CN212318590U - Pawl type bidirectional controllable overrunning clutch - Google Patents
Pawl type bidirectional controllable overrunning clutch Download PDFInfo
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- CN212318590U CN212318590U CN202020241538.2U CN202020241538U CN212318590U CN 212318590 U CN212318590 U CN 212318590U CN 202020241538 U CN202020241538 U CN 202020241538U CN 212318590 U CN212318590 U CN 212318590U
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- ring
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Abstract
The utility model discloses a two-way controllable freewheel clutch of pawl formula, wherein, forward pawl and reverse pawl are installed in pairs between inner circle and outer lane, and two pawl roots are installed on the outer lane, two pawl heads and inner circle outside joint, install tab spring between two pawls and the outer lane, and two pawl sides are equipped with pawl control pin, and pawl control pin sliding connection is in the control window that corresponds on the control ring, and under the control surface effect of control window bottom, pawl control pin drives corresponding pawl luffing motion, be equipped with on the outer circumference of control ring with the driven control teeth of a cogwheel of clutch control mechanism meshing, control ring rotary control forward pawl and reverse pawl are connected simultaneously including circling, including the forward pawl joint and reverse pawl and inner circle separation or forward pawl and reverse pawl are simultaneously with the inner circle separation. The utility model discloses can effectively fall and make an uproar on the basis of realizing great power transmission to can realize two-way locking, one-way surging and two-way surging.
Description
Technical Field
The utility model belongs to the technical field of transmission system, concretely relates to two-way controllable freewheel clutch of pawl formula.
Background
The common overrunning clutches include ratchet type overrunning clutches, roller type overrunning clutches and wedge type overrunning clutches, and the common overrunning clutches have the functional purposes of:
1. speed conversion: under the condition that the kinematic chain is uninterrupted, the driven piece can obtain two speeds;
2. preventing reversion: the one-way overrunning clutch transmits torque in one rotation direction and idles under the action of torque in the opposite direction;
3. intermittent motion: the intermittent motion of the driven part can be realized by the proper combination of the bidirectional overrunning clutch and the one-way overrunning clutch.
The overrunning clutch can only realize one-way overrunning based on respective functional characteristics, and the use working conditions are different. The ratchet wheel type overrunning clutch has large transmission torque, but generates noise when overrunning, and cannot be used for high-speed transmission; the wedge type overrunning clutch and the roller overrunning clutch solve the problem of noise in the transmission process, but the cost is low in bearing contact force, and the situation of blocking at a working point position is easily caused by overlarge impact force and long service time.
However, as the transmission member, whether the power that can be transmitted is sufficiently large is an important index for the performance requirement, the ratchet type overrunning clutch has strong development potential, and the problem of transmission noise needs to be considered first.
In order to prevent the ratchet wheel type overrunning clutch from generating noise, in the prior art, a control mechanism is additionally arranged near the ratchet wheel, when the clutch does not need to transmit power, the control mechanism controls the ratchet wheel to move out of a working position to realize noise reduction, and when the clutch needs to transmit power, the ratchet wheel is controlled to return to a normal working position. Although this solution can reduce noise, the structure is complex and requires a large design space.
In addition, there is also a need in existing transmission technology applications for clutches that can control forward or reverse overrunning, such as: in the two-gear gearbox of the electric vehicle, energy recovery is the main function of the electric vehicle, the function requires that normal power output can be realized under the working conditions of forward rotation and reverse rotation of the motor, power is also transmitted back to the motor, the state can be realized in two gears, and the existing overrunning clutch is difficult to meet the requirement.
