CN214788679U

CN214788679U - Pneumatic separating mechanism

Info

Publication number: CN214788679U
Application number: CN202120291665.8U
Authority: CN
Inventors: 蔡和盛; 占贵贤; 吴勇; 林立
Original assignee: Fujian Wanrun New Energy Technology Co ltd
Current assignee: Fujian Wanrun New Energy Technology Co ltd
Priority date: 2021-02-02
Filing date: 2021-02-02
Publication date: 2021-11-19
Anticipated expiration: 2031-02-02

Abstract

The utility model discloses a pneumatic separating mechanism, which comprises a cylinder body, a piston and a pushing piece; the front end surface of the cylinder body is provided with a cylinder opening; a shaft channel is arranged in the cylinder body, the front port of the shaft channel penetrates through the cylinder opening on the front end surface of the cylinder body, and the rear port of the shaft channel penetrates through the rear end surface of the cylinder body; the piston is annular, is arranged in the cylinder body and is sleeved outside the shaft channel, and the rear end of the piston and the inner wall of the cylinder body form an annular air cavity; the annular air cavity is closed, when air is pumped into the annular air cavity, the piston is pushed to move towards the direction of the front port of the shaft channel, the volume of the annular air cavity is increased, when the piston is pushed towards the direction of the rear port of the shaft channel, and the air is pumped out of the annular air cavity, the volume of the annular air cavity is reduced; the pushing piece is annular, is arranged at the cylinder port of the cylinder body and is connected with the piston, and extends into the cylinder body or extends out of the cylinder body when moving along with the piston. The utility model has the advantages of simple structure, small volume and small radial space required by installation.

Description

Pneumatic separating mechanism

Technical Field

The utility model relates to a separating mechanism field especially relates to a pneumatic separating mechanism.

Background

The traditional hybrid vehicle widely adopts a diaphragm spring clutch as a device for separating a gearbox and a motor, and the diaphragm spring clutch can push the diaphragm spring clutch to act by using a matched separating mechanism. In the existing separating mechanism, a shifting fork 7 is arranged at one end of a swing rod 3, the other end of the swing rod 3 is communicated with the outside, and the swing rod 3 is pushed by an air cylinder, so that a separating bearing 4 obtains thrust to push the separating action of a diaphragm spring clutch.

Referring to fig. 1, the conventional release mechanism includes a release bearing 4, a shift fork 7, a swing link 3, a swing link support (copper bush), a boost cylinder 2, a bracket 1, a release sleeve 5, and the like, so that the conventional release mechanism is complex in installation and operation, occupies a large space, and may cause deformation of the swing link 3 and abrasion of the swing link support after long-term use, or cause incomplete clutch release and damage of the clutch due to clamping stagnation of the swing link 3.

For a vehicle adopting a diaphragm spring clutch, the automatic gear shifting process is controlled in an open loop mode, the gear shifting control is time control, namely, a ventilation time is given, when the ventilation time reaches a set value, the gear shifting is finished by default, the time control is controlled in the open loop mode, various external factors need to be considered for gear shifting, and therefore the set gear shifting finishing time is larger than the actual gear shifting time. The control mode has no specific feedback signal to determine whether the gear shifting is finished, so when the gear shifting is out of order, such as air leakage of an air cylinder or other reasons, the air cylinder cannot push the diaphragm spring clutch open completely, the diaphragm spring clutch is not separated completely, a semi-linkage state can occur, and the direct result is that the clutch plate is abraded and burnt.

SUMMERY OF THE UTILITY MODEL

Therefore, a pneumatic separating mechanism is needed to be provided to solve the problems that in the prior art, the separating mechanism of the diaphragm spring clutch is complex in installation and large in size, and the open-loop control easily causes the abrasion and burning of the clutch plates.

