CN113883239B - A clutch with passive double reduction ratio - Google Patents

Abstract

A clutch with passive double reduction ratios relates to the technical field of clutches. The invention aims to solve the problems of heavy weight, large volume and special controller and driver of the existing clutch. The motor is fixedly connected to a supporting plate, a driving gear is fixedly connected to a motor shaft of the motor, a first transition gear and a second transition gear are fixedly connected to a driving ratchet wheel, the driving gear is meshed with the first transition gear, the driving ratchet wheel is arranged between a first driven ratchet wheel and a second driven ratchet wheel, the driving ratchet wheel is sleeved on a transition shaft and can axially reciprocate along the transition shaft under the pushing of the first driven ratchet wheel and the second driven ratchet wheel, the first driven gear and the second driven gear are fixedly connected to an output shaft, the first transition gear can be meshed with the first driven gear, and the second transition gear can be meshed with the second driven gear. The invention is used for switching the transmission path and the reduction ratio.

Description

A clutch with passive double reduction ratio

technical field

The invention relates to the technical field of clutches, in particular to a clutch with passive double reduction ratios.

Background technique

With the development of robot technology and UAV technology, lighter and smaller drive and transmission mechanisms are required to perform more complex tasks. For example, the robot end effector performs the opening and closing capture action, and the drone performs the pull-down recovery action, which requires the actuator to output different speeds, forces or torques in different directions of motion. At present, the common clutches or reducers on automation equipment mostly use active clutches to switch the reduction ratio. Active clutches are usually composed of electromagnets, shift forks, gears and other components, which have the disadvantages of large volume, heavy weight, and high power. It greatly limits the miniaturization and lightweight development of advanced automation systems such as robots and drones. Therefore, it is necessary to develop a new type of clutch with small, light weight, passive, forward and reverse dual reduction ratios, and provide technical support for the refined development of automation equipment.

Contents of the invention

In order to solve the problems that the existing clutches are heavy and bulky and require special controllers and drivers, the present invention further proposes a passive double reduction ratio clutch that relies on its own power to realize output switching of two reduction ratios.

The technical scheme that the present invention takes for solving the problems of the technologies described above is:

A passive double reduction ratio clutch includes a driving gear, a motor, a first transition gear, a second transition gear, a first driven ratchet, a second driven ratchet, a first driven gear, a second driven gear, an output shaft, The driving ratchet, the first one-way bearing, the second one-way bearing and the transition shaft, the motor is fixed on the support plate, the motor shaft of the motor is fixed with the driving gear, the first transition gear and the second transition gear are fixed on the drive On the ratchet, the driving gear meshes with the first transition gear, the first passive ratchet is set in the first bearing seat through the first one-way bearing, and the second passive ratchet is set in the second bearing seat through the second one-way bearing. The ratchet is arranged between the first passive ratchet and the second passive ratchet, the active ratchet is set on the transition shaft, and can reciprocate axially along the transition shaft under the push of the first passive ratchet and the second passive ratchet, the first slave The driven gear and the second driven gear are fixedly connected to the output shaft, the first transition gear can mesh with the first driven gear, and the second transition gear can mesh with the second driven gear.

Further, both end surfaces of the active ratchet are provided with active ratchet toothed surfaces, the first passive ratchet is sleeved on one end of the transition shaft, and the inner end surface of the first passive ratchet is provided with a first passive ratchet toothed surface. The inner ring set of a one-way bearing is fixedly connected to the first passive ratchet, the outer ring of the first one-way bearing is fixedly connected to the first bearing seat, and the end of one end of the transition shaft passes through a first rolling bearing and the first bearing seat Rotational connection, the second passive ratchet is set on the other end of the transition shaft, the inner end surface of the second passive ratchet is provided with a toothed surface of the second passive ratchet, and the inner ring of the second one-way bearing is fixedly connected to the second passive ratchet , the outer ring of the second one-way bearing is fixedly connected to the second bearing seat, and the other end of the transition shaft is rotationally connected with the second bearing seat through a first rolling bearing.

Further, the toothed surface of the active ratchet at one end of the active ratchet matches the toothed surface of the first passive ratchet of the first passive ratchet, and the toothed surface of the active ratchet at the other end of the active ratchet matches the teeth of the second passive ratchet of the second passive ratchet. The shape and surface match.