Disclosure of Invention
To the defect that exists among the above-mentioned prior art, the utility model discloses a two-way controllable freewheel clutch of pawl formula effectively makes an uproar on realizing great power transmission's basis to can realize two-way locking, one-way surging and two-way surging. With the attached drawings, the technical scheme of the utility model is as follows:
the utility model provides a two-way controllable freewheel clutch of pawl formula, includes inner circle 8 and outer lane 3, still includes: a forward folding spring 4, a forward pawl 5, a reverse pawl 6, a reverse folding spring 7 and a control ring 2;
the forward pawl 5 and the reverse pawl 6 are uniformly arranged between the inner ring 8 and the outer ring 3 in pairs, the pawl roots of the forward pawl 5 and the reverse pawl 6 are arranged on the outer ring 3, the pawl heads of the forward pawl 5 and the reverse pawl 6 are clamped with pawl clamping grooves uniformly distributed on the outer side of the inner ring 8, the forward folding spring 4 is connected between the forward pawl 5 and the outer ring 3, the reverse folding spring 7 is connected between the reverse pawl 6 and the outer ring 3, and pawl control pins are vertically arranged on the side surfaces of the forward pawl 5 and the reverse pawl 6;
the control ring 2 is provided with a plurality of groups of control window pairs, each group of control window pairs consists of two control windows which are respectively in one-to-one correspondence with the forward pawls 5 and the reverse pawls 6, the bottom of each control window is a control surface, pawl control pins of the forward pawls 5 and the reverse pawls 6 are inserted into the corresponding control windows, and the pawl control pins are pressed against the control surfaces at the bottoms of the corresponding control windows under the action of the forward folding springs 4 and the reverse folding springs 7;
the outer circumference of the control ring 2 is provided with control gear teeth 202 which are meshed with the clutch control mechanism for transmission so as to control the control ring 2 to rotate;
the control ring 2 controls the forward pawl 5 and the reverse pawl 6 to be simultaneously clamped on the inner ring 8, the forward pawl 5 is clamped on the inner ring 8, and the reverse pawl 6 is separated from the inner ring 8 or the forward pawl 5 and the reverse pawl 6 are simultaneously separated from the inner ring 8, so that bidirectional locking, unidirectional overrunning or bidirectional overrunning of the inner ring 8 and the outer ring 3 is realized.
Further, evenly open along the circumferencial direction on the lateral surface of inner circle 8 has a plurality of pawl draw-in grooves to, every group draw-in groove is to constituteing by two pawl draw-in grooves, two pawl draw-in grooves respectively with the pawl head phase-match of forward pawl 5 and reverse pawl 6, when the draw-in groove of inner circle 8 counter-rotation to arbitrary a set of pawl to the department, the pawl draw-in groove of the assorted joint with it is inside to the pawl draw-in groove that the lateral surface of inner circle 8 corresponds to forward pawl 5 and reverse pawl 6 homoenergetic.
Further, the outer ring 3 is composed of an outer ring 301 and an outer ring inner ring 302;
the outer circumference of the outer ring 301 is provided with a spline structure for matching connection with an external transmission shaft;
the inner side wall of the outer ring inner ring 302 is provided with a plurality of groups of pawl mounting grooves corresponding to the forward pawls 5 and the reverse pawls 6 one by one, and each pawl mounting groove in the pawl mounting groove pair is provided with a folding spring mounting groove.
Furthermore, a control mechanism avoiding groove 305 is formed at a position of the outer ring 301 of the outer ring 3 corresponding to the control gear teeth 202, so as to avoid the control mechanism.
Further, in the control window pair on the control ring 2, the control surface of the forward control window 203 is a forward control window inclined surface 205 and a forward control window plane 206 that are sequentially and continuously arranged along the rotation direction of the control ring 2, the control surface of the reverse control window 204 is a reverse control window inclined surface 207 and a reverse control window inclined surface 208 that are sequentially and continuously arranged along the rotation direction of the control ring 2, wherein the forward control window inclined surface 205 and the reverse control window inclined surface 208 are curved surfaces that are gradually close to the circle center position of the control ring 2 along the rotation direction of the control ring 2, and the forward control window plane 206 and the reverse control window plane 207 are curved surfaces that are concentrically arranged with the control ring 2.
Furthermore, two control rings 2 are respectively arranged on two sides of the forward pawl 5 and the reverse pawl 6, and pawl control pins are vertically arranged on two side faces of the forward pawl 5 and the reverse pawl 6;
the two control rings 2 are relatively fixed through a positioning lock pin and synchronously drive the forward pawl 5 and the reverse pawl 6 to move.
Compared with the prior art, the beneficial effects of the utility model reside in that:
1. the pawl type bidirectional controllable overrunning clutch of the utility model adopts the pawl as the torque transmission component of the inner ring and the outer ring, has large transmission torque and can bear larger load;
2. the pawl type bidirectional controllable overrunning clutch adopts the pawl as an inner ring torque transmission component and an outer ring torque transmission component, and the matching position of the pawl and the clamping groove on the outer wall of the inner ring is accurately controlled by the control ring to realize the combination or separation between the inside and the outside, thereby improving the control effect of the clutch and effectively avoiding the long-term noise problem;
3. the pawl type bidirectional controllable overrunning clutch of the utility model adopts a pawl arrangement structure with opposite directions, and can achieve transmission or overrunning in both forward and reverse directions through reasonable control;
4. the pawl type bidirectional controllable overrunning clutch can effectively avoid the problem of jamming of wedge block type or roller type overrunning clutches;
5. the bidirectional controllable overrunning clutch of pawl type only needs one set of control mechanism to realize the bidirectional control of the clutch.