In order to achieve the purpose, the inventor provides a pneumatic separating mechanism, which comprises a cylinder body, a piston and a pushing piece;

a cylinder opening is formed in the front end face of the cylinder body; a shaft channel is arranged in the cylinder body, the front port of the shaft channel penetrates through the cylinder opening on the front end surface of the cylinder body, and the rear port of the shaft channel penetrates through the rear end surface of the cylinder body;

the piston is annular, is arranged in the cylinder body and is sleeved outside the shaft channel, and the rear end of the piston and the inner wall of the cylinder body form an annular air cavity; the annular air cavity is closed, when air is pumped into the annular air cavity, the piston is pushed to move towards the direction of the front port of the shaft channel, the volume of the annular air cavity is increased, when the piston is pushed towards the direction of the rear port of the shaft channel, and when the air is pumped out of the annular air cavity, the volume of the annular air cavity is reduced;

the pushing piece is annular, is arranged at the cylinder port of the cylinder body, is connected with the piston and extends into the cylinder body or extends out of the cylinder body when moving along with the piston.

As a preferred structure of the present invention, the outer ring wall of the middle section of the piston protrudes outward to form a first annular protrusion, and the inner side wall of the rear end of the cylinder body protrudes inward to form a second annular protrusion; the rear end of the piston is sleeved with a first sealing ring, the rear end of the piston penetrates into the second annular bulge, the first sealing ring abuts against the inner ring wall of the second annular bulge, the first annular bulge is sleeved with a second sealing ring, and the second sealing ring abuts against the middle section of the cylinder body to form the annular air cavity in a surrounding mode.

As the utility model discloses a preferred structure still includes the bearing, the bearing is located between impeller and the piston, and the outer lane and the piston of bearing are connected, and the inner circle and the impeller of bearing are connected.

As a preferred structure of the utility model, the utility model also comprises a positioning column; the positioning column is arranged in the annular air cavity, is connected with the piston, and has the axial direction consistent with the moving direction of the piston; the inner wall of the cylinder body is provided with a blind hole, and a positioning column is inserted into the blind hole; when the piston moves, the positioning column moves axially in the blind hole and limits the piston to rotate.

As a preferred structure of the utility model, the annular air cavity is provided with an air port and a water drain port, and the water drain port is arranged downwards for draining water when the cylinder body is installed between the motor and the gearbox; the gas port is used for pumping gas into the annular gas cavity by the gas supply pump or discharging the gas in the annular gas cavity.

As the utility model discloses a preferred structure still includes proximity sensor, proximity sensor locates cylinder body department to whether the detection piston removes and targets in place.

As an optimized structure of the present invention, the proximity sensor is an inductive sensor.

As a preferred structure of the utility model, the jar mouth department of cylinder body is equipped with spacing retaining ring, spacing retaining ring is used for supplying the front end of piston to pass the jar mouth to and the jar mouth is worn out to the rear end of restriction piston.

As the utility model discloses a preferred structure, still the cover is equipped with the third sealing washer between spacing retaining ring and the piston, and the front end of the inner wall of spacing retaining ring, third sealing washer, cylinder body, piston encloses into inclosed chamber of stepping down, the chamber of stepping down is equipped with the breather valve.

As a preferred structure of the utility model, the jar mouth of cylinder body still is equipped with the circlip for the hole, circlip for the hole and the interior wall connection of cylinder body, and lean on by spacing retaining ring.

Different from the prior art, the pneumatic separating mechanism of the technical scheme adopts an annular inner cylinder structure, so that when the pneumatic separating mechanism is installed, the pneumatic separating mechanism can be directly installed between a motor and a gearbox, the motor is located at the rear end face of a cylinder body, the gearbox is located at the front end face of the cylinder body, a motor shaft and an input shaft of the gearbox can penetrate into the cylinder body and are in coaxial transmission connection in the cylinder body, when gas is pumped into an annular gas cavity, a pushing piece can move towards the direction close to the gearbox under the pushing of a piston to apply pressure to a diaphragm spring, so that a pressure plate and a clutch driven plate which are tightly pressed together are separated, and gear shifting control is completed. The diaphragm spring can be directly stressed without a support, the overall structure is simple, the size is small, the radial space required by installation is reduced, and the diaphragm spring can be well suitable for installation occasions with limited space.

