the external control executive device, the right side of the wedge 31 is pushed by the control frame 5 and acted by the torque of the elastic piece 32, the arc circle center of the upper cam of the wedge 31 is taken as a rotation center, the wedge swings back clockwise, the lower cam 313 of the wedge 31 is contacted with the outer peripheral surface of the inner ring 2 again, and at the moment, the controllable inclined strut clutch restores the common working state of the overrunning clutch.
The foregoing is considered as illustrative of the preferred embodiments of the invention and is not to be construed as limiting the invention in any way. Although the present invention has been described with reference to the preferred embodiments, it is not intended to be limited thereto. Those skilled in the art can make numerous possible variations and modifications to the present invention, or modify equivalent embodiments to equivalent variations, without departing from the scope of the invention, using the teachings disclosed above. Therefore, any simple modification, equivalent change and modification made to the above embodiments according to the technical spirit of the present invention should fall within the protection scope of the technical scheme of the present invention, unless the technical spirit of the present invention departs from the content of the technical scheme of the present invention.

Claims (9)

1. Controllable bracing clutch, including outer loop (1) and inner ring (2) of coaxial assembly and arrange along a plurality of voussoirs (31) of unified direction one-way transmission power between outer loop (1) and inner ring (2), its characterized in that:
the wedge block (31) is characterized in that cam structures abutted to the outer ring (1) and the inner ring (2) are respectively arranged at two ends of the wedge block (31), a positioning groove (11) for embedding and positioning a wedge block cam at one end is arranged at the position, corresponding to the abutment position of the wedge block, of the outer ring (1) or the inner ring (2), the wedge block (31) swings around the wedge block cam at the end part, and the wedge block (31) is pressed into the positioning groove (11) through an elastic piece (32);
and the control frame (5) is used for shifting all the wedges (31) to synchronously swing towards the same direction.
2. The controllable sprag clutch according to claim 1, wherein the positioning slot (11) is a circular arc slot, and the cam structure of the wedge (31) corresponding to the positioning slot is a circular arc cam.
3. The controllable sprag clutch according to claim 2, wherein the arc of the positioning slot (11) is greater than 180 ° and a transition chamfer is provided at each end of the positioning slot.
4. Controllable sprag clutch according to claim 1, the wedge angle at which the wedge cam at the other end of the wedge (31) acts on the contact surface not exceeding 3 °.
5. The controllable sprag clutch according to claim 1, wherein the control frame (5) comprises an outer disc (51) and a plurality of shifting blocks (53) arranged on the outer disc (51) and distributed along a circular ring, the shifting blocks (53) are inserted between adjacent sprags one by one, and all the shifting blocks (53) on the outer disc (51) are enabled to shift all the sprags (31) to synchronously swing by rotating the outer disc (51).
6. The controllable sprag clutch according to claim 5, wherein the outer discs (51) are arranged in two groups coaxially, the two ends of the shifting block (53) are fixedly connected with the two groups of outer discs (51), and a pocket (52) for accommodating the wedge block (31) is formed between the adjacent shifting blocks (53).
7. Controllable sprag clutch according to claim 4 or 5 or 6, the outer disc (51) being provided with a drive stud (54) connected to an external control actuator.
8. The controllable sprag clutch according to claim 1, wherein the wedges (31) are provided with locking grooves (312), the locking grooves (312) of all the wedges (31) form a circular through groove, the elastic member (32) is an annular elastic member embedded in the circular through groove, and all the wedges (31) are pressed into the corresponding positioning grooves (11) by the elastic force of the annular elastic member.
9. Two-way freewheel clutch, its characterized in that: comprising an outer ring (1), an inner ring (2) and two sets of sprags (31) arranged between the outer ring (1) and the inner ring (2), the sprag directions of the two sets of sprags (31) being opposite and at least one of the sets of sprags (31) forming with the outer ring (1) and the inner ring a controllable sprag clutch as claimed in claims 1-8.
CN201911011275.4A 2019-10-23 2019-10-23 Controllable inclined strut clutch and bidirectional overrunning clutch applied by same Pending CN110701210A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201911011275.4A CN110701210A (en) 2019-10-23 2019-10-23 Controllable inclined strut clutch and bidirectional overrunning clutch applied by same

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201911011275.4A CN110701210A (en) 2019-10-23 2019-10-23 Controllable inclined strut clutch and bidirectional overrunning clutch applied by same

Publications (1)

Publication Number Publication Date
CN110701210A true CN110701210A (en) 2020-01-17

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11808313B2 (en) 2019-05-20 2023-11-07 Tsubakimoto Chain Co. Cam clutch

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Publication number Priority date Publication date Assignee Title
US11808313B2 (en) 2019-05-20 2023-11-07 Tsubakimoto Chain Co. Cam clutch

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