Drawings
Fig. 1 is a schematic perspective view of a pawl type bi-directional controllable overrunning clutch according to the present invention;
fig. 2 is an exploded view of the pawl type bi-directional controllable overrunning clutch of the present invention;
FIG. 3 is a front view of the pawl type bi-directional controllable overrunning clutch of the present invention;
fig. 4 is a rear view of the pawl type bi-directional controllable overrunning clutch of the present invention;
FIG. 5 is a schematic view of the three-dimensional structure of the control ring in the pawl-type bi-directional controllable overrunning clutch of the present invention
Fig. 6a is a schematic three-dimensional structure diagram of an inner ring in the pawl type bidirectional controllable overrunning clutch according to the present invention;
FIG. 6b is a partial enlarged view of a portion a of FIG. 6 a;
FIG. 7 is a schematic structural view of an outer ring of the pawl type bi-directional controllable overrunning clutch of the present invention;
fig. 8 is a schematic view of a three-dimensional structure of a forward pawl in the pawl-type bi-directional controllable overrunning clutch of the present invention;
fig. 9 is a schematic view of the bidirectional locking of the pawl type bidirectional controllable overrunning clutch according to the present invention;
FIG. 10 is a schematic view of the ratchet type bi-directional controllable overrunning clutch according to the present invention during one-way overrunning;
fig. 11 is a schematic diagram of the pawl type bi-directional controllable overrunning clutch according to the present invention in both directions.
In the figure:
1 a first snap spring, 2 a control ring, 3 an outer ring, 4 a positive folding spring,
5 forward pawl, 6 reverse pawl, 7 reverse folding spring, 8 inner ring,
9 a second clamp spring;
201 control ring body, 202 control gear teeth, 203 forward control window, 204 reverse control window
205 forward control window slope, 206 forward control window plane, 207 reverse control window plane, 208 reverse control window slope;
301 outer ring, 302 outer ring inner ring, 303 forward pawl mounting groove, 304 reverse pawl mounting groove,
305 control mechanism to avoid the slot;
501 pawl body, 502 pawl control pin, 503 folding spring catch, 504 pawl root,
505 a pawl head;
801 forward pawl pockets and 802 reverse pawl pockets.
Detailed Description
For clear and complete description of the technical solution and the specific working process of the present invention, the following embodiments are provided in conjunction with the accompanying drawings of the specification:
as shown in fig. 1, fig. 2, fig. 3 and fig. 4, the utility model discloses a pawl type bidirectional controllable overrunning clutch, which comprises: the device comprises a first clamp spring 1, a control ring 2, an outer ring 3, a forward folding spring 4, a forward pawl 5, a reverse pawl 6, a reverse folding spring 7, an inner ring 8 and a second clamp ring 9. Wherein, the inner circle 8 is installed in 3 inboards in the outer lane, forward pawl 5 and reverse pawl 6 ann are in the annular space between inner circle 8 and outer lane 3, forward folding leaf spring 4 installs between forward pawl 6 and outer lane 3, reverse folding leaf spring 7 installs between reverse pawl 6 and outer lane 3, control ring 2 installs in the axial outside of forward pawl 5 and reverse pawl 6 and is connected with forward pawl 5 and reverse pawl 6 cooperation, with control forward pawl 5 and reverse pawl 6 luffing motion, first jump ring 1 fixed mounting is in 3 front axial outer ends in outer lane, second jump ring 9 fixed mounting is in 3 front axial outer ends in outer lane, first jump ring 1 and second jump ring 9 are used for carrying out axial spacing to the part in the outer lane 3 respectively.
The specific structure of the pawl-type bi-directional controllable overrunning clutch will be further explained below.
As shown in fig. 9, the forward pawls 5 and the reverse pawls 6 are provided in pairs between the outer race 3 and the inner race 8 in the form of pawl pairs, and in the present embodiment, twelve sets of pawl pairs are uniformly distributed in the annular space between the inner race 8 and the outer race 3, and the structures of the forward pawls 5 and the reverse pawls 6 are identical.