Drawings

Fig. 1 is a diagram illustrating a state of use of a separating mechanism according to the background art of the present invention;

fig. 2 is a cross-sectional view of a pneumatic separation mechanism according to an embodiment of the present invention before gas is pumped;

fig. 3 is a cross-sectional view of the pneumatic separation mechanism according to an embodiment of the present invention after gas is pumped;

fig. 4 is an end view of a pneumatic separating mechanism according to an embodiment of the present invention;

fig. 5 is a partial view of a pneumatic separating mechanism according to an embodiment of the present invention;

fig. 6 is a first state diagram of the pneumatic separation mechanism according to an embodiment of the present invention mounted to the motor;

fig. 7 is a second state diagram of the pneumatic separating mechanism according to an embodiment of the present invention, mounted to the motor.

Description of reference numerals:

1. a support;

2. a booster cylinder;

3. a swing rod;

4. separating the bearing;

5. separating the casing;

6. a motor front end cover;

7. a shifting fork;

8. a motor shaft;

9. a gearbox;

10. a transmission input shaft;

11. a platen;

12. a diaphragm spring;

13. a clutch driven plate;

14. a brake drum;

15. a cylinder body; 150. a shaft passage; 151. an annular air cavity; 152. a second annular projection; 153. blind holes;

16. a piston; 160. a first annular projection; 161. a gas port; 162. a water discharge outlet; 163. a yielding cavity; 164. a vent valve;

17. a first seal ring;

18. a second seal ring;

19. a bearing;

20. a pusher member;

21. a positioning column;

22. a proximity sensor;

23. a limit retainer ring;

24. a third seal ring;

25. a circlip for a hole;

26. and (4) bolts.

Detailed Description

To explain technical contents, structural features, and objects and effects of the technical solutions in detail, the following detailed description is given with reference to the accompanying drawings in conjunction with the embodiments.

Referring to fig. 2 and 3, the present invention provides a pneumatic separating mechanism, which is mainly used as a separating device of a diaphragm spring clutch to push the separating action of the diaphragm spring clutch, and apply pressure to a diaphragm spring 12 on a pressure plate 11 behind a brake drum 14, so that the originally compressed pressure plate 11 and a clutch driven plate 13 are separated, thereby changing the gear state. The diaphragm separator is suitable for occasions with a shaft penetrating through the center, particularly has no complex external structure, has simple structure and small volume, can be directly arranged at the opposite position of the diaphragm spring 12 of the diaphragm separator, has small radial space required for installation, and can be well suitable for installation occasions with limited external space.

In a specific embodiment, the pneumatic separating mechanism comprises a cylinder 15, a piston 16 and a pushing member 20; the cylinder body 15 is a shell of the pneumatic separating mechanism, specifically, the cylinder body 15 is arranged in a horizontal column shape, one end face of the cylinder body 15 is a front end face, the other end face of the cylinder body 15 is a rear end face, and a space for accommodating a piston 16, a pushing piece 20 and a shaft (such as a motor shaft 8 and a transmission input shaft 10) is arranged in the cylinder body 15, and when the pneumatic separating mechanism is used, the front end face of the cylinder body 15 is opposite to a diaphragm spring 12 of a diaphragm spring clutch; the piston 16 is used for pushing the pushing piece 20 to move when gas is pumped into the cylinder 15; the pushing member 20 is a direct part for pushing the diaphragm spring 12, and the pushing member 20 is in direct contact with the diaphragm spring 12 when pushing the diaphragm spring 12.

The front end face of the cylinder body 15 is provided with a cylinder opening, when in production and installation, the piston 16 is placed into the cylinder body 15 from the cylinder opening, therefore, the size of the cylinder opening is not smaller than that of the piston 16, when the piston 16 moves away from the cylinder opening, the pushing piece 20 penetrates into the cylinder body 15 from the cylinder opening along with the movement of the piston 16, when the piston 16 moves close to the cylinder opening, the pushing piece 20 penetrates out of the cylinder body 15 from the cylinder opening along with the movement of the piston 16, therefore, the size of the cylinder opening is not smaller than that of the piston 16 and that of the pushing piece 20.

