CN117605769A - Integrated clutch release system for differential response of AMT (automated mechanical transmission) - Google Patents
Integrated clutch release system for differential response of AMT (automated mechanical transmission) Download PDFInfo
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- CN117605769A CN117605769A CN202410095888.5A CN202410095888A CN117605769A CN 117605769 A CN117605769 A CN 117605769A CN 202410095888 A CN202410095888 A CN 202410095888A CN 117605769 A CN117605769 A CN 117605769A
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Abstract
The invention discloses an integrated clutch release system for differential response of an AMT (automated mechanical transmission), belonging to the technical field of clutches, comprising a clutch actuating mechanism, a connecting cavity and an electromagnetic valve group; the clutch actuating mechanism comprises a shell, wherein one end of the shell is provided with an air inlet and outlet hole, the connecting cavity is communicated with the shell through the air inlet and outlet hole, and the electromagnetic valve group is matched with the connecting cavity and used for regulating and controlling air inlet and air outlet of the connecting cavity; the piston is arranged in the shell, an elastic piece is arranged between the piston and the inner wall of the shell, and one end of the elastic piece, which is far away from the piston, is opposite to the air inlet and outlet holes; one end of the piston, which is far away from the elastic piece, is provided with a release bearing; the elastic piece comprises a cylindrical spring arranged in the middle and conical springs respectively arranged at two ends of the cylindrical spring, and one end of the conical spring with a large caliber is far away from the cylindrical spring. The invention can realize the effective matching of the piston and the spring, ensure the smooth operation of the piston, reduce the abrasion and prolong the service life.
Description
Technical Field
The invention belongs to the technical field of clutches, and particularly relates to an integrated clutch release system for differential response of an AMT (automated mechanical transmission).
Background
The AMT transmission is an electric control mechanical automatic transmission, integrates the functions of a manual transmission and an automatic transmission, has the advantages of simple structure, high transmission efficiency and low cost, and is increasingly applied to heavy-duty transmissions of commercial vehicles. The existing integrated AMT transmission is integrated with a gear selecting and shifting executing mechanism, a clutch executing mechanism and the like, and automatic gear shifting is completed through connection with an electronic control unit of the transmission. However, the existing AMT transmission has the problem of insufficient integration, which easily results in insufficient arrangement space, thereby causing faults and increasing installation complexity.
The invention of the publication CN104685249B relates to a decoupling system for a clutch of a motor vehicle using a drive which is in operative connection via a transmission with a piston which is arranged axially displaceably in a housing and in which the piston builds up pressure in a pressure chamber formed by the housing and the piston when actuated, the decoupling system having a sensor device for determining the position of the piston, the inductive sensor device being integrated into the decoupling system, the sensor device having an inductive sensor which is fixed to the housing, by means of which the position of an electrically conductive object to be detected can be determined. The invention makes it possible to carry out displacement measurement/position determination of the piston in a simple and cost-effective manner in a limited installation space.
The invention application with publication number of CN102330757A discloses an integrated design of a motor rotor support and a clutch hydraulic cylinder and application thereof, and relates to an integrated clutch hydraulic cylinder and a driving system for closing or separating a clutch by using the hydraulic cylinder. The drive system includes a housing, a stator, a rotor support, a clutch, and a hydraulic cylinder. The strength and the rigidity of the outer wall of the hydraulic cylinder body are enhanced, so that the hydraulic cylinder body not only bears the oil pressure in the cylinder, but also is used as a rotating support of a rotor bracket; a main shaft is arranged in a hole reserved in the middle of the hydraulic cylinder; the integrated design of the motor rotor support rotation support and the clutch hydraulic cylinder and the main shaft is realized. The clutch is connected with the rotor bracket through the coupling pair, the coupling pair is driven to be closed or separated through the telescopic movement of the piston, the motor power is superposed on the main shaft through the clutch in the closed state, and the main shaft motor is separated from the main shaft in the separated state. With this design, the structure is very compact.
However, the existing integrated clutch release system has increased requirements on the piston, and displacement friction can occur between the spring and the piston, so that piston abrasion and spring displacement are caused, even the flow rate of inlet and outlet air flow can be influenced, further, the piston is invalid, and faults are caused.
Disclosure of Invention
The invention aims to provide an integrated clutch release system with a simple structure and differential response of an AMT (automated mechanical transmission), which can realize effective matching of a piston and a spring, ensure smooth operation of the piston, reduce abrasion and prolong service life.
The technical scheme adopted by the invention for achieving the purpose is as follows:
an integrated clutch release system for differential response of an AMT transmission comprises a clutch actuating mechanism, a connecting cavity and an electromagnetic valve group; the clutch actuating mechanism comprises a shell, wherein one end of the shell is provided with an air inlet and outlet hole, the connecting cavity is communicated with the shell through the air inlet and outlet hole, and the electromagnetic valve group is matched with the connecting cavity and used for regulating and controlling air inlet and air outlet of the connecting cavity;
the piston is arranged in the shell, an elastic piece is arranged between the piston and the inner wall of the shell, and one end of the elastic piece, which is far away from the piston, is opposite to the air inlet and outlet holes; the piston can move back and forth in the shell; one end of the piston, which is far away from the elastic piece, is provided with a release bearing;
the elastic piece comprises a cylindrical spring arranged in the middle and conical springs respectively arranged at two ends of the cylindrical spring, and one end of the conical spring with a large caliber is far away from the cylindrical spring.