The pawl structure will be further described below by taking the forward pawl 5 as an example.
As shown in fig. 8, the forward pawl 5 is composed of a pawl main body 501 and a pawl control pin 502, a folded piece spring slot 503 is formed in the upper surface of the pawl main body 501 and is used for being matched and connected with one end of a corresponding forward folded piece spring 4, the other end of the forward folded piece spring 4 is installed on an outer ring 3, the end with larger diameter size of the pawl main body 501 is a pawl root 504, the pawl root 504 is installed in a matching way with the outer ring 3, the end with larger diameter size of the pawl main body 501 is a pawl head 505, and the pawl head 505 is installed in a matching way with an inner ring 8; the pawl control pin 502 is vertically installed on the outer side surface of the middle part of the pawl main body 501, and the pawl main body 501 swings up and down around the central axis of the pawl root 504 under the drive of the pawl control pin 502, so that the pawl head 505 is controlled to swing up and down.
As shown in fig. 9, the forward pawl spring assembly composed of the forward pawl 5 and the forward folding spring 4 and the reverse pawl spring assembly composed of the reverse pawl 6 and the reverse folding spring 7 are symmetrically installed in the radial direction of the inner ring 8 and the outer ring 3, the forward pawl 5 and the reverse pawl 6 are both obliquely arranged, the forward pawl 5 and the reverse pawl 6 are arranged in a reverse manner, that is, the pawl roots of the forward pawl 5 and the reverse pawl 6 are arranged in a reverse manner, and the pawl heads of the forward pawl 5 and the reverse pawl 6 are arranged in a reverse manner.
As shown in fig. 6a and 6b, the main body of the inner ring 8 is a circular ring structure, a plurality of pawl slot pairs are uniformly arranged on the outer side surface of the inner ring 8 along the circumferential direction, each of the pawl slot pairs is composed of a forward pawl slot 801 and a reverse pawl slot 802, wherein the forward pawl slot 801 is in matched and clamped connection with the pawl head 505 of the forward pawl 5, and the reverse pawl slot 802 is in matched and clamped connection with the pawl head of the reverse pawl 6, as mentioned above, because the forward pawl 5 and the reverse pawl 6 are both obliquely arranged and the pawl heads of the forward pawl 5 and the reverse pawl 6 are reversely arranged, the notches of the forward pawl slot 801 and the reverse pawl slot 802 are obliquely and reversely symmetrically arranged. When the inner ring 8 rotates, no matter where the inner ring rotates, the forward pawl 5 and the reverse pawl 6 can find a pawl clamping groove matched and clamped with the pawl clamping groove in the corresponding pawl clamping groove pair on the outer side surface of the inner ring 8; the outer side wall of the inner ring 8 is provided with a spline structure for matching connection with a transmission shaft on one side of a transmission system.
As shown in fig. 7, the outer ring 3 is an integral circular ring structure composed of an outer ring 301 and an outer ring inner ring 302; the outer circumference of the outer ring 301 is provided with a spline structure for matching connection with a transmission shaft on the other side of the transmission system; the inner side wall of the outer ring inner ring 302 is provided with a plurality of mounting grooves for matching and mounting the forward pawl 5 and the reverse pawl 6.
Twelve groups of pawl mounting groove pairs are formed on the inner side surface of the outer ring inner ring 302, the twelve groups of pawl mounting groove pairs are respectively in one-to-one correspondence with twelve groups of pawl pairs consisting of forward pawls 5 and reverse pawls 6, each group of pawl mounting groove pairs consists of a forward pawl mounting groove 303 and a reverse pawl mounting groove 304, the forward pawls 5 in the pawl pairs are correspondingly mounted in the forward pawl mounting grooves 303, the reverse pawls 6 are correspondingly mounted in the reverse pawl mounting grooves 304, as described above, the forward pawls 5 and the reverse pawls 6, the root parts of the forward pawl 5 and the reverse pawl 6 are arranged oppositely, and the pawl heads of the forward pawl 5 and the reverse pawl 6 are arranged reversely, therefore, the forward pawl mounting groove 303 and the reverse pawl mounting groove 304 are identical in construction and opposite in direction, and the forward pawls 5 and the reverse pawls 6 are mounted in the forward pawl mounting grooves 303 and the reverse pawl mounting grooves 304 in the same manner.