The cylinder body 15 is provided with a shaft channel 150, the front port of the shaft channel 150 penetrates through the cylinder opening of the front end surface of the cylinder body 15, the rear port of the shaft channel 150 penetrates through the rear end surface of the cylinder body 15, the front port of the shaft channel 150 is flush with the front end surface of the cylinder body 15, the rear port of the channel is flush with the rear end surface of the cylinder body 15, in addition, the caliber of the cylinder opening is larger than that of the front port of the shaft channel 150, the front port of the shaft channel 150 is positioned in the cylinder opening, the shaft channel 150 is coaxially arranged with the cylinder body 15, when in use, the motor shaft 8 penetrates into the shaft channel 150 from the rear port of the shaft channel 150, the gearbox input shaft 10 penetrates into the shaft channel 150 from the front port of the shaft channel 150, because the shaft channel 150 is used for shafts, such as the motor shaft 8 and the gearbox input shaft 10, the inner diameter of the shaft channel 150 should be larger than the diameters of the shafts, i.e. the diameter of the motor shaft 8 and the diameter of the gearbox input shaft 10, so that the motor shaft 8 and the gearbox input shaft 10 can pass through the shaft channel 150, and the rotation of the motor shaft 8 and the gearbox input shaft 10 is not affected.

The piston 16 and the pushing part 20 are both annular, the piston 16 is arranged in the cylinder body 15 and sleeved outside the shaft channel 150, and the rear end of the piston 16 and the inner wall of the cylinder body 15 enclose an annular air cavity 151; the annular air cavity 151 is closed, when air is pumped into the annular air cavity 151, the piston 16 is pushed to move towards the direction of the front port of the shaft channel 150, the volume of the annular air cavity 151 is increased, when the piston 16 is pushed towards the direction of the rear port of the shaft channel 150, and when air is pumped out of the annular air cavity 151, the volume of the annular air cavity 151 is decreased; the pushing member 20 is disposed at a cylinder opening of the cylinder 15, is connected to the piston 16, and extends into the cylinder 15 or extends out of the cylinder 15 when moving with the piston 16.

Because the piston 16 and the pushing member 20 are both annular, the piston 16 is located at the outer ring of the shaft channel 150, and the pushing member 20 is located at the axial projection of the outer ring of the shaft channel 150, the motor shaft 8 and the transmission input shaft 10 are not affected to penetrate into the shaft channel 150,

in order to provide an annular air chamber 151 which is closed and has a variable volume for pushing the piston 16 to move, in one embodiment, the inner side wall of the rear end of the cylinder 15 protrudes and bends toward the axis to form an annular groove, the notch of the annular groove is in the same direction as the notch of the cylinder 15, the rear end of the piston 16 penetrates into the annular groove, and the rear end of the piston 16 and the annular groove form the annular air chamber 151.

Between the front end of the piston 16 and the rear end of the piston 16 is a middle section of the piston 16, and in another embodiment, the outer ring wall of the middle section of the piston 16 protrudes outward to form a first annular protrusion 160, and the inner side wall of the rear end of the cylinder 15 protrudes inward to form a second annular protrusion 152; the rear end of the piston 16 is sleeved with a first sealing ring 17, the rear end of the piston 16 penetrates into the second annular bulge 152, the first sealing ring 17 abuts against the inner ring wall of the second annular bulge 152, the first annular bulge 160 is sleeved with a second sealing ring 18, and the second sealing ring 18 abuts against the middle section of the cylinder body 15, so that the annular air chamber 151 is defined.

