CN111271392A - Pawl type two-way controllable overrunning clutch - Google Patents

Abstract

The invention discloses a pawl type bidirectional controllable overrunning clutch, wherein a forward pawl and a reverse pawl are arranged between an inner ring and an outer ring in pairs, the roots of the two pawls are arranged on the outer ring, the heads of the two pawls are clamped with the outer side of the inner ring, a fold spring is arranged between the two pawls and the outer ring, pawl control pins are arranged on the side surfaces of the two pawls and are connected in corresponding control windows on a control ring in a sliding manner, the pawl control pins drive the corresponding pawls to swing up and down under the action of a control surface at the bottom of the control windows, control gear teeth which are meshed with a clutch control mechanism and driven are arranged on the outer circumference of the control ring, the control ring controls the forward pawl and the reverse pawl to be simultaneously clamped on the inner ring, the forward pawl is clamped on the inner ring, and the reverse pawl is separated from the inner ring or the forward pawl and the. The invention can effectively reduce noise on the basis of realizing larger power transmission, and can realize bidirectional locking, unidirectional overrunning and bidirectional overrunning.

Description

Pawl type two-way controllable overrunning clutch

technical field

The invention belongs to the technical field of transmission systems, and in particular relates to a pawl type bidirectional controllable overrunning clutch.

Background technique

Commonly used types of overrunning clutches are ratchet type overrunning clutches, roller type overrunning clutches and sprag type overrunning clutches, and their functional uses include:

1. Transformation speed: in the case of uninterrupted kinematic chain, the follower can obtain two speeds of fast and slow;

2. Prevent reverse rotation: the one-way overrunning clutch transmits torque in one direction of rotation, while idling under the action of torque in the opposite direction;

3. Intermittent motion: Through the proper combination of the two-way overrunning clutch and the one-way overrunning clutch, the driven part can perform a certain regular intermittent motion.

Based on their respective functional characteristics, the above-mentioned overrunning clutches can only achieve one-way overrunning, and the working conditions are different. Among them, the ratchet-type overrunning clutch has a large transmission torque, but it will make noise when overrunning, so it cannot be used in high-speed transmission; the wedge-type overrunning clutch and the roller overrunning clutch solve the noise problem in the transmission process, but the cost is to bear The contact force is small, and it is easy to be stuck at the working point due to excessive impact force and long use time.

However, as a transmission component, whether the power it can transmit is large enough is an important indicator of its performance requirements. Therefore, the ratchet-type overrunning clutch has strong development potential, and the first thing to consider is the transmission noise problem.

In order to prevent the ratchet type overrunning clutch from making noise, in the prior art, a control mechanism is added near the ratchet wheel. When the clutch does not need to transmit power, the control mechanism will control the ratchet wheel to move out of the working position to achieve noise reduction, and when the clutch needs to transmit power, Then control the ratchet back to the normal working position. Although this solution can reduce noise, the structure is complex and requires a large design space.

In addition, in the existing transmission technology application field, a clutch capable of controlling forward or reverse overrun is also required. For example, in a two-speed gearbox for electric vehicles, energy recovery is its main function. The normal power output can be achieved in the reverse rotation condition, and the power must be transmitted back to the motor. This state can be achieved in both gears, and the existing overrunning clutch is difficult to meet this requirement.

SUMMARY OF THE INVENTION

In view of the above-mentioned defects in the prior art, the present invention discloses a pawl-type two-way controllable overrunning clutch, which can effectively reduce noise on the basis of realizing large power transmission, and can realize two-way locking, one-way overrunning and Two-way transcendence. In conjunction with the accompanying drawings, the technical solutions of the present invention are as follows:

A pawl-type two-way controllable overrunning clutch includes an inner ring 8 and an outer ring 3, and also includes: a forward flap spring 4, a forward pawl 5, a reverse pawl 6, a reverse flap spring 7 and a control ring 2;

