CN219035366U - Tooth clutch - Google Patents

Abstract

The utility model discloses a tooth clutch, which comprises a piston assembly, an inner fluted disc, an outer toothed sleeve and an elastic piece. The piston assembly comprises a piston seat and a piston sleeve, a pressure cavity extending along the axial direction of the piston seat is formed in the piston seat, a mounting port communicated with the pressure cavity is formed at one end of the piston seat, a pressure source inlet and a pressure source outlet communicated with the pressure cavity are formed on the side wall of the piston seat, and the piston sleeve penetrates through the mounting port and can be axially movably and hermetically mounted in the pressure cavity. The inner fluted disc is rotatably sleeved in the piston sleeve and can axially move along with the axial movement of the piston sleeve. The outer tooth sleeve is arranged opposite to the inner tooth plate, is positioned on one side of the inner tooth plate far away from the bottom wall, is suitable for being sleeved on the outer circumferential wall of the inner tooth plate, one of the outer circumferential wall of the inner tooth plate and the inner circumferential wall of the outer tooth sleeve forms at least one combination tooth, and the other forms at least one combination groove capable of being embedded with the combination tooth. The elastic piece is arranged between the inner fluted disc and the outer tooth sleeve. The clutch has long service life and high transmission stability and reliability.

Description

Tooth clutch

Technical Field

The present utility model relates to the field of clutch devices, and more particularly to tooth clutches.

Background

Clutches are common components in mechanical transmissions, and are typically provided in both an engaged state, in which they can transfer power, thereby effecting power transfer between the two components, and a disengaged state, in which they can no longer transfer power, thereby interrupting power transfer between the two components.

At present, a tooth clutch is often engaged or disengaged by engaging teeth and engaging grooves provided on both end walls, respectively, being engaged or disengaged close to or away from each other. However, when the engaging teeth on one end wall are tightly engaged with the engaging grooves on the other end wall, the end wall is damaged easily, and the service life of the clutch is reduced. If the engaging teeth on one end wall are not tightly engaged with the engaging grooves on the other end wall, the engaging teeth and the engaging grooves are easily separated when the clutch transmits power, so that the transmission stability and reliability of the clutch are deteriorated.

Disclosure of Invention

One advantage of the present utility model is to provide a tooth clutch that has a long service life and high transmission stability and reliability.

The utility model has the advantages of simple structure, fewer parts and convenient disassembly and assembly.

To achieve at least one of the above advantages, the present utility model provides a tooth clutch comprising: the piston assembly comprises a piston seat and a piston sleeve, a pressure cavity extending along the axial direction of the piston seat is formed in the piston seat, a mounting port communicated with the pressure cavity is formed at one end part of the piston seat, a bottom wall opposite to the mounting port is formed at the other end part of the piston seat, a pressure source inlet and a pressure source outlet communicated with the pressure cavity are formed on the side wall of the piston seat, and the piston sleeve is axially movably and hermetically mounted in the pressure cavity through the mounting port and is respectively arranged on two opposite sides of the pressure source inlet and the pressure source outlet with the bottom wall; the inner fluted disc is rotatably sleeved in the piston sleeve and can axially move along with the axial movement of the piston sleeve; the outer tooth sleeve is arranged opposite to the inner tooth disc and is positioned on one side of the inner tooth disc away from the bottom wall, a connecting channel extending along the axial direction of the outer tooth sleeve is formed in the outer tooth sleeve and is suitable for being sleeved on the outer circumferential wall of the inner tooth disc, one of the outer circumferential wall of the inner tooth disc and the inner circumferential wall of the outer tooth sleeve forms at least one combination tooth protruding along the radial direction of the outer tooth disc, and the other forms at least one combination groove recessed along the radial direction of the inner tooth disc and capable of being embedded with the combination tooth; when the pressure source is introduced into the pressure source inlet and outlet, the piston sleeve moves along the axial direction towards the direction close to the outer tooth sleeve so as to drive the inner tooth disc to axially approach and enter the outer tooth sleeve, so that the combination teeth are moved to be embedded into the combination grooves, and the elastic piece is compressed; when the pressure source is discharged from the pressure source inlet and outlet, the inner tooth disc moves in the direction away from the outer tooth sleeve along the axial direction under the elastic action of the elastic piece, so that the combination teeth move to be separated from the combination grooves.