In order to increase the moving stroke of the piston 16, in a further embodiment, the dimension (i.e., thickness) of the second annular protrusion 152 in the axial direction is sufficiently large, or the inner ring wall of the second annular protrusion 152 extends toward the cylinder port such that the rear end of the piston 16 is flush with the rear end surface of the cylinder 15 when the gas in the annular gas chamber 151 is completely pumped out, and the rear end of the piston 16 is not separated from the first annular protrusion 160 when the gas is pumped in the annular gas chamber 151 and the pushing member 20 pushes the diaphragm spring 12 until the pressure plate 11 and the clutch driven plate 13 are separated.

In a further embodiment, the first sealing ring 17 may be a Y-shaped sealing ring, and the second sealing ring 18 may also be a Y-shaped sealing ring.

The pneumatic separating mechanism is used as a separating mechanism of the diaphragm spring clutch and can be installed between a motor and a gearbox 9, a cylinder opening of a cylinder body 15 of the pneumatic separating mechanism faces the gearbox 9, the rear end face of the cylinder body 15 is connected with a motor front end cover 6, a gearbox input shaft 10 penetrates through a front end opening of a shaft passage 150 from the cylinder opening and enters the shaft passage 150, a motor shaft 8 penetrates into a peripheral passage from a rear end opening of the shaft passage 150, the motor shaft 8 and the gearbox input shaft 10 are coaxially connected in the shaft passage 150, the movement of a piston 16 is not influenced by the connection of the motor shaft 8 and the gearbox input shaft 10, the pneumatic separating mechanism can be directly installed at the motor front end cover 6, a support 1 is not required to be arranged, the structure is simple, and the radial space required by installation is reduced.

In addition, an annular air chamber 151 and a piston 16 are arranged outside a channel of the pneumatic separating mechanism, so, referring to fig. 7, when the motor and the gearbox 9 need to be separated, air is pumped into the annular air chamber 151, the piston 16 is pushed to move towards the front port of the shaft channel 150, in the process, the volume of the annular air chamber 151 is increased, and meanwhile, a pushing piece 20 moves along with the piston 16 and extends out of a cylinder body 15, so that pressure can be applied to a diaphragm spring 12, and the pressing plate 11 and a clutch driven plate 13 which are pressed together are separated; referring to fig. 6, when the motor is required to be in transmission connection with the transmission case 9, gas is pumped out from the annular gas chamber 151, the pressure of the pushing member 20 on the diaphragm spring 12 is gradually reduced, and at the same time, the diaphragm spring 12 gradually releases elastic potential energy to apply pressure on the pushing member 20, so that the piston 16 is pushed towards the rear end of the shaft channel 150, the volume of the annular gas chamber 151 is gradually reduced until the diaphragm spring 12 completely releases the elastic potential energy, and the pressure plate 11 and the clutch driven plate 13 are pressed together.

The pneumatic separating mechanism adopts an annular inner cylinder structure, compared with the traditional cylinder, the center of the annular air cavity 151 is a through hole (namely a shaft channel 150), a motor shaft 8 for transmitting power and a transmission input shaft 10 can pass through, the piston 16 of the traditional cylinder is a cylindrical entity and cannot be installed on the occasion with a shaft passing through the center, and the pneumatic separating mechanism can be directly installed on the outer surface of a front end cover of a driving motor, the traditional cylinder is also installed by an independent support 1, the pneumatic separating mechanism does not have a complex external structure, an external boosting cylinder 2 and the support 1 are not needed, the radial space required by assembly installation is reduced, and the annular cylinder stress area of the pneumatic separating mechanism can be adjusted according to requirements, so that larger thrust can be output.

The size determination method of the annular air cavity 151 of the pneumatic separation mechanism comprises the following steps:

according to the relation formula of the pressure P and the force F: p ═ F/s, resulting in the variant: f ═ P × s;

the formula shows that the thrust generated by air pressure is related to the size of the air pressure and the stress area s, the air pressure of the whole vehicle is in a range, so the minimum air pressure of the whole vehicle is used as an air pressure value to design, the required thrust can be obtained from the specification of the diaphragm spring clutch, and a certain margin needs to be added to the thrust in consideration of the friction force among all parts of the machine, so a safety coefficient eta is introduced, wherein the eta is more than or equal to 1.05.