The forward pawl 5 and the reverse pawl 6 are evenly installed in pairs between the inner ring 8 and the outer ring 3, and the pawl roots of the forward pawl 5 and the reverse pawl 6 are installed on the outer ring 3, The pawl heads of the forward pawl 5 and the reverse pawl 6 are engaged with the pawl slots evenly distributed on the outside of the inner ring 8, and the forward flap spring 4 is connected between the forward pawl 5 and the outer ring 3. During the time, the reverse flap spring 7 is connected between the reverse pawl 6 and the outer ring 3, and a pawl control pin is vertically provided on the sides of the forward pawl 5 and the reverse pawl 6;

The control ring 2 is provided with several groups of control window pairs, each group of control window pairs is composed of two control windows corresponding to the forward pawl 5 and the reverse pawl 6 respectively, and the bottom of the control window is composed of two control windows. For the control surface, the pawl control pins of the forward pawl 5 and the reverse pawl 6 are inserted into the corresponding control windows. Under the action of the forward flap spring 4 and the reverse flap spring 7, the pawl control pin Press the top on the control surface at the bottom of the corresponding control window;

The outer circumference of the control ring 2 is provided with control gear teeth 202, which are engaged with the clutch control mechanism for transmission to control the rotation of the control ring 2;

The control ring 2 controls the forward pawl 5 and the reverse pawl 6 to be clamped on the inner ring 8 at the same time, the forward pawl 5 is clamped to 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 separated from the inner ring 4 at the same time, so that the inner ring 8 and the outer ring 3 can be locked in both directions, one-way overrun or two-way overrun.

Further, several pairs of pawl clamping grooves are evenly opened on the outer surface of the inner ring 8 along the circumferential direction, and each group of clamping groove pairs is composed of two pawl clamping grooves, and the two pawl clamping grooves are respectively connected to the positive direction. The pawl heads of the pawl 5 and the reverse pawl 6 are matched, and when the groove pair of the inner ring 8 rotates to any set of pawl pairs, both the forward pawl 5 and the reverse pawl 6 can be in In the pair of ratchet grooves corresponding to the outer surface of the inner ring 8, a matching ratchet groove is found.

Further, the outer ring 3 is composed of an outer ring outer ring 301 and an outer ring inner ring 302;

The outer circumferential surface of the outer ring 301 of the outer ring is provided with a spline structure for matching connection with the external transmission shaft;

The inner side wall of the inner ring 302 of the outer ring is provided with several sets of pawl installation groove pairs corresponding to the forward pawl 5 and the reverse pawl 6 one-to-one, in each pawl installation groove of the pair of pawl installation grooves There is a slot for installing the flap spring.

Further, at the position of the outer ring 301 of the outer ring 3 corresponding to the control gear teeth 202 , a control mechanism avoidance groove 305 is opened to realize the avoidance of the control mechanism.

Further, in the control window pair on the control loop 2, the control surface of the forward control window 203 is the forward control window inclined plane 205 and the forward control window plane 206 that are successively arranged along the rotation direction of the control ring 2, and the reverse The control surface of the control window 204 is the reverse control window plane 207 and the reverse control window slope 208 which are successively arranged along the rotation direction of the control ring 2, wherein the forward control window slope 205 and the reverse control slope 208 are both along the control The rotation direction of the ring 2 is gradually approaching the curved surface at the center of the control ring 2 . The forward control window plane 206 and the reverse control window plane 207 are both curved surfaces concentric with the control ring 2 .

Further, there are two control rings 2 , which are respectively installed on both sides of the forward pawl 5 and the reverse pawl 6 . Matchingly, the two sides of the forward pawl 5 and the reverse pawl 6 All are vertically provided with pawl control pins;

The two control rings 2 are relatively fixed by the positioning lock pins, and synchronously drive the forward pawl 5 and the reverse pawl 6 to move.