Further, when the active ratchet moves close to the first passive ratchet along the transition axis, the toothed surface of the active ratchet at one end of the active ratchet contacts the toothed surface of the first passive ratchet of the first passive ratchet, and the teeth of the active ratchet at the other end of the active ratchet The profile surface of the second passive ratchet is separated from the tooth surface of the second passive ratchet, the first transition gear meshes with the first driven gear, and the second transition gear is separated from the second driven gear; when the active ratchet moves along the transition axis When moving to the second passive ratchet, the active ratchet tooth surface at one end of the active ratchet is separated from the first passive ratchet tooth surface of the first passive ratchet, and the active ratchet tooth surface at the other end of the active ratchet is separated from the first passive ratchet tooth surface of the second passive ratchet. The toothed surfaces of the two driven ratchets are in contact, the first transition gear is separated from the first driven gear, and the second transition gear is meshed with the second driven gear.

Further, the active ratchet tooth surfaces at both ends of the active ratchet are double helical slopes, the first passive ratchet tooth surface of the first passive ratchet and the second passive ratchet tooth surface of the second passive ratchet are both double helical slopes .

Further, there is a gap between the first passive ratchet and the second passive ratchet and the transition shaft.

Further, the rotation directions of the first one-way bearing and the second one-way bearing are set in opposite directions.

Further, the motor shaft, the transition shaft and the output shaft of the motor are all arranged in parallel, and the transition shaft is arranged between the motor shaft and the output shaft of the motor.

Further, the inner peripheral side wall of the active ratchet is provided with a plurality of mounting grooves along the circumferential direction, and each mounting groove is respectively arranged along the radial direction, and a positioning steel ball is respectively arranged in each mounting groove, and the positioning steel ball There is a spring between the bottom of the installation groove and the outer circumferential side wall of the transition shaft. Two annular grooves are arranged side by side in the axial direction. The two annular grooves are adjacent to each other. Press down into an annular groove.

Further, the groove walls on both sides of the annular groove are inclined inwardly from the notch to the bottom of the groove.

The beneficial effect that the present invention comprises compared with prior art is:

1. The present invention adopts components such as one-way bearings and ratchet wheels, uses the driving gear as the power source of the clutch, and realizes the clutch of the transmission path by switching the positive and negative rotation of the driving gear, with low power consumption and high efficiency.

2. The present invention has two sets of transmission paths, two kinds of reduction ratios, and the positive and negative rotation of the driving shaft or the driving gear will switch to different transmission paths, so that the input speed is constant and the output speed is different.

3. The structure is compact, the integration is high, and the control is simple. It can realize the forward and reverse double reduction ratio output without special clutch controller and driving device.

4. The present invention has the advantages of low cost, safe and reliable use. The clutch can not only be used in the field of robots and unmanned aerial vehicles, but also can be extended to other application fields of mechanical transmission.

Description of drawings

Fig. 1 is the overall structural representation of the present invention;

Fig. 2 is a perspective view of the first passive ratchet 5-1 or the second passive ratchet 5-2 in the present invention.

Detailed ways

Specific Embodiment 1: This embodiment is described in conjunction with Fig. 1 to Fig. 2. A passive double reduction ratio clutch described in this embodiment includes a driving gear 1, a motor 2, a first transition gear 3-1, and a second transition gear 3-2. First passive ratchet 5-1, second passive ratchet 5-2, first driven gear 7-1, second driven gear 7-2, output shaft 8, driving ratchet 9, first one-way The bearing 10-1, the second one-way bearing 10-2 and the transition shaft 11, the motor 2 is fixed on the support plate, the motor shaft of the motor 2 is fixed with the driving gear 1, the first transition gear 3-1 and the second The transition gear 3-2 is fixedly connected to the driving ratchet 9, the driving gear 1 meshes with the first transition gear 3-1, and the first passive ratchet 5-1 is set on the first bearing seat 12 through the first one-way bearing 10-1. -1, the second passive ratchet 5-2 is set in the second bearing seat 12-2 through the second one-way bearing 10-2, and the active ratchet 9 is set on the first passive ratchet 5-1 and the second passive ratchet 5-1 2, the active ratchet 9 is set on the transition shaft 11, and can reciprocate axially along the transition shaft 11 under the push of the first passive ratchet 5-1 and the second passive ratchet 5-2, the first driven gear 7-1 and the second driven gear 7-2 are fixedly connected on the output shaft 8, the first transition gear 3-1 can be meshed with the first driven gear 7-1, and the second transition gear 3-2 can be meshed with the first driven gear 7-1. Two driven gears 7-2 are meshed.

Both the first bearing seat 12-1 and the second bearing seat 12-2 are fixedly connected to the support plate.