Finally, the formula is obtained: thrust F is P × s × η;

therefore, as can be seen from the above equation, the radial size of the pneumatic release mechanism is determined by the thrust required by the diaphragm spring clutch, and the larger the required thrust is, the larger the force receiving area required by the pneumatic release bearing is, and therefore, the larger the radial size of the pneumatic release mechanism is.

If the pressure plate 11 and the clutch driven plate 13 rotate in a separated state, the pressure plate 11 and the diaphragm spring 12 also rotate along with the pressure plate 11, in order to avoid abrasion caused by the rotation of the piston 16 along with the diaphragm spring 12 and avoid the diaphragm spring 12 being restricted by the piston 16, which causes the pressure plate 11 to be difficult to rotate and to be abraded, in a further embodiment, the clutch driven plate further comprises a bearing 19, the bearing 19 can be a deep groove ball bearing, the bearing 19 is arranged between the pushing member 20 and the piston 16, the outer ring of the bearing 19 is connected with the piston 16, and the inner ring of the bearing 19 is connected with the pushing member 20. When the diaphragm spring 12 also rotates along with the pressure plate 11, the pushing part 20 also synchronously rotates, the piston 16 does not need to rotate along with the pushing part 20, friction between the piston 16 and the cylinder body 15 is avoided, when the first sealing ring 17 and the second sealing ring 18 are installed, friction between the first sealing ring 17 and the cylinder body 15 and the second sealing ring 18 are avoided, abrasion caused by follow-up rotation of the piston 16, the first sealing ring 17 and the second sealing ring 18 is avoided, and the service life of the mechanism is prolonged.

To further prevent the piston 16 from rotating with the pusher 20, in a further embodiment, a positioning post 21 is also included; the positioning column 21 is arranged in the annular air cavity 151, the positioning column 21 is connected with the piston 16, and the axial direction of the positioning column 21 is consistent with the moving direction of the piston 16; a blind hole 153 is formed in the inner wall of the cylinder body 15, and the blind hole 153 is used for the positioning column 21 to penetrate; the positioning post 21 axially moves in the blind hole 153 when the piston 16 moves, and restricts the rotation of the piston 16. When the first annular protrusion 160 and the second annular protrusion 152 are arranged, the blind hole 153 is opened at a surface of the second annular protrusion 152 facing the cylinder opening, and the positioning column 21 is arranged at a surface of the first annular protrusion 160 facing away from the cylinder opening, that is, the positioning column 21 is opposite to the blind hole 153.

The positioning column 21 can limit the rotation of the piston 16, the diaphragm spring 12 can only rotate along with the inner ring of the deep groove ball bearing when the pressure plate 11 rotates, a certain gap is reserved between the pneumatic separation mechanism and the diaphragm spring 12 during actual installation, and the diaphragm spring 12 is prevented from retreating along with the abrasion of a clutch plate, so that the diaphragm spring is prevented from being abutted against the pneumatic separation mechanism, the pressing force is reduced, and all parts of the pneumatic separation mechanism are abraded.

In addition, the positioning column 21 may be connected to the cylinder 15, and the axial direction of the positioning column 21 may be the same as the moving direction of the piston 16; a blind hole 153 is formed in the rear end of the piston 16, and the blind hole 153 is used for the positioning column 21 to penetrate; the positioning post 21 axially moves in the blind hole 153 when the piston 16 moves, and restricts the rotation of the piston 16. When the first annular protrusion 160 and the second annular protrusion 152 are disposed, the blind hole 153 is opened on a surface of the first annular protrusion 160 facing away from the cylinder opening, and the positioning column 21 is disposed on a surface of the second annular protrusion 152 facing the cylinder opening, that is, the positioning column 21 is disposed opposite to the blind hole 153.