According to an embodiment of the present utility model, the outer peripheral wall of the inner toothed disc is provided with the engaging teeth protruding radially along the inner toothed disc, the inner peripheral wall of the outer toothed sleeve is provided with the engaging grooves recessed radially along the outer toothed sleeve, and the engaging teeth of the inner toothed disc can be fitted into the engaging grooves of the outer toothed sleeve.

According to an embodiment of the present utility model, the outer peripheral wall of the inner gear is provided with the coupling groove recessed along the radial direction of the inner gear, the inner peripheral wall of the outer gear sleeve is provided with the coupling teeth protruding along the radial direction of the outer gear sleeve, and the coupling teeth of the outer gear sleeve can be fitted and engaged in the coupling groove on the inner gear disc.

According to an embodiment of the present utility model, the outer peripheral wall of the inner gear is provided with a plurality of the coupling teeth or a plurality of the coupling grooves spaced apart along the circumferential direction of the inner gear, the outer peripheral wall of the outer gear sleeve is correspondingly provided with a plurality of the coupling grooves or a plurality of the coupling teeth spaced apart along the circumferential direction of the outer gear sleeve, and the plurality of the coupling teeth can be fitted in the plurality of the coupling grooves in a one-to-one correspondence.

According to an embodiment of the present utility model, the bottom wall is configured in a ring shape, the piston seat has an annular outer side wall and an annular inner side wall, the annular inner side wall is disposed inside the annular outer side wall and is disposed at a distance from the annular outer side wall, the bottom wall is connected between the annular outer side wall and the annular inner side wall to form the annular pressure chamber between the bottom wall, the annular outer side wall and the annular inner side wall, and the annular outer side wall forms the pressure source inlet and outlet.

According to an embodiment of the present utility model, the inner toothed disc includes a first tube body and an outer convex ring, the first tube body is rotatably sleeved in the piston sleeve, the outer convex ring is located outside the piston sleeve and extends radially outwards along the first tube body, the outer diameter of the outer convex ring is larger than the inner diameter of the piston sleeve, and the outer peripheral wall is provided with the coupling teeth or the coupling grooves; the external gear sleeve comprises a second pipe body and an inner convex ring, the connecting channel is formed in the second pipe body, the inner diameter of a port, close to the inner fluted disc, of the connecting channel is larger than the outer diameter of the outer convex ring, the inner convex ring extends inwards in the radial direction of the second pipe body to form, and the inner peripheral wall is correspondingly provided with the combining groove or the combining teeth.

According to an embodiment of the present utility model, the driving device further includes a driving shaft, and the driving shaft penetrates the external gear sleeve after penetrating the piston seat key to connect to the inner peripheral wall of the first tube.

According to an embodiment of the present utility model, the drive shaft further includes a first bearing mounted between the drive shaft and the outer hub, and a second bearing disposed between the piston hub and the inner disk.

According to an embodiment of the present utility model, the outer gear sleeve is provided with a first ring and a second ring, the second ring is opposite to the outer gear sleeve, the first rings are respectively mounted on an inner circumferential wall of the outer gear sleeve and an outer circumferential wall of the driving shaft, the first rings are located at one side of the first bearing away from the inner gear disc, the pressing ring is sleeved on the outer side of the driving shaft, the pressing ring is located at one side of the first bearing close to the inner gear disc, and the elastic member is disposed between the pressing ring and the inner gear disc.

According to an embodiment of the present utility model, the engine further includes a third bearing and two second check rings, wherein the third bearing is disposed between the piston seat and the driving shaft, and the two second check rings are respectively mounted on an inner peripheral wall of the piston seat and an outer peripheral wall of the driving shaft, and are located at a side of the third bearing away from the inner fluted disc.