Taking the forward pawl 5 and the forward pawl mounting groove 303 as an example, as shown in fig. 7 and 8, one end in the forward pawl 5 mounting groove 303 is an arc-shaped groove surface matched with the outer contour of the pawl root 504 of the forward pawl 5, the pawl root 504 is mounted in the arc-shaped groove surface, and the pawl root 504 relatively rotates in the arc-shaped groove surface under the driving of external force; a fold-flap spring mounting groove is formed in the middle of the inside of the forward pawl mounting groove 303, one end of a forward fold-flap spring 6 is mounted in the fold-flap spring mounting groove, and the other end of the forward fold-flap spring 6 is clamped in a fold-flap spring clamping groove 503 on the upper surface of the forward pawl 5; the other end in the forward pawl mounting groove 303 leaves a necessary space for the pawl head 505 of the forward pawl 5 to prevent interference with the outer race inner ring 302 when the pawl head 505 of the forward pawl 5 is raised.
As shown in fig. 5, the control ring main body 201 of the control ring 2 is an annular plate structure, twelve groups of control window pairs are opened on the control ring main body 201, the twelve groups of control window pairs are respectively in one-to-one correspondence with twelve groups of pawl pairs consisting of forward pawls 5 and reverse pawls 6, each group of control window pairs consists of a forward control window 203 and a reverse control window 204, the forward control window 203 is connected with a pawl control pin 502 of the forward pawl 5 in a matching manner, and the reverse control window 204 is connected with a pawl control pin of the reverse pawl 6 in a matching manner; the matched connection of the control window and the pawl control pin means that the pawl control pin is inserted into the control window and is connected with the bottom control surface of the control window, and in the process of abutting against the bottom control surface of the control window, the pawl control pin is controlled by the bottom control surface of the control window to move, so that the pawl control pin is lifted, and then the corresponding pawl is controlled by the pawl control pin to swing up and down, so that the swing mode of the pawl depends on the design of the bottom control surface of the control window, and the shape of the corresponding control surface can be designed according to the actual working condition to realize different working modes; in this embodiment, the control ring 2 is set to rotate clockwise relative to the forward pawls 5 and the reverse pawls 6 distributed in a ring shape, and then the pawls are controlled to swing correspondingly by the pawl control pins, and accordingly, the swinging modes of the forward pawls 5 and the reverse pawls 6 are designed as follows: firstly: the forward pawl 5 and the reverse pawl 6 are both at the lowest position; then: the forward pawl 5 is held at the lowest position and the reverse pawl 6 is gradually raised to the highest position; and finally: the forward pawl 5 is gradually raised to the uppermost position and the reverse pawl 6 is held at the uppermost position. In match, the control window pair on the control ring has the following structure:
as shown in fig. 5, twelve groups of control window pairs are formed on the control ring main body 201 of the control ring 2, the twelve groups of control window pairs are respectively in one-to-one correspondence with twelve groups of pawl pairs consisting of forward pawls 5 and reverse pawls 6, each group of control window pairs consists of a forward control window 203 and a reverse control window 204, the forward control window 203 is in fit connection with a pawl control pin 502 of the forward pawl 5, and the reverse control window 204 is in fit connection with a pawl control pin of the reverse pawl 6; the control surface at the bottom of the forward control window 203 comprises a forward control window inclined plane 205 and a forward control window plane 206 which are sequentially arranged clockwise (namely, the same rotation direction as the control ring 2), the forward control window inclined plane 205 and the reverse control window plane 206 are continuous without blocking, wherein the forward control window inclined plane 205 is an arc surface which is gradually far away from the circle center of the control ring 2 anticlockwise (namely, opposite to the rotation direction of the control ring 2), and the forward control window plane 206 is an arc surface which is concentrically arranged with the control ring 2; the control surface at the bottom of the reverse control window 204 comprises a reverse control window plane 207 and a reverse control window inclined plane 208 which are sequentially arranged clockwise (i.e. the same rotation direction as the control ring 2), and the reverse control window plane 207 and the reverse control window inclined plane 208 are continuous without blocking, wherein the reverse control window plane 207 is an arc surface which is concentrically arranged with the control ring 2, and the reverse control window inclined plane 208 is an arc surface which is gradually away from the circle center position of the control ring 2 anticlockwise (i.e. the opposite rotation direction of the control ring 2). The forward control window bevel 205 and the reverse control window bevel 207 have the same length, and the forward control window bevel 206 and the reverse control window bevel 208 have the same length.