In order to avoid the piston 16 from disengaging from the cylinder 15 at the cylinder opening, in a further embodiment, said cylinder 15 is provided with a limit stop 23 at the cylinder opening, the limit stop ring 23 is used for allowing the front end of the piston 16 to pass through the cylinder opening, and limiting the rear end of the piston 16 to pass through the cylinder opening, and specifically, in order to limit the movement of the piston 16, which is not affected by the stop collar 23, the front end of said piston 16 has dimensions smaller than the internal dimensions of the cylinder 15, namely, a gap is left between the front end of the piston 16 and the inner wall of the cylinder body 15, the specific gap size is larger than the width of the limit retainer ring 23, so that the front end of the piston 16 can pass through the limit stop ring 23, pass through the cylinder opening of the cylinder body 15, that is, the gap between the front end of the piston 16 and the inner wall of the cylinder 15 is a space for the rear end of the piston 16 to move, in addition, the size of the portion of the piston 16 except the front end should be larger than the size of the inner ring of the limit stop 23, and only the front end of the piston 16 can pass through the limit stop 23.

Because the front end of the piston 16 and the abdicating space for avoiding impurities from entering the cylinder body 15 from the cylinder opening affect the movement of the piston 16, in a further embodiment, a third sealing ring 24 is further sleeved between the limiting retainer ring 23 and the piston 16, such arrangement makes the abdicating space surrounded by the limiting retainer ring 23, the third sealing ring 24, the inner wall of the cylinder body 15 and the front end of the piston 16 to form a closed abdicating cavity 163, which can effectively prevent impurities from entering the abdicating space. Because the piston 16 needs to move towards the direction close to the cylinder opening, the abdicating cavity 163 is provided with the ventilation valve 164, and the ventilation valve 164 is kept in an open state when the release bearing mechanism is started to be installed and used, so that the abdicating cavity 163 is ensured to be communicated with the outside air, and the movement of the piston 16 is not influenced.

In a further embodiment, the cylinder opening of the cylinder body 15 is further provided with a circlip for hole 25, and the circlip for hole 25 is connected with the inner wall of the cylinder body 15 and abuts against the limit stop 23.

In order to pump gas into the annular air chamber 151 or pump gas out of the annular air chamber 151, in a further embodiment, the annular air chamber 151 is provided with a gas port 161, and the gas port 161 can be provided with a pagoda joint, and the gas port 161 is used for pumping gas into the annular air chamber 151 or exhausting gas in the annular air chamber 151 by a gas pump. An air pump may be connected to the air port 161 of the pagoda adapter through an external accessory solenoid valve, so that air (compressed air) is pumped into the annular air chamber 151 to push the piston 16 to move in a direction close to the front port of the shaft passage 150 until the piston 16 reaches a specified position (i.e., stopped by a stopper ring 23 described below), at which time the pushing member 20 presses the spring to a fixed stroke.

Since condensed oil gas is accumulated in the annular air chamber 151 when oil gas impurities exist in the introduced gas (compressed air) in the annular air chamber 151, in a further embodiment, the annular air chamber 151 is provided with a water outlet 162, the water outlet 162 may be provided with a pagoda joint, and the water outlet 162 is used for draining water. The pneumatic separating mechanism is mounted on the motor front end cover 6, specifically, is mounted on the motor front end cover 6 through the bolt 26, and is located when the cylinder body 15 is mounted between the gearbox 9 and the motor, the water outlet 162 is arranged downwards, the water outlet 162 is in a normally closed state, the water outlet 162 is opened when internal liquid needs to be discharged, condensed liquid deposited at the bottom of the annular air cavity 151 is discharged, cleanness of the annular air cavity 151 is guaranteed, the service life is prolonged, and the water outlet 162 is closed after discharging.

Referring to fig. 4, in a further embodiment, the water outlet 162 and the air outlet 161 are symmetrically installed at the cylinder 15, and specifically, when the water outlet 162 faces, the air outlet 161 faces upwards.