Drawings

Fig. 1 shows a schematic structural view of a tooth clutch according to an embodiment of the present utility model.

Fig. 2 shows a cross-sectional view of a tooth clutch according to an embodiment of the utility model.

FIG. 3 shows a schematic diagram of the internal gear disk of an embodiment of the present utility model.

Fig. 4 shows a schematic structural view of an outer sleeve according to an embodiment of the present utility model.

Fig. 5 shows a schematic structural view of a piston seat according to an embodiment of the present utility model.

Reference numerals

100. A tooth clutch;

10. a piston assembly 11 and a piston seat; 1101. a pressure chamber; 1102. a mounting port; 113. a bottom wall; 1104. a pressure source inlet and outlet; 115. an annular outer sidewall, 116, an annular inner sidewall; 12. a piston sleeve; 1201. an annular seal groove; 13. a seal ring;

20. an inner fluted disc; 21. a first tube body; 22. an outer convex ring; 221. a coupling tooth;

30. an outer tooth sleeve; 301. a connection channel; 31. a second tube body; 32. an inner convex ring; 3201. a coupling groove;

40. an elastic member;

50. driving the rotating shaft;

60. a first bearing;

70. a second bearing;

80. a first retainer ring;

90. a compression ring;

110. a third bearing;

120. and a second check ring.

Detailed Description

The following description is presented to enable one of ordinary skill in the art to make and use the utility model. The preferred embodiments in the following description are by way of example only and other obvious variations will occur to those skilled in the art. The basic principles of the utility model defined in the following description may be applied to other embodiments, variations, modifications, equivalents, and other technical solutions without departing from the spirit and scope of the utility model.

It will be appreciated by those skilled in the art that in the present disclosure, the terms "longitudinal," "transverse," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," etc. refer to an orientation or positional relationship based on that shown in the drawings, which is merely for convenience of description and to simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore the above terms should not be construed as limiting the present utility model.

It will be understood that the terms "a" and "an" should be interpreted as referring to "at least one" or "one or more," i.e., in one embodiment, the number of elements may be one, while in another embodiment, the number of elements may be plural, and the term "a" should not be interpreted as limiting the number.

In the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; may be mechanically connected, may be electrically connected or may communicate with each other; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.

Referring to fig. 1 to 4, a tooth clutch 100 according to a preferred embodiment of the present utility model will be described in detail below, wherein the tooth clutch 100 includes a piston assembly 10, an inner toothed disc 20 and an outer toothed sleeve 30.

Referring to fig. 2 to 4, the piston assembly 10 includes a piston seat 11 and a piston sleeve 12. The piston seat 11 is internally provided with a pressure cavity 1101 extending along the axial direction thereof, one end part of the piston seat 11 is provided with a mounting port 1102 communicated with the pressure cavity 1101, the other end part of the piston seat 11 is provided with a bottom wall 113 opposite to the mounting port 1102, and the side wall of the piston seat 11 is provided with a pressure source inlet and outlet 1104 communicated with the pressure cavity 1101. The piston sleeve 12 is axially movably and sealingly mounted to the pressure chamber 1101 through the mounting opening 1102, and the piston sleeve 12 and the bottom wall 113 are disposed on opposite sides of the pressure source inlet and outlet 1104, respectively.

The inner gear 20 is rotatably fitted in the piston housing 12 and is axially movable with the axial movement of the piston housing 12.

The external gear sleeve 30 is disposed opposite to the internal gear plate 20 and is located at a side of the internal gear plate 20 away from the bottom wall 113, a connecting channel 301 extending along an axial direction thereof is formed in the external gear sleeve 30, and is adapted to be sleeved on an outer peripheral wall of the internal gear plate 20, one of the outer peripheral wall of the internal gear plate 20 and an inner peripheral wall of the external gear sleeve 30 forms at least one coupling tooth 221 protruding along a radial direction thereof, and the other forms at least one coupling groove 3201 recessed along a radial direction thereof and capable of being engaged with the coupling tooth.