Compared with the prior art, the beneficial effects of the present invention are:

1. The pawl-type two-way controllable overrunning clutch of the present invention adopts the pawl as the torque transmission component of the inner and outer rings, and its transmission torque is large and can bear a large load;

2. The pawl-type two-way controllable overrunning clutch of the present invention adopts the pawl as the torque transmission component of the inner and outer rings, and the control ring accurately controls the matching position of the pawl and the groove on the outer wall of the inner ring to realize the combination or separation of the inner and outer fronts, and lift the clutch. control effect, and can effectively avoid long-term noise problems;

3. The pawl type two-way controllable overrunning clutch of the present invention adopts the pawl arrangement structure in the opposite direction, and can achieve forward and reverse transmission or overrun through reasonable control;

4. The pawl type two-way controllable overrunning clutch of the present invention can effectively avoid the stuck problem of the wedge type or roller type overrunning clutch;

5. The pawl-type two-way controllable overrunning clutch of the present invention only needs one set of control mechanisms to realize the two-way control of the clutch.

Description of drawings

Fig. 1 is the three-dimensional structure schematic diagram of the pawl type two-way controllable overrunning clutch of the present invention;

Fig. 2 is the exploded exploded view of the pawl type two-way controllable overrunning clutch of the present invention;

Fig. 3 is the front view of the pawl type bidirectional controllable overrunning clutch of the present invention;

Fig. 4 is the rear view of the pawl type two-way controllable overrunning clutch of the present invention;

FIG. 5 is a three-dimensional structural diagram of the control ring in the pawl type two-way controllable overrunning clutch of the present invention

Figure 6a is a three-dimensional structural schematic diagram of the inner ring in the pawl type bidirectional controllable overrunning clutch of the present invention;

Fig. 6b is a partial enlarged view at a in Fig. 6a;

7 is a schematic structural diagram of the outer ring in the pawl type bidirectional controllable overrunning clutch of the present invention;

8 is a schematic diagram of the three-dimensional structure of the forward pawl in the pawl type bidirectional controllable overrunning clutch of the present invention;

9 is a schematic diagram of the pawl type two-way controllable overrunning clutch of the present invention when it is two-way locked;

10 is a schematic diagram of the pawl type two-way controllable overrunning clutch of the present invention when overrunning in one direction;

11 is a schematic diagram of the pawl type bidirectional controllable overrunning clutch of the present invention when it is bidirectional.

In the picture:

1 first circlip, 2 control ring, 3 outer ring, 4 positive flap spring,

5 forward pawl, 6 reverse pawl, 7 reverse flap spring, 8 inner ring,

9 second circlip;

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 outer ring, 302 outer ring inner ring, 303 forward pawl installation groove, 304 reverse pawl installation groove,

305 Control mechanism avoidance groove;

501 pawl body, 502 pawl control pin, 503 leaf spring clip, 504 pawl root,

505 pawl head;

801 forward pawl slot, 802 reverse pawl slot.

Detailed ways

In order to clearly and completely describe the technical solution of the present invention and its specific working process, with reference to the accompanying drawings, the specific embodiments of the present invention are as follows:

As shown in Figure 1, Figure 2, Figure 3 and Figure 4, the present invention discloses a pawl type two-way controllable overrunning clutch, comprising: a first retaining spring 1, a control ring 2, an outer ring 3, a positive flap Spring 4 , forward pawl 5 , reverse pawl 6 , reverse flap spring 7 , inner ring 8 and second snap ring 9 . Among them, the inner ring 8 is installed on the inner side of the outer ring 3, the forward pawl 5 and the reverse pawl 6 are installed in the annular space between the inner ring 8 and the outer ring 3, and the forward flap spring 4 is installed on the forward pawl 6 and the outer ring 3, the reverse flap spring 7 is installed between the reverse pawl 6 and the outer ring 3, the control ring 2 is installed on the axial outer side of the forward pawl 5 and the reverse pawl 6 and is connected with the reverse pawl 6 and the outer ring 3. The forward pawl 5 and the reverse pawl 6 are matched and connected to control the forward and reverse pawls 5 and 6 to swing up and down. 9 is fixedly installed on the outer end of the front face of the outer ring 3, and the first circlip 1 and the second circlip 9 are respectively used to limit the axial position of the components in the outer ring 3.