Similarly, when the pawl control pin of the reverse pawl 6 is inserted into the reverse control window 204, the pawl control pin of the reverse pawl 6 is always pressed against the control surface of the reverse control window 204 under the elastic force of the reverse spring 304, and the pawl control pin of the forward pawl 6 is always pressed against the control surface of the forward control window 203 under the elastic force of the reverse spring 304 when the pawl control pin of the forward pawl 5 is inserted into the forward control window 203.
As shown in fig. 9, in the initial position, the pawl control pin of the forward pawl 5 is at the rightmost end of the forward control window plane 206 of the forward control window 203, where the forward pawl 5 is at the lowest position, and the pawl control pin of the reverse pawl 6 is at the rightmost end of the reverse control window slope 208 of the reverse control window 204, where the reverse pawl 6 is also at the lowest position;
as the control ring 2 rotates clockwise, as shown in fig. 10, the pawl control pin of the forward pawl 5 moves under the action of the forward control window plane 206 of the control ring 2, since the forward control window plane 206 is disposed coaxially with the control ring 2, the pawl control pin of the forward pawl 5 has no movement in the radial direction of the control ring 2, so that the forward pawl 5 is always kept at the lowest position (i.e., the position closest to the center of the control ring 2), at the same time, the pawl control pin of the reverse pawl 6 is moved by the reverse control window slope 208 of the control ring 2, because the reverse control window inclined plane 208 gradually moves away from the center of the control ring 2 along the counterclockwise direction, as the control ring 2 rotates clockwise, the pawl control pin of the reverse pawl 6 gradually moves away from the center of the control ring 2 along the radial direction of the control ring 2, and the reverse pawl 6 is gradually lifted under the driving of the pawl control pin of the reverse pawl 6; when the pawl control pin of the forward pawl 5 is located at the junction of the forward control window plane 206 and the forward control window slope, the forward pawl 5 is still at the lowest position, and at the moment, the pawl control pin of the reverse pawl 6 is located at the junction of the reverse control window plane 207 and the reverse control window slope, and at the moment, the reverse pawl 6 rises to the highest position (i.e., the position farthest from the center of the control ring);
as shown in fig. 11, as the control ring 2 continues to rotate clockwise, the pawl control pin of the forward pawl 5 starts to move under the action of the forward control window inclined plane 205 of the control ring 2, and as the forward control window inclined plane 205 gradually moves away from the center of the control ring 2 in the counterclockwise direction, as the control ring 2 continues to rotate clockwise, the pawl control pin of the forward pawl 5 gradually moves away from the center of the control ring 2 in the radial direction of the control ring 2, and the forward pawl 5 gradually rises under the driving of the pawl control pin of the forward pawl 5 until the pawl control pin moves to the leftmost end of the forward control window inclined plane 205, at which time the forward pawl 5 rises to the highest position (i.e., the position farthest from the center of the control ring); at the same time, the pawl control pin of the reverse pawl 6 moves under the action of the reverse control window plane 207 of the control ring 2, and since the reverse control window plane 207 is coaxially arranged with the control ring 2, the pawl control pin of the reverse pawl 6 does not move in the radial direction of the control ring 2, and the reverse pawl 6 is held at the highest position.
As shown in fig. 9, when the pawl control pins of the forward pawl 5 and the reverse pawl 6 are located at the rightmost end of the control window pair of the control ring 2, at this time, the forward pawl 5 and the reverse pawl 6 are located at the lowest position, the pawl head of the forward pawl 5 is clamped in the forward pawl clamping groove 801 of one pawl clamping groove pair of the inner ring 8, the pawl head of the reverse pawl 6 is clamped in the reverse pawl clamping groove 802 of the other pawl clamping groove pair of the inner ring 8, and the pawl heads of the forward pawl 5 and the reverse pawl 6 are arranged in the reverse direction, so that the inner ring 8 and the outer ring 3 are locked in the clockwise direction and the counter-clockwise direction, and at this time, power transmission can be performed in the clockwise direction and the counter-clockwise direction between the inner ring 8 and the outer ring 3.