The elastic member 40 is disposed between the inner disk 20 and the outer hub 30.

Thus, when the tooth clutch 100 is used, the tooth clutch 100 may be connected to a driving device capable of driving the inner gear 20 to rotate and a load device capable of being driven to rotate by the outer gear sleeve 30, so that when the pressure source, such as gas, is introduced into the pressure source inlet/outlet 1104, the introduced pressure source drives the piston sleeve 12 to move in a direction axially approaching the outer gear sleeve 30, thereby driving the inner gear 20 to axially approach and enter the outer gear sleeve 30, further driving the engaging teeth 221 to move and engage with the engaging grooves 3201, and compressing the elastic members 40. Therefore, the rotation of the inner gear plate 20 can drive the outer gear sleeve 30 to rotate, the rotation motion transmitted from the inner gear plate 20 by the driving device can be transmitted to the outer gear sleeve 30 and transmitted out through the outer gear sleeve 30, so that the load device is driven to rotate, and the tooth clutch 100 can realize power transmission.

When the pressure source is discharged from the pressure source inlet/outlet 1104, the inner gear 20 is moved in the axial direction away from the outer gear housing 30 by the elastic force of the elastic member 40, so that the coupling teeth 221 are moved out of the coupling grooves. In this way, the external gear sleeve 30 does not rotate when the internal gear plate 20 is driven to rotate, so that the rotational motion transmitted from the internal gear plate 20 by the driving device cannot be transmitted to the external gear sleeve 30, and transmitted through the external gear sleeve 30, the load device cannot be driven to rotate, and the power transmission of the tooth clutch 100 cannot be realized. In addition, in the above use process, the coupling teeth 221 can be tightly coupled with the coupling grooves 3201, and the damage to the outer gear sleeve 30 during coupling is small, so that the tooth clutch 100 has long service life, high transmission stability and reliability, simple structure, few parts and convenient disassembly and assembly.

According to some preferred embodiments of the present utility model, referring to fig. 2 to 4, the outer circumferential wall of the inner gear 20 is provided with the coupling teeth 221 protruding radially along the inner gear 20, the inner circumferential wall of the outer gear sleeve 30 is provided with the coupling grooves 3201 recessed radially along the outer gear sleeve 30, and the coupling teeth 221 of the inner gear 20 can be fitted into the coupling grooves 3201 of the outer gear sleeve 30.

Alternatively, the outer peripheral wall of the inner gear 20 may be provided with the coupling groove 3201 recessed in the radial direction of the inner gear 20, the inner peripheral wall of the outer gear sleeve 30 may be provided with the coupling teeth 221 protruding in the radial direction of the outer gear sleeve 30, and the coupling teeth 221 of the outer gear sleeve 30 may be fitted into the coupling groove 3201 of the inner gear 20.

Further, the outer peripheral wall of the inner gear 20 is provided with a plurality of coupling teeth 221 or a plurality of coupling grooves 3201 arranged at intervals along the circumferential direction of the inner gear 20, the outer peripheral wall of the outer gear sleeve 30 is correspondingly provided with a plurality of coupling grooves 3201 or a plurality of coupling teeth 221 arranged at intervals along the circumferential direction of the outer gear sleeve 30, and the plurality of coupling teeth 221 can be correspondingly embedded in the plurality of coupling grooves 3201, so that the coupling strength of the inner gear 20 and the outer gear sleeve 30 when being coupled is further improved, and the transmission stability and reliability of the gear clutch 100 when transmitting power are further ensured.

According to some preferred embodiments of the present utility model, referring to fig. 2 and 5, the bottom wall 113 is configured in a ring shape, the piston seat 11 has an annular outer side wall 115 and an annular inner side wall 116, the annular inner side wall 116 is disposed inside the annular outer side wall 115 and is spaced apart from the annular outer side wall 115, the bottom wall 113 is connected between the annular outer side wall 115 and the annular inner side wall 116 to form the annular pressure chamber 1101 between the bottom wall 113, the annular outer side wall 115 and the annular inner side wall 116, and the annular outer side wall 115 forms the pressure source inlet/outlet 1104.