The specific composition and structure of the pawl type bidirectional controllable overrunning clutch will be further elaborated below.

As shown in FIG. 9 , the forward pawl 5 and the reverse pawl 6 are installed in pairs between the outer ring 3 and the inner ring 8 in the form of a pawl pair. In this specific embodiment, there are twelve groups of pawls The pawl pairs are evenly distributed in the annular space between the inner ring 8 and the outer ring 3 , and the structures of the forward pawl 5 and the reverse pawl 6 are exactly the same.

The structure of the pawl is further described below by taking the positive pawl 5 as an example.

As shown in FIG. 8 , the positive pawl 5 is composed of a pawl body 501 and a pawl control pin 502. The upper surface of the pawl body 501 is provided with a flap spring slot 503, which is used for the corresponding positive folding One end of the leaf spring 4 is matched and connected, and the other end of the positive folded leaf spring 4 is installed on the outer ring 3. The larger diameter of the pawl body 501 is the pawl root 504. The pawl root 504 is installed in cooperation with the outer ring 3. The larger diameter end of the main body 501 is the pawl head 505, and the pawl head 505 is installed in cooperation with the inner ring 8; Driven by the driving, the pawl body 501 swings up and down around the central axis of the pawl root 504, thereby controlling the pawl head 505 to swing up and down.

As shown in FIG. 9 , the forward pawl spring assembly composed of the forward pawl 5 and the forward flap spring 4 and the reverse pawl spring assembly composed of the reverse pawl 6 and the reverse flap spring 7 are relative to the inner The radially symmetrical installation of the ring 8 and the outer ring 3, the forward pawl 5 and the reverse pawl 6 are arranged obliquely, and the forward pawl 5 and the reverse pawl 6 are arranged opposite to each other, that is, the forward pawl 5 and the reverse pawl 6 are arranged opposite to each other. The pawl roots of the reverse pawl 6 are arranged opposite to each other, and the pawl heads of the forward pawl 5 and the reverse pawl 6 are arranged in opposite directions.

As shown in Figures 6a and 6b, the main body of the inner ring 8 is a ring structure, and the outer surface of the inner ring 8 is evenly provided with several pairs of pawl clamping grooves along the circumferential direction, and each group of clamping groove pairs is formed by the positive direction. The pawl slot 801 and the reverse pawl slot 802 are formed, wherein the forward pawl slot 801 is engaged with the pawl head 505 of the forward pawl 5, and the reverse pawl slot 802 is connected to the reverse pawl 505. The pawl heads of the pawls 6 are engaged with each other. As mentioned above, since both the forward pawl 5 and the reverse pawl 6 are inclined, and the pawl heads of the forward pawl 5 and the reverse pawl 6 are reversed. Therefore, correspondingly, the slots of the forward pawl engaging slot 801 and the reverse pawl engaging slot 802 are inclined and symmetrically arranged. When the inner ring 8 rotates, no matter where it is rotated, the forward pawl 5 and the reverse pawl 6 can find the matching pawl in the pair of pawl grooves corresponding to the outer side of the inner ring 8 The slot; the outer side wall of the inner ring 8 is provided with a spline structure, which is used for matching connection with the transmission shaft on one side of the transmission system.

As shown in FIG. 7 , the outer ring 3 is an integral ring structure composed of an outer ring outer ring 301 and an outer ring inner ring 302; wherein, the outer peripheral surface of the outer ring outer ring 301 is provided with splines The structure is used for matching connection with the transmission shaft on the other side of the transmission system; the inner side wall of the inner ring 302 of the outer ring has several installation grooves for matching and installing the forward pawl 5 and the reverse pawl 6 .