As shown in fig. 10, in the process that the pawl control pin of the forward pawl 5 moves from the rightmost end of the forward control window plane 206 to the boundary between the forward control window plane 206 and the forward control window inclined plane 205 along with the clockwise rotation of the control ring 2, the forward pawl 5 does not move along the radial direction of the control ring 2 and is always at the lowest position, that is, the forward pawl 5 is kept clamped in the forward pawl clamping groove 801 of the inner ring 8, meanwhile, the reverse pawl 6 moves from the rightmost end of the reverse control window inclined plane 208 to the boundary between the reverse control window plane 207 and the reverse control window inclined plane 208, in the process, the reverse pawl 6 is lifted upwards to the highest position, at this time, the pawl head of the reverse pawl 6 is separated from the reverse pawl clamping groove 802 of the inner ring 8, at this time, the inner ring 8 is locked clockwise relative to the outer ring 3 and can rotate counterclockwise relatively freely, that is, that no power transmission is generated when the inner ring 8 rotates counterclockwise, when the inner ring 8 rotates clockwise relative to the outer ring 3, power can be transmitted, namely the clutch realizes one-way overrunning.
As shown in fig. 11, as the control ring 2 continues to rotate clockwise, when the pawl control pins of the forward pawl 5 and the reverse pawl 6 both move to the leftmost end of the control window pair of the control ring 2, the forward pawl 5 and the reverse pawl 6 are both at the highest positions, the pawl heads of the forward pawl 5 and the reverse pawl 6 are respectively disengaged from the forward pawl slot 801 and the reverse pawl slot 802 of the inner ring 8, at this time, both the inner ring 8 and the outer ring 3 can rotate freely in the clockwise direction and the counterclockwise direction, at this time, both the inner ring 8 and the outer ring 3 do not have power transmission in the clockwise direction and the counterclockwise direction, that is, the clutch realizes bidirectional overrunning.
In addition, as shown in fig. 3 and 4, in the present embodiment, only one control ring 2 is installed at one axial outer end of the forward pawl 5 and the reverse pawl 6 in a matching manner, in addition, one control ring 2 can also be installed at the other axial outer end of the forward pawl 5 and the reverse pawl 6 in a matching manner, pawl control pins 502 are vertically arranged on two outer side surfaces of the middle portion of the pawl main body 501 of the forward pawl 5 and the reverse pawl 6, the two control rings 2 are completely identical in structure and symmetrically arranged, and the two control rings 2 are relatively fixed through positioning lock pins, so that the two control rings 2 synchronously drive the forward pawl 5 and the reverse pawl 6 to swing up and down, and the forward pawl 5 and the reverse pawl 6 are ensured to be stressed evenly without unbalance loading.
To sum up, the overrunning clutch of the present invention controls the corresponding pawl motion through the rotation of the control ring 2 to further achieve the locking or separation between the inner ring 8 and the outer ring 3, so as to control the rotation of the control ring 2, as shown in fig. 5, a sector-shaped control gear tooth 202 is arranged on the outer side of the circumference of the control ring 2, and the control gear tooth 202 is meshed with the driving gear in the gear pair type control mechanism to achieve the power transmission, or meshed with the rack in the gear pair type control mechanism to achieve the power transmission, or meshed with the worm and gear type control mechanism to achieve the power transmission; correspondingly, as shown in fig. 7, an arc-shaped control mechanism avoiding groove 305 is formed in the outer ring 301 of the outer ring 3 at a position corresponding to the control gear teeth 202, so as to avoid the control mechanism.
Claims (6)
1. The utility model provides a two-way controllable freewheel clutch of pawl formula, includes inner circle (8) and outer lane (3), its characterized in that:
further comprising: the device comprises a forward folding spring (4), a forward pawl (5), a reverse pawl (6), a reverse folding spring (7) and a control ring (2);
the forward pawl (5) and the reverse pawl (6) are uniformly arranged between the inner ring (8) and the outer ring (3) in pairs, the pawl roots of the forward pawl (5) and the reverse pawl (6) are arranged on the outer ring (3), the pawl heads of the forward pawl (5) and the reverse pawl (6) are clamped with pawl clamping grooves uniformly distributed on the outer side of the inner ring (8), a forward folding spring (4) is connected between the forward pawl (5) and the outer ring (3), a reverse folding spring (7) is connected between the reverse pawl (6) and the outer ring (3), and pawl control pins are vertically arranged on the side surfaces of the forward pawl (5) and the reverse pawl (6);
the control ring (2) is provided with a plurality of groups of control window pairs, each group of control window pairs consists of two control windows which are respectively in one-to-one correspondence with the forward pawl (5) and the reverse pawl (6), the bottom of each control window is a control surface, pawl control pins of the forward pawl (5) and the reverse pawl (6) are inserted into the corresponding control windows, and the pawl control pins are pressed against the control surfaces at the bottoms of the corresponding control windows under the action of the forward folding springs (4) and the reverse folding springs (7);
the outer circumference of the control ring (2) is provided with control gear teeth (202) which are meshed with the clutch control mechanism for transmission so as to control the control ring (2) to rotate;
the control ring (2) controls the forward pawl (5) and the reverse pawl (6) to be simultaneously clamped on the inner ring (8), the forward pawl (5) is clamped on the inner ring (8) and the reverse pawl (6) is separated from the inner ring (8) or the forward pawl (5) and the reverse pawl (6) are simultaneously separated from the inner ring (8), so that bidirectional locking, unidirectional overrunning or bidirectional overrunning of the inner ring (8) and the outer ring (3) is realized.