Further, referring to fig. 2, the piston assembly 10 includes two annular sealing rings 13, an annular sealing groove 1201 is formed on the outer peripheral wall and the inner peripheral wall of the piston sleeve 12, and the two annular sealing rings 13 are disposed in the two annular sealing grooves 1201 respectively and are in contact with the annular inner sidewall 1105 and the annular outer sidewall 1106 respectively, so that the piston sleeve 12 can be mounted in the pressure chamber 1101 in a sealing manner, and can also move along the axial direction of the pressure chamber 101.

According to some preferred embodiments of the present utility model, referring to fig. 2 and 3, the inner gear 20 includes a first pipe 21 and an outer collar 22. The first pipe body 21 is rotatably sleeved in the piston sleeve 12. The outer diameter of the outer convex ring 22 is larger than the inner diameter of the piston sleeve 12, and the outer peripheral wall is provided with the engaging teeth 221 or the engaging grooves 3201, and the outer convex ring 22 is located outside the piston sleeve 12 and extends radially outwards along the first pipe body 21. In this way, the inner gear 20 is conveniently rotatably sleeved in the piston sleeve 12, and when the piston sleeve 12 moves in the axial direction to approach the outer gear sleeve 30, the piston sleeve 12 can push the inner gear 20 to move along the axial direction along with the axial movement, so that the inner gear 20 approaches and enters the outer gear sleeve 30 along the axial direction. The outer gear sleeve 30 includes a second pipe body 31 and an inner convex ring 32, the second pipe body 31 is internally provided with the connecting channel 301, and the inner diameter of the port of the connecting channel 301 near the inner gear plate 20 is larger than the outer diameter of the outer convex ring 22, so as to be suitable for the outer convex ring 22 to be sleeved into the second pipe body 31. The inner collar 32 extends radially inward along the second pipe body 31, and the inner peripheral wall of the inner collar 32 is correspondingly provided with the coupling groove 3201 or the coupling tooth 221. In this way, the inner gear plate 20 is conveniently moved into the outer gear sleeve 30 along the axial direction and combined with the outer gear sleeve 30, so that the combination and the separation of the tooth clutch 100 are conveniently and smoothly realized.

According to some preferred embodiments of the present utility model, in conjunction with fig. 2-4, the tooth clutch 100 further includes a drive shaft 50. The driving shaft 50 penetrates through the piston seat 11, is connected to the inner peripheral wall of the first tube 21 by a key, and then penetrates into the outer gear sleeve 30 to drive the inner gear plate 20 to rotate. Specifically, the driving shaft 50 is adapted to be connected to a driving device, so that the driving device can rotate the inner gear 20 by driving the driving shaft 50 to rotate. The tooth clutch 100 is convenient to drive and compact in structure.

Specifically, the driving shaft 50 is hollow and tubular, which saves materials, has light weight and low cost. The key connection of the driving shaft 50 to the inner peripheral wall of the inner gear 20 means that one of the outer peripheral wall of the driving shaft 50 and the inner peripheral wall of the inner gear 20 forms a driving protrusion protruding along a radial direction thereof, the other forms a driving groove recessed along a radial direction thereof, and the driving protrusion is embedded in the driving groove, so that the inner gear 20 can be driven to rotate synchronously when the driving shaft 50 rotates.

According to some preferred embodiments of the present utility model, in combination with fig. 2, the tooth clutch 100 further includes a first bearing 60 and a second bearing 70, the first bearing 60 being installed between the driving shaft 50 and the outer gear sleeve 30. The second bearing 70 is disposed between the piston sleeve 12 and the inner toothed disk 20. Thus, when the tooth clutch 100 is in the disengaged state, the rotation of the drive shaft 50 does not affect the outer hub 30, the rotation of the inner disk 20 does not affect the piston hub 12, the rotation accuracy of the drive shaft 50 and the inner disk 20 during rotation is ensured, and the drive shaft 50 and the inner disk 20 are not easily damaged by friction during rotation.