There are twelve sets of pawl installation groove pairs on the inner surface of the inner ring 302 of the outer ring, and the twelve sets of pawl installation groove pairs are respectively connected with twelve sets of ratchet pawls composed of positive pawls 5 and reverse pawls 6 . The pawl pairs correspond one by one, each set of pawl installation groove pairs is composed of a forward pawl installation slot 303 and a reverse pawl installation slot 304, and the forward pawl 5 in the pawl pair is correspondingly installed in the forward pawl installation In the groove 303, the reverse pawl 6 is correspondingly installed in the reverse pawl installation groove 304. As mentioned above, the forward pawl 5 and the reverse pawl 6, and the forward pawl 5 and the reverse pawl 6 The roots of the pawls are arranged opposite to each other, and the pawl heads of the forward pawl 5 and the reverse pawl 6 are arranged in the opposite direction. Therefore, the forward pawl installation groove 303 and the reverse pawl installation groove 304 have the same structure and The directions are opposite, and the installation and connection manners of the forward pawl 5 and the reverse pawl 6 in the forward pawl installation groove 303 and the reverse pawl installation groove 304 are exactly the same.

Taking the installation of the positive pawl 5 and the positive pawl installation groove 303 as an example, as shown in FIGS. 7 and 8 , the inner end of the installation groove 303 of the positive pawl 5 is the pawl root 504 of the positive pawl 5 The outer contour matches the arc-shaped groove surface, the pawl root 504 is installed in the arc-shaped groove surface, and the pawl root 504 rotates relatively in the arc-shaped groove surface under the driving of external force; the middle part of the positive pawl installation groove 303 There is a flap spring installation slot, one end of the positive flap spring 6 is installed in the flap spring installation slot, and the other end of the positive flap spring 6 is clamped to the flap spring on the upper surface of the positive pawl 5 In the card slot 503; the other end of the positive pawl installation slot 303 leaves a necessary space for the pawl head 505 of the positive pawl 5 to prevent the pawl head 505 of the positive pawl 5 from rising up with the outer ring. The inner ring 302 interferes.

As shown in FIG. 5 , the control ring main body 201 of the control ring 2 is a ring-shaped plate structure, and twelve groups of control window pairs are opened on the control ring main body 201 , and the twelve groups of control window pairs are respectively connected with twelve groups of positive spines. The pawl pairs formed by the pawl 5 and the reverse pawl 6 correspond to each other one by one. Each control window pair is composed of a forward control window 203 and a reverse control window 204. The pawl control pin 502 is cooperatively connected, and the reverse control window 204 is cooperatively connected with the pawl control pin of the reverse pawl 6; the cooperative connection between the control window and the pawl control pin means that the pawl control pin is inserted into the control window and connected to the control window. At the point where the control surface at the bottom of the window meets, and in the process of colliding with the control surface at the bottom of the control window, the movement of the pawl control pin is controlled by the control surface at the bottom of the control window to realize the lifting and lowering of the pawl control pin, and then the corresponding control pin is controlled by the pawl control pin. The pawl swings up and down. Therefore, the swing mode of the pawl depends on the design of the control surface at the bottom of the control window. According to the actual working conditions, the corresponding shape of the control surface can be designed to realize different working modes; in this specific embodiment, the control ring is set 2 rotate clockwise relative to the annularly distributed forward pawl 5 and reverse pawl 6, and then control the corresponding pawl to swing through the pawl control pin. Correspondingly, the forward pawl 5 and the reverse pawl 6 rotate clockwise. The swinging way to the pawl 6 is designed as: first: both the forward pawl 5 and the reverse pawl 6 are in the lowest position; then: the forward pawl 5 is kept in the lowest position and the reverse pawl 6 is gradually raised to the highest position position; finally: the forward pawl 5 gradually rises to the highest position and the reverse pawl 6 remains in the highest position. Correspondingly, the control window pair structure on the control loop is as follows:

As shown in FIG. 5 , the control ring main body 201 of the control ring 2 is provided with twelve groups of control window pairs, and the twelve groups of control window pairs and the twelve groups are respectively composed of forward pawls 5 and reverse pawls 6 Each set of control window pairs is composed of a forward control window 203 and a reverse control window 204. The forward control window 203 is connected with the pawl control pin 502 of the forward pawl 5, and the reverse The control window 204 is matched and connected with the pawl control pin of the reverse pawl 6; the control surface at the bottom of the forward control window 203 includes the forward control window inclined surfaces 205 arranged clockwise (that is, the same as the rotation direction of the control ring 2) in sequence. and the forward control window plane 206, the forward control window slope 205 and the reverse control window plane 206 are continuous and unobstructed, wherein the forward control window slope 205 is counterclockwise (that is, opposite to the rotation direction of the control ring 2) gradually away from the control ring 2 The arc surface at the center of the circle, the forward control window plane 206 is an arc surface arranged concentrically with the control ring 2; The reverse control window plane 207 and the reverse control window slope 208 are set in turn, and the reverse control window plane 207 and the reverse control window slope 208 are continuous and unobstructed, wherein the reverse control window plane 207 is set concentric with the control ring 2. Arc surface, the reverse control window slope 208 is an arc surface gradually away from the center of the control ring 2 counterclockwise (ie, opposite to the rotation direction of the control ring 2 ). The lengths of the forward control window slope 205 and the reverse control window plane 207 are the same, and the forward control window plane 206 and the reverse control window slope 208 have the same length.

When the pawl control pin of the forward pawl 5 is inserted into the forward control window 203, under the elastic force of the forward spring 303, the pawl control pin of the forward pawl 5 is always It is pressed against the control surface of the forward control window 203. Similarly, when the pawl control pin of the reverse pawl 6 is inserted into the reverse control window 204, the reverse pawl 6 is in the reverse spring. Under the action of the elastic force of 304 , the pawl control pin of the reverse pawl 6 is always pressed against the control surface of the reverse control window 204 .

As shown in FIG. 9 , in the initial position, the pawl control pin of the forward pawl 5 is at the far right end of the forward control window plane 206 of the forward control window 203 . At this time, the forward pawl 5 is in the lowest position, while the reverse The pawl control pin of the pawl 6 is at the far right end of the reverse control window slope 208 of the reverse control window 204, and the reverse pawl 6 is also in the lowest position at this time;

As shown in FIG. 10, as the control ring 2 rotates clockwise, the pawl control pin of the positive pawl 5 moves under the action of the positive control window plane 206 of the control ring 2. The ring 2 is coaxially arranged, so the pawl control pin of the positive pawl 5 does not move along the radial direction of the control ring 2, so the positive pawl 5 is always kept at the lowest position (ie, the position closest to the center of the control ring 2) At the same time, the pawl control pin of the reverse pawl 6 moves under the action of the reverse control window slope 208 of the control ring 2. Since the reverse control window slope 208 gradually moves away from the center of the control ring 2 counterclockwise, it follows 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. Driven by the pawl control pin of the reverse pawl 6, the reverse The pawl 6 is gradually raised; when the pawl control pin of the positive pawl 5 is located at the junction of the positive control window plane 206 and the inclined surface of the positive control window, the positive pawl 5 is still in the lowest position, and at this time the reverse The pawl control pin of the pawl 6 is located at the junction of the reverse control window plane 207 and the inclined surface of the reverse control window, at this time the reverse pawl 6 is raised to the highest position (that is, 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 positive pawl 5 starts to move under the action of the positive control window slope 205 of the control ring 2, because the positive control window slope 205 It is gradually away from the center of the control ring 2 counterclockwise, so as the control ring 2 continues to rotate clockwise, the pawl control pin of the positive pawl 5 gradually moves away from the center of the control ring 2 along the radial direction of the control ring 2. Driven by the pawl control pin of the pawl 5, the positive pawl 5 gradually rises until it moves to the leftmost end of the inclined surface 205 of the positive control window. At this time, the positive pawl 5 rises to the highest position (ie, away 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, since the reverse control window plane 207 is coaxial with the control ring 2 Therefore, 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 remains 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 both 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 All are in the lowest position, the pawl head of the forward pawl 5 is clamped in the forward pawl slot 801 of a pair of pawl slots of the inner ring 8, and the pawl head of the reverse pawl 6 is clamped. It is connected to the reverse pawl clamping groove 802 of the other group of pawl clamping groove pairs of the inner ring 8, and the pawl heads of the forward pawl 5 and the reverse pawl 6 are arranged in opposite directions. Therefore, the inner ring 8 The relative clockwise and relative counter-clockwise directions between the inner ring 8 and the outer ring 3 are locked. At this time, the power transmission between the inner ring 8 and the outer ring 3 can be performed in both clockwise and relatively counter-clockwise directions.