Both ends of the output shaft 8 are rotatably connected to the support plate through a second rolling bearing 14 respectively.

The index circle diameter of the first transition gear 3-1 is greater than the index circle diameter of the second transition gear 3-2, and the index circle diameter of the first driven gear 7-1 is smaller than the second driven gear 7-2 The diameter of the pitch circle, the distance between the first transition gear 3-1 and the second transition gear 3-2 is smaller than the distance between the first driven gear 7-1 and the second driven gear 7-2.

The present invention proposes a forward and reverse double reduction ratio clutch composed of one-way bearings, gears, screw shafts, springs, steel balls and other parts, which has the characteristics of simple and ingenious structure, small volume, light weight and no energy consumption.

The invention utilizes the characteristic that the inner ring of the one-way bearing can only rotate in one direction relative to the outer ring, and designs a special ratchet mechanism, which changes the positive and negative rotation of the driving wheel into the axial movement of the clutch sleeve, and realizes the switching of different driven gears , to achieve positive and negative output with different reduction ratios.

The power of the clutch in the present invention is derived from the rotation of the drive shaft itself, and the switching of the reduction ratio can be realized without using a controller and without consuming power.

The forward and reverse rotation of the input end of the clutch of the present invention has different output torques and rotational speeds at the output end.

The clutch of the present invention uses a one-way bearing to realize the switching of gear meshing.

The clutch of the present invention uses active and passive ratchets to realize the gear switching action of changing rotation into axial translation.

The motor 2 in this embodiment is a forward and reverse motor.

In this embodiment, the active ratchet 9 and the transition shaft 11 rotate synchronously.

The motor 2 is installed on the support plate, and the driving gear 1 is installed on the motor shaft, which can rotate positively and negatively with the motor 2; the first transition gear 3-1 and the second transition gear 3-2 have different graduation circles, and are fixedly installed On the active ratchet 9, the active ratchet 9 is sleeved on the transition shaft 11, which can slide and rotate freely in the axial direction; the positioning steel ball 4 and the spring 6 are installed on the active ratchet 9, and two annular grooves 1101 on the transition shaft 11 Cooperate to realize the positioning of the two transmission positions of the driving ratchet 9 on the transition shaft 11; the first driven gear 7-1 and the second driven gear 7-2 are installed on the output shaft 8 and have different pitch circles, which can Mesh with the first transition gear 3-1 and the second transition gear 3-2 respectively to obtain different reduction ratios; the outer ring of the first one-way bearing 10-1 is connected to the first bearing seat 12-1 through a key, and the inner ring is connected through a key It is connected with the first passive ratchet 5-1, and it can only rotate when the first passive ratchet 5-1 turns in a specific direction. The outer ring of the second one-way bearing 10-2 is connected with the second bearing seat 12-2 through a key, and the inner ring is passed through The key is connected with the second passive ratchet 5-2, and it can only rotate when the second passive ratchet 5-2 turns in a specific direction; the first transition gear 3-1 on the active ratchet 9 is always meshed with the driving gear 1, so that the motor output torque passes through The driving gear 1 is transmitted to the driving ratchet 9, and the driving ratchet 9 rotates on the transition shaft 11 and is pushed to perform axial translation on the transition shaft 11 by the first passive ratchet 5-1 and the second passive ratchet 5-2.

Specific embodiment 2: This embodiment is described with reference to Fig. 1 to Fig. 2. Both end faces of the active ratchet 9 in this embodiment are provided with toothed surfaces of the active ratchet, and the first passive ratchet 5-1 is set on the transition shaft 11. At one end, the inner end surface of the first passive ratchet 5-1 is provided with a tooth-shaped surface of the first passive ratchet, and the inner ring sleeve of the first one-way bearing 10-1 is fixedly connected to the first passive ratchet 5-1, and the first single The outer ring of the bearing 10-1 is firmly connected to the first bearing seat 12-1, the end of one end of the transition shaft 11 is connected to the first bearing seat through a first rolling bearing 13, and the second passive ratchet 5-2 is set on the On the other end of the transition shaft 11, the inner end surface of the second passive ratchet 5-2 is provided with a toothed surface of the second passive ratchet, and the inner ring sleeve of the second one-way bearing 10-2 is fixedly connected to the second passive ratchet 5-2. Above, the outer ring of the second one-way bearing 10-2 is fixedly connected to the second bearing seat 12-2, and the other end of the transition shaft 11 is rotatably connected to the second bearing seat through a first rolling bearing 13. Other compositions and connection methods are the same as those in Embodiment 1.