Further, in conjunction with fig. 2, the tooth clutch 100 further includes two first retainers 80 and a pressure ring 90. The second bearing 70 is disposed opposite the outer collar 22. The two first retainers 80 are respectively mounted on the inner peripheral wall of the outer gear sleeve 30 and the outer peripheral wall of the driving shaft 50, and are located on the side of the first bearing 60 away from the inner gear plate 20. The pressing ring 90 is sleeved on the outer side of the driving shaft 50, and is located on one side of the first bearing 60, which is close to the inner gear 20. The elastic member 110 is disposed between the pressing ring 90 and the inner disk 20. Thus, when the tooth clutch 100 is assembled, the elastic member 110 may give a certain initial elastic force to the inner disk 20 and the pressing ring 90, so that the outer ring 22 of the inner disk 20 may abut against the second bearing 70, and the pressing ring 90 may abut against the first bearing 60, thereby ensuring that the inner disk 20 and the outer hub 30 may be stably separated.

According to some preferred embodiments of the present utility model, in conjunction with fig. 2, the tooth clutch 100 further includes a third bearing 110 and two second retainers 120. The third bearing 110 is disposed between the piston seat 11 and the driving shaft 50, and the two second retainers 120 are respectively mounted on the inner peripheral wall of the piston seat 11 and the outer peripheral wall of the driving shaft 50, and are located at a side of the third bearing 110 away from the inner fluted disc. Therefore, the rotation of the driving shaft 50 does not affect the piston seat 11, so that the rotation accuracy of the driving shaft 50 is ensured, and the driving shaft 50 is not easy to be damaged by friction caused by rotation.

It will be appreciated by persons skilled in the art that the embodiments of the utility model described above and shown in the drawings are by way of example only and are not limiting. The advantages of the present utility model have been fully and effectively realized. The functional and structural principles of the present utility model have been shown and described in the examples and embodiments of the utility model may be modified or practiced without departing from the principles described.

Claims (10)

1. A tooth clutch, comprising:

the piston assembly comprises a piston seat and a piston sleeve, a pressure cavity extending along the axial direction of the piston seat is formed in the piston seat, a mounting port communicated with the pressure cavity is formed at one end part of the piston seat, a bottom wall opposite to the mounting port is formed at the other end part of the piston seat, a pressure source inlet and a pressure source outlet communicated with the pressure cavity are formed on the side wall of the piston seat, and the piston sleeve is axially movably and hermetically mounted in the pressure cavity through the mounting port and is respectively arranged on two opposite sides of the pressure source inlet and the pressure source outlet with the bottom wall;

the inner fluted disc is rotatably sleeved in the piston sleeve and can axially move along with the axial movement of the piston sleeve;

the outer tooth sleeve is arranged opposite to the inner tooth disc and is positioned on one side of the inner tooth disc away from the bottom wall, a connecting channel extending along the axial direction of the outer tooth sleeve is formed in the outer tooth sleeve and is suitable for being sleeved on the outer circumferential wall of the inner tooth disc, one of the outer circumferential wall of the inner tooth disc and the inner circumferential wall of the outer tooth sleeve forms at least one combination tooth protruding along the radial direction of the outer tooth disc, and the other forms at least one combination groove recessed along the radial direction of the inner tooth disc and capable of being embedded with the combination tooth; the method comprises the steps of,

the elastic piece is arranged between the inner fluted disc and the outer tooth sleeve, when the pressure source is introduced into the pressure source inlet and outlet, the piston sleeve moves along the axial direction towards the direction close to the outer tooth sleeve so as to drive the inner fluted disc to axially approach and enter the outer tooth sleeve, so that the combination teeth are moved to be embedded into the combination grooves, and the elastic piece is compressed; when the pressure source is discharged from the pressure source inlet and outlet, the inner tooth disc moves in the direction away from the outer tooth sleeve along the axial direction under the elastic action of the elastic piece, so that the combination teeth move to be separated from the combination grooves.