As shown in FIG. 10 , as the control ring 2 rotates clockwise, the pawl control pin of the forward pawl 5 moves from the rightmost end of the forward control window plane 206 to the forward control window plane 206 and the forward control window slope 205 During the process of the junction, the positive pawl 5 has no movement along the radial direction of the control ring 2 and is always in the lowest position, that is, the positive pawl 5 remains engaged in the positive pawl slot 801 of the inner ring 8, and At the same time, the reverse pawl 6 moves from the rightmost end of the reverse control window inclined surface 208 to the junction of the reverse control window plane 207 and the reverse control window inclined surface 208. During this process, the reverse pawl 6 is lifted upward to At the highest point, the pawl head of the reverse pawl 6 is disengaged from the reverse pawl slot 802 of the inner ring 8. At this time, the inner ring 8 is locked clockwise relative to the outer ring 3 and can be counterclockwise. Relatively free rotation, that is, when the inner ring 8 rotates counterclockwise relative to the outer ring 3, there is no power transmission, and when the inner ring 8 rotates clockwise relative to the outer ring 3, power can be transmitted, that is, the clutch realizes one-way overrun.

As shown in FIG. 11 , as the control ring 2 continues to rotate clockwise, when both the pawl control pins of the forward pawl 5 and the reverse pawl 6 move to the leftmost end of the control window pair of the control ring 2, the forward pawl The pawl 5 and the reverse pawl 6 are both in the highest position, and the pawl heads of the forward pawl 5 and the reverse pawl 6 are separated from the forward pawl slot 801 and the reverse pawl slot 802 of the inner ring 8 respectively. At this time, the inner ring 8 and the outer ring 3 can rotate freely in both clockwise and relatively counterclockwise directions. At this time, there is no clockwise or counterclockwise direction between the inner ring 8 and the outer ring 3 Power transmission, that is, the clutch achieves two-way overrun.

In addition, as shown in FIG. 3 and FIG. 4 , in this specific embodiment, only one control ring 2 is matched and installed on one axial outer end of the forward pawl 5 and the reverse pawl 6 . A control ring 2 can also be installed on the other side of the axial outer end of the forward pawl 5 and the reverse pawl 6 . The pawl control pins 502 are vertically arranged on the two outer sides of the middle part of the main body 501. The two control rings 2 are identical in structure and symmetrically arranged. The forward pawl 5 and the reverse pawl 6 swing up and down to ensure that the forward pawl 5 and the reverse pawl 6 are balanced in force without eccentric load.

To sum up, the overrunning clutch of the present invention controls the corresponding pawl movement through the rotation of the control ring 2 to achieve locking or separation between the inner ring 8 and the outer ring 3. Therefore, in order to control the rotation of the control ring 2, As shown in FIG. 5 , a sector-shaped control gear tooth 202 is provided on the outer circumference of the control ring 2 , and the control gear tooth 202 meshes with the driving gear in the gear-pair control mechanism to realize power transmission, or meshes with the gear tooth The rack in the bar-type control mechanism is meshed to achieve power transmission, or it is meshed with the worm-gear and worm-type control mechanism to achieve power transmission; accordingly, as shown in Figure 7, in the outer ring of the outer ring 3 On the outer ring 301, at a position corresponding to the control gear teeth 202, there is an arc-shaped control mechanism avoidance groove 305, so as to realize the avoidance of 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 (4), 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 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.

Images