Referring to fig. 2 and 5, in a further embodiment, a proximity sensor 22 is further included, and the proximity sensor 22 is disposed at the cylinder 15 to detect whether the piston 16 is moved to a certain position. Whether the stroke of the clutch is in place after ventilation can be accurately judged through the proximity sensor 22, the gear shifting time can be shortened, closed-loop control can be realized, the effectiveness of each separation action is ensured, the proximity sensor 22 is preferably an inductive sensor, the inductive sensor is simple to install, does not need to be in mechanical contact with a measured object, has sensing performance, and is reliable in action and stable in performance.

The proximity sensor 22 is arranged at the end of the stroke of the piston 16, namely the position of the piston 16 when the pushing piece 20 presses the diaphragm spring 12 to the pressure plate 11 and the clutch driven plate 13, and the arrangement is such that when the starting release bearing mechanism is in use, the pushing piece 20 pushes the diaphragm spring 12 to a fixed stroke when the pushing piece 16 pushes the piston 16 to move towards the direction close to the cylinder opening until the piston 16 is blocked by the limit check ring 23, and meanwhile, the proximity sensor 22 at the end of the stroke of the piston 16 feeds back a signal that the piston 16 is in position, and then the separation of the pressure plate 11 and the clutch driven plate 13 is judged.

It should be noted that, although the above embodiments have been described herein, the scope of the present invention is not limited thereby. Therefore, based on the innovative concept of the present invention, the changes and modifications of the embodiments described herein, or the equivalent structure or equivalent process changes made by the contents of the specification and the drawings of the present invention, directly or indirectly apply the above technical solutions to other related technical fields, all included in the scope of the present invention.

Claims

1. A pneumatic separating mechanism is characterized by comprising a cylinder body, a piston and a pushing piece;

2. A pneumatic release mechanism according to claim 1, wherein the outer ring wall of the intermediate section of the piston projects outwardly to form a first annular lip and the inner side wall of the rear end of the cylinder projects inwardly to form a second annular lip; the rear end of the piston is sleeved with a first sealing ring, the rear end of the piston penetrates into the second annular bulge, the first sealing ring abuts against the inner ring wall of the second annular bulge, the first annular bulge is sleeved with a second sealing ring, and the second sealing ring abuts against the middle section of the cylinder body to form the annular air cavity in a surrounding mode.

3. The pneumatic release mechanism of claim 1, further comprising a bearing disposed between the pusher and the piston, wherein an outer race of the bearing is coupled to the piston and an inner race of the bearing is coupled to the pusher.

4. The pneumatic separation mechanism of claim 3, further comprising a locating post; the positioning column is arranged in the annular air cavity, is connected with the piston, and has the axial direction consistent with the moving direction of the piston; the inner wall of the cylinder body is provided with a blind hole, and a positioning column is inserted into the blind hole; when the piston moves, the positioning column moves axially in the blind hole and limits the piston to rotate.

5. The pneumatic separating mechanism of claim 1, wherein the annular air chamber is provided with an air port and a water discharge port, and the water discharge port is arranged downward for discharging water when the cylinder body is installed between the motor and the gearbox; the gas port is used for pumping gas into the annular gas cavity by the gas supply pump or discharging the gas in the annular gas cavity.

6. The pneumatic separating mechanism of claim 1, further comprising a proximity sensor provided at the cylinder to detect whether the piston is moved into position.

7. The pneumatic separating mechanism of claim 6, wherein the proximity sensor is an inductive sensor.

8. The pneumatic separating mechanism of claim 1, wherein a limit retainer is disposed at the cylinder opening of the cylinder body, and the limit retainer is used for allowing the front end of the piston to pass through the cylinder opening and limiting the rear end of the piston to pass through the cylinder opening.

9. The pneumatic separating mechanism according to claim 8, wherein a third sealing ring is further sleeved between the limiting check ring and the piston, the limiting check ring, the third sealing ring, the inner wall of the cylinder body and the front end of the piston define a closed abdicating cavity, and the abdicating cavity is provided with a ventilation valve.

10. The pneumatic separating mechanism of claim 1, wherein the cylinder opening of the cylinder body is further provided with a hole elastic check ring, and the hole elastic check ring is connected with the inner wall of the cylinder body and abuts against the limit check ring.