2. A pawl-type bi-directionally controllable overrunning clutch according to claim 1, wherein:
evenly open along the circumferencial direction on the lateral surface of inner circle (8) has a plurality of pawl draw-in grooves to, every group draw-in groove is to constituteing by two pawl draw-in grooves, two pawl draw-in grooves respectively with the pawl head phase-match of forward pawl (5) and reverse pawl (6), when the draw-in groove of inner circle (8) pair department to arbitrary a set of pawl, the pawl draw-in groove of matching joint is inwards found to forward pawl (5) and reverse pawl (6) homoenergetic at the pawl draw-in groove that inner circle (8) lateral surface corresponds.
3. A pawl-type bi-directionally controllable overrunning clutch according to claim 1, wherein:
the outer ring (3) consists of an outer ring (301) and an outer ring inner ring (302);
the outer circumferential surface of the outer ring (301) is provided with a spline structure which is used for being connected with an external transmission shaft in a matching way;
the inner side wall of the outer ring inner ring (302) is provided with a plurality of groups of pawl mounting groove pairs which are in one-to-one correspondence with the forward pawls (5) and the reverse pawls (6), and each pawl mounting groove in the pawl mounting groove pairs is internally provided with a folding spring mounting groove.
4. A pawl-type bi-directionally controllable overrunning clutch according to claim 3, wherein:
and a control mechanism avoiding groove (305) is formed in the position, corresponding to the control gear teeth (202), of the outer ring (301) of the outer ring (3) so as to realize avoidance of the control mechanism.
5. A pawl-type bi-directionally controllable overrunning clutch according to claim 1, wherein:
control window centering on control ring (2), the control surface of forward control window (203) is forward control window inclined plane (205) and forward control window plane (206) that set up in proper order in succession along control ring (2) direction of rotation, and the control surface of reverse control window (204) is reverse control window plane (207) and reverse control window inclined plane (208) that set up in succession in proper order along control ring (2) direction of rotation, and wherein, forward control window inclined plane (205) and reverse control window inclined plane (208) are the curved surface that is close to control ring (2) centre of a circle position gradually along control ring (2) direction of rotation, and forward control window plane (206) and reverse control window plane (207) are the curved surface that sets up with control ring (2) are concentric.
6. A pawl-type bi-directionally controllable overrunning clutch according to claim 1, wherein:
two control rings (2) are respectively arranged on two sides of the forward pawl (5) and the reverse pawl (6), and pawl control pins are vertically arranged on two side faces of the forward pawl (5) and the reverse pawl (6) in a matching manner;
the two control rings (2) are relatively fixed through a positioning lock pin and synchronously drive the forward pawl (5) and the reverse pawl (6) to move.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020241538.2U CN212318590U (en) | 2020-03-03 | 2020-03-03 | Pawl type bidirectional controllable overrunning clutch |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020241538.2U CN212318590U (en) | 2020-03-03 | 2020-03-03 | Pawl type bidirectional controllable overrunning clutch |
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| Publication Number | Publication Date |
|---|---|
| CN212318590U true CN212318590U (en) | 2021-01-08 |
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| CN202020241538.2U Expired - Fee Related CN212318590U (en) | 2020-03-03 | 2020-03-03 | Pawl type bidirectional controllable overrunning clutch |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111271392A (en) * | 2020-03-03 | 2020-06-12 | 吉林大学 | Pawl type bidirectional controllable overrunning clutch |
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- 2020-03-03 CN CN202020241538.2U patent/CN212318590U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111271392A (en) * | 2020-03-03 | 2020-06-12 | 吉林大学 | Pawl type bidirectional controllable overrunning clutch |
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Granted publication date: 20210108 |