Specific embodiment three: This embodiment is described in conjunction with Fig. 1 to Fig. 2, the active ratchet tooth surface of one end of the active ratchet 9 described in this embodiment is matched with the first passive ratchet tooth surface of the first passive ratchet 5-1, the active ratchet The active ratchet toothed surface on the other end of the ratchet 9 cooperates with the second passive ratchet toothed surface of the second passive ratchet 5-2. Other compositions and connection methods are the same as those in the second embodiment.

Specific Embodiment 4: This embodiment is described in conjunction with FIGS. 1 to 2. In this embodiment, when the active ratchet 9 moves along the transition shaft 11 to approach the first passive ratchet 5-1, the toothed surface of the active ratchet at one end of the active ratchet 9 is aligned with the first passive ratchet 5-1. The first passive ratchet tooth surface of the first passive ratchet 5-1 is in contact, the active ratchet tooth surface of the other end of the active ratchet 9 is separated from the second passive ratchet tooth surface of the second passive ratchet 5-2, and the first transition gear 3-1 meshes with the first driven gear 7-1, and the second transition gear 3-2 is separated from the second driven gear 7-2; when the driving ratchet 9 moves along the transition shaft 11 to approach the second driven ratchet 5-2, the active ratchet tooth surface at one end of the active ratchet 9 is separated from the first passive ratchet tooth surface of the first passive ratchet 5-1, and the active ratchet tooth surface at the other end of the active ratchet 9 is separated from the second passive ratchet 5-1. The second driven ratchet tooth profile of -2 is in contact, the first transition gear 3-1 is separated from the first driven gear 7-1, and the second transition gear 3-2 is meshed with the second driven gear 7-2 . Other compositions and connection methods are the same as those in the third embodiment.

Specific embodiment five: this embodiment is described in conjunction with Fig. 1 to Fig. 2, the active ratchet tooth-shaped surfaces at both ends of the active ratchet 9 described in this embodiment are double helical slopes, the first passive ratchet teeth of the first passive ratchet 5-1 Both the profile surface and the second passive ratchet tooth profile surface of the second passive ratchet 5-2 are double helical slopes. Other composition and connection modes are the same as those in Embodiment 4.

In this embodiment, the double helical slope includes two symmetrical spiral slopes along the center.

Embodiment 6: This embodiment is described with reference to FIG. 1 to FIG. 2 . In this embodiment, there is a gap between the first passive ratchet 5 - 1 and the second passive ratchet 5 - 2 and the transition shaft 11 . Other compositions and connection methods are the same as those in the second embodiment.

Embodiment 7: This embodiment is described with reference to FIG. 1 to FIG. 2 . The rotation directions of the first one-way bearing 10 - 1 and the second one-way bearing 10 - 2 in this embodiment are set in opposite directions. Other compositions and connection methods are the same as those in Embodiment 1.

Embodiment 8: This embodiment is described in conjunction with FIGS. 1 to 2. The motor shaft, transition shaft 11 and output shaft 8 of the motor 2 described in this embodiment are all arranged in parallel, and the transition shaft 11 is arranged between the motor shaft of the motor 2 and the output shaft 8. Between the output shaft 8. Other compositions and connection methods are the same as those in Embodiment 1.

Ninth specific embodiment: This embodiment is described in conjunction with Fig. 1 to Fig. 2. The inner peripheral side wall of the active ratchet 9 described in this embodiment is provided with a plurality of mounting grooves 901 along the circumferential direction, and each mounting groove 901 is respectively along the radial direction. direction setting, each mounting groove 901 is respectively provided with a positioning steel ball 4, a spring 6 is provided between the positioning steel ball 4 and the groove bottom of the mounting groove 901, and the outer circumferential side wall of the transition shaft 11 is juxtaposed in the axial direction Two annular grooves 1101 are provided, and the two annular grooves 1101 are adjacently arranged, and the outside of the positioning steel ball 4 is pressed into one annular groove 1101 under the elastic force of the spring 6 . Other composition and connection modes are the same as those in Embodiment 1, 2, 3, 4, 5, 6, 7 or 8.

In such a design, a plurality of positioning steel balls 4 are used to clamp the transition shaft 11 circumferentially, so that the active ratchet 9 and the transition shaft 11 can rotate synchronously. When pushed by the first passive ratchet 5-1 and the second passive ratchet 5-2 , the positioning steel ball 4 slides out from the current annular groove 1101 and moves into another annular groove 1101 to realize the positioning of the two transmission positions of the active ratchet 9 on the transition shaft 11 .