2. The tooth clutch as claimed in claim 1, characterized in that the outer peripheral wall of the inner tooth disk is provided with the engaging teeth protruding radially along the inner tooth disk, the inner peripheral wall of the outer tooth sleeve is provided with the engaging grooves recessed radially along the outer tooth sleeve, and the engaging teeth of the inner tooth disk are fittingly engaged in the engaging grooves on the outer tooth sleeve.

3. The tooth clutch as claimed in claim 1, characterized in that the outer peripheral wall of the inner tooth disk is provided with the engaging groove recessed in the radial direction of the inner tooth disk, the inner peripheral wall of the outer tooth sleeve is provided with the engaging tooth protruding in the radial direction of the outer tooth sleeve, and the engaging tooth of the outer tooth sleeve is fittingly engaged in the engaging groove on the inner tooth disk.

4. The tooth clutch according to claim 1, wherein the inner tooth disk outer peripheral wall is provided with a plurality of the engaging teeth or a plurality of the engaging grooves provided at intervals in the inner tooth disk circumferential direction, the outer tooth cover outer peripheral wall is correspondingly provided with a plurality of the engaging grooves or a plurality of the engaging teeth provided at intervals in the outer tooth cover circumferential direction, and the plurality of the engaging teeth can be fitted in the plurality of the engaging grooves in one-to-one correspondence.

5. The tooth clutch as claimed in claim 1, wherein said bottom wall is configured in a ring shape, said piston seat has an annular outer side wall and an annular inner side wall disposed inside and spaced from said annular outer side wall, said bottom wall being connected between said annular outer side wall and said annular inner side wall to form said pressure chamber in a ring shape between said bottom wall, said annular outer side wall and said annular inner side wall, and said annular outer side wall forming said pressure source inlet and outlet.

6. The tooth clutch as claimed in claim 1, wherein said inner tooth disc includes a first tube rotatably fitted in said piston sleeve and an outer collar located outside said piston sleeve and extending radially outwardly along said first tube, said outer collar having an outer diameter greater than an inner diameter of said piston sleeve and an outer peripheral wall provided with said engaging teeth or said engaging grooves; the external gear sleeve comprises a second pipe body and an inner convex ring, the connecting channel is formed in the second pipe body, the inner diameter of a port, close to the inner fluted disc, of the connecting channel is larger than the outer diameter of the outer convex ring, the inner convex ring extends inwards in the radial direction of the second pipe body to form, and the inner peripheral wall is correspondingly provided with the combining groove or the combining teeth.

7. The tooth clutch as claimed in claim 6, further comprising a driving shaft, wherein said driving shaft penetrates said outer gear sleeve after penetrating said piston seat key to connect with said inner circumferential wall of said first tube.

8. The tooth clutch as claimed in claim 7, further comprising a first bearing and a second bearing, said first bearing being mounted between said drive shaft and said outer tooth sleeve, said second bearing being disposed between said piston sleeve and said inner tooth disc.

9. The tooth clutch as claimed in claim 8, further comprising two first check rings and a pressing ring, wherein said second check rings are disposed opposite to said outer race, said two first check rings are respectively mounted on said outer sleeve inner peripheral wall and said drive shaft outer peripheral wall and on a side of said first bearing away from said inner toothed disc, said pressing ring is sleeved on said drive shaft outer side and on a side of said first bearing adjacent to said inner toothed disc, and said elastic member is disposed between said pressing ring and said inner toothed disc.

10. The tooth clutch as claimed in claim 7, further comprising a third bearing and two second retainers, wherein said third bearing is disposed between said piston seat and said driving shaft, and said two second retainers are respectively mounted on an inner peripheral wall of said piston seat and an outer peripheral wall of said driving shaft, and are located on a side of said third bearing away from said inner toothed disc.

Images