Embodiment 10: This embodiment is described with reference to FIG. 1 to FIG. 2 . The groove walls on both sides of the annular groove 1101 in this embodiment are inclined inwardly from the notch opening to the bottom of the groove. Other compositions and connection modes are the same as those in Embodiment 9.

Such a design facilitates the movement of the positioning steel ball 4 .

working principle

The first passive ratchet 5-1 and the second passive ratchet 5-2 have complex end face geometry, by two spiral slopes as the working surface, the two end faces of the active ratchet 9 are the same as the first passive ratchet 5-1 and the second The passive ratchet 5-2 matches the spiral bevel. When the active ratchet 9 rotates clockwise as in Figure 1, the first one-way bearing 10-1 can rotate, the active ratchet 9 drives the first passive ratchet 5-1 to rotate, the second one-way bearing 10-2 cannot rotate, and the second one-way bearing 10-2 can rotate. The passive ratchet 5-2 does not move, and the first transition gear 3-1 installed on the active ratchet 9 meshes with the first driven gear 7-1, and the second transition gear 3-2 and the second driven gear 7-2 are engaged. When the active ratchet 9 rotates counterclockwise as shown in Figure 1, since the first one-way bearing 10-1 cannot rotate in this direction, the first passive ratchet 5-1 cannot rotate either, and the active ratchet 9 is in the first passive ratchet. 5-1 Axial movement occurs under the action of the double helical slope, the first transition gear 3-1 and the second transition gear 3-2 installed on the driving ratchet 9 will move together, the first transition gear 3-1 and the first transition gear The driven gear 7-1 is separated, the second transition gear 3-2 is meshed with the second driven gear 7-2, and the driving ratchet 9 is disengaged from the first driven ratchet 5-1 and is connected to the second driven ratchet at the other end. 5-2 meshes, the second one-way bearing 10-2 can rotate, and the active ratchet 9 drives the second passive ratchet 5-2 to rotate. Similarly, when the driving ratchet 9 rotates clockwise again, the driving ratchet 9 and the above first transition gear 3-1 and second transition gear 3-2 will be pushed back again by the second passive ratchet 5-2. Thus, the clutch is automatically switched to different rotation output paths according to the different rotation directions of the driving gear 1, and the forward and reverse double reduction ratio output is realized.

Although the invention is described herein with reference to specific embodiments, it should be understood that these embodiments are merely illustrative of the principles and applications of the invention. It is therefore to be understood that numerous modifications may be made to the exemplary embodiments and that other arrangements may be devised without departing from the spirit and scope of the invention as defined by the appended claims. It shall be understood that different dependent claims and features described herein may be combined in a different way than that described in the original claims. It will also be appreciated that features described in connection with individual embodiments can be used in other described embodiments.

Claims (8)

1. A passive dual reduction ratio clutch, characterized by: the device comprises a driving gear (1), a motor (2), a first transition gear (3-1), a second transition gear (3-2), a first driven ratchet wheel (5-1), a second driven ratchet wheel (5-2), a first driven gear (7-1), a second driven gear (7-2), an output shaft (8), a driving ratchet wheel (9), a first one-way bearing (10-1), a second one-way bearing (10-2) and a transition shaft (11), wherein the motor (2) is fixedly connected on a supporting plate, the driving gear (1) is fixedly connected on a motor shaft of the motor (2), the first transition gear (3-1) and the second transition gear (3-2) are fixedly connected on the driving ratchet wheel (9), the driving gear (1) is meshed with the first transition gear (3-1), the first driven ratchet wheel (5-1) is arranged in a first bearing seat (12-1) through the first one-way bearing, the second driven ratchet wheel (5-2) is arranged in a second bearing seat (12-2) through the second one-way bearing (10-2), the driving ratchet wheel (9) is fixedly connected on a motor shaft of the motor (2), the first driven ratchet wheel (5-1) is arranged between the first driven ratchet wheel (5-2) and the first driven ratchet wheel (9), the first driven ratchet wheel (5-1) and the second driven ratchet wheel (5-2) can axially reciprocate along the transition shaft (11), the first driven gear (7-1) and the second driven gear (7-2) are fixedly connected on the output shaft (8), the first transition gear (3-1) can be meshed with the first driven gear (7-1), and the second transition gear (3-2) can be meshed with the second driven gear (7-2);

the two end faces of the driving ratchet wheel (9) are provided with driving ratchet wheel tooth-shaped faces, a first driven ratchet wheel (5-1) is sleeved at one end of a transition shaft (11), the inner end face of the first driven ratchet wheel (5-1) is provided with a first driven ratchet wheel tooth-shaped face, the inner ring of a first one-way bearing (10-1) is fixedly sleeved on the first driven ratchet wheel (5-1), the outer ring of the first one-way bearing (10-1) is fixedly connected on a first bearing seat (12-1), one end part of the transition shaft (11) is in rotary connection with the first bearing seat through a first rolling bearing (13), a second driven ratchet wheel (5-2) is sleeved at the other end of the transition shaft (11), the inner ring of the second one-way bearing (10-2) is fixedly sleeved on the second driven ratchet wheel (5-2), the outer ring of the second one-way bearing (10-2) is fixedly connected on a second bearing seat (12-2), and the other end part of the transition shaft (11) is in rotary connection with the first bearing seat through a first rolling bearing (13);

a plurality of mounting grooves (901) are formed in the inner circumferential side wall of the driving ratchet wheel (9) along the circumferential direction, each mounting groove (901) is respectively arranged along the radial direction, a positioning steel ball (4) is respectively arranged in each mounting groove (901), a spring (6) is arranged between each positioning steel ball (4) and the groove bottom of each mounting groove (901), two annular grooves (1101) are formed in the outer circumferential side wall of the transition shaft (11) in parallel along the axial direction, the two annular grooves (1101) are adjacently arranged, and the outer part of each positioning steel ball (4) is pressed into one annular groove (1101) under the elastic action of the spring (6).

2. A passive dual reduction ratio clutch as defined in claim 1, wherein: the driving ratchet tooth surface at one end of the driving ratchet wheel (9) is matched with the first driven ratchet tooth surface of the first driven ratchet wheel (5-1), and the driving ratchet tooth surface at the other end of the driving ratchet wheel (9) is matched with the second driven ratchet tooth surface of the second driven ratchet wheel (5-2).

3. A passive dual reduction ratio clutch as defined in claim 2, wherein: when the driving ratchet wheel (9) moves along the transition shaft (11) to be close to the first driven ratchet wheel (5-1), a driving ratchet tooth surface at one end of the driving ratchet wheel (9) is contacted with a first driven ratchet tooth surface of the first driven ratchet wheel (5-1), a driving ratchet tooth surface at the other end of the driving ratchet wheel (9) is separated from a second driven ratchet tooth surface of the second driven ratchet wheel (5-2), the first transition gear (3-1) is meshed with the first driven gear (7-1), and the second transition gear (3-2) is separated from the second driven gear (7-2); when the driving ratchet wheel (9) moves along the transition shaft (11) to be close to the second driven ratchet wheel (5-2), the driving ratchet tooth surface at one end of the driving ratchet wheel (9) is separated from the first driven ratchet tooth surface of the first driven ratchet wheel (5-1), the driving ratchet tooth surface at the other end of the driving ratchet wheel (9) is contacted with the second driven ratchet tooth surface of the second driven ratchet wheel (5-2), the first transition gear (3-1) is separated from the first driven gear (7-1), and the second transition gear (3-2) is meshed with the second driven gear (7-2).

4. A passive dual reduction ratio clutch as defined in claim 3, wherein: the tooth-shaped surfaces of the driving ratchet wheels at two ends of the driving ratchet wheel (9) are double spiral inclined surfaces, and the tooth-shaped surfaces of the first driven ratchet wheel (5-1) and the tooth-shaped surfaces of the second driven ratchet wheel (5-2) are double spiral inclined surfaces.

5. A passive dual reduction ratio clutch as defined in claim 1, wherein: a gap is arranged between the first passive ratchet wheel (5-1) and the transition shaft (11) and between the second passive ratchet wheel (5-2) and the transition shaft.

6. A passive dual reduction ratio clutch as defined in claim 1, wherein: the rotation directions of the first unidirectional bearing (10-1) and the second unidirectional bearing (10-2) are opposite.

7. A passive dual reduction ratio clutch as defined in claim 1, wherein: the motor shaft, the transition shaft (11) and the output shaft (8) of the motor (2) are all arranged in parallel, and the transition shaft (11) is arranged between the motor shaft and the output shaft (8) of the motor (2).

8. A passive dual reduction ratio clutch as defined in claim 1, wherein: the groove walls at two sides of the annular groove (1101) are obliquely arranged inwards from the groove opening to the groove bottom.

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