By adopting the technical scheme, the limit of the sliding distance of the piston can be realized by the structure of the cylindrical spring and the conical spring which are matched. Utilize elastic component and piston cooperation, piston and elastic component take place deformation and produce the displacement, for adopting traditional cylindricality spring, through conical spring and piston cooperation, utilize conical spring and piston zonulae occludens, avoid taking place great displacement friction between the two to conical spring structure can avoid the elastic component to block up business turn over gas pocket.
Further, the small-caliber end of the cone spring is fixedly connected with the cylindrical spring, for example, the cone spring and the cylindrical spring can be matched in a welding way. The end of the cylindrical spring may also be arranged to extend into the interior of the conical spring.
Therefore, in the process of compression deformation of the cylindrical spring and the conical spring, the cylindrical spring and the conical spring can be compressed to a certain length, the structure of the cylindrical spring and the conical spring combination enables multi-point contact to exist between the tail end of the compressed elastic piece and the piston, namely the contact surface of the conical spring and the piston is increased, and under extreme conditions, the tail end of the cylindrical spring can also be in contact with the end surface of the piston, so that the contact pressure between the elastic piece and the piston is relatively dispersed, and the piston failure caused by excessive extrusion of the piston can be avoided.
According to one embodiment of the invention, the end of the cone spring, which is far away from the cylindrical spring, is provided with a limiting piece; the limiting piece is made of flexible materials. Therefore, the tail ends of the cone springs arranged at the two ends of the elastic piece are elastically matched with the piston or the shell through the limiting piece.
Further, the limiting piece comprises a limiting base body, the middle of the limiting base body is provided with an assembly hole, and the tail end of the cone spring is sleeved in the assembly hole.
Furthermore, one side of the limiting base body is provided with a limiting bulge, and the limiting bulge is far away from the body of the cone spring; an arc-shaped plate is arranged on one side of the limiting base body, which is far away from the limiting bulge, and a groove body is arranged on the outer surface of the arc-shaped plate.
Therefore, a certain interval distance is reserved between the elastic piece and the end face of the piston and between the elastic piece and the inner side wall of the shell by using the limiting piece, the limiting piece is made of a relatively flexible material, and local deformation of the piston caused by direct contact between hard materials such as a cylindrical spring and a conical spring and the piston can be avoided.
According to one embodiment of the invention, the air inlet and outlet holes are matched with the filter assembly, the filter assembly comprises a mounting sleeve, one end of the mounting sleeve is communicated with the air inlet and outlet holes, a fan is arranged in the mounting sleeve and can rotate, and the two sides of the fan are provided with first filter plates.
From this, utilize filter unit to filter the air current that advances out the casing, fan drive air current flows, and the particulate matter that carries in the filtering air current of through first filter plate can avoid because of the piston cavity is too much that particulate matter in the casing promptly to prevent to slide unsmooth or slip inefficacy because of piston slip face frictional force increases and causes the piston. The fan can be matched with the motor, and the fan rotates under the drive of the motor, so that the air flow is guided to flow towards the air inlet and outlet hole direction of the shell, and the response speed of the piston and other parts is improved.
According to one embodiment of the invention, the side of the first filter plate, which is far away from the fan, is provided with a rectifying piece; the rectifying piece can be used for rectifying the air flow entering and exiting the shell, so that the unstable air pressure caused by the air flow disorder is prevented, the stable operation of the piston is ensured, and the occurrence of clamping is avoided. The rectifying piece comprises a rectifying base block and a second filter plate which are oppositely arranged, and the rectifying base block is connected with the second filter plate through a connecting net body; the rectifying base block is of a conical structure; the connecting net body is provided with continuous fold parts, and the fold parts are distributed around the axis of the connecting net body; the second filter plate is arranged opposite to the first filter plate, and a third spring is connected between the first filter plate and the second filter plate.
The air flow in the connecting cavity is filtered by the filtering component and then enters the air inlet and outlet holes of the shell and is matched with the rectifying piece. Specifically, the second filter plate of the air flow enters the rectifying part and is discharged from the side through the connecting net body, so that the air flow balance is improved. Because the connecting net body is of a net structure, the air flow is divided through the meshes on the connecting net body, the effect of uniform air flow can be achieved, and a large amount of high-speed air flow is prevented from directly entering the shell. The provision of the pleated portions to the connecting web body also helps to enhance the division and mixing effect of the air flow. The air flow changes the flow direction in the connecting net body and flows towards the connecting net body, and due to the arrangement of the fold parts, the air flow changes the flow direction again before being discharged from the rectifying piece, and the discharged air flow is caused to collide and meet again in a smaller space range, so that the mixing effect of the air flow entering the inside of the shell is improved.
In addition, the rectifying piece is elastically connected with the first filter plate, so that the rectifying piece generates shaking with a certain amplitude under the blowing action of the air flow, and the mixing of the air flow is promoted. The vibration of the rectifying piece can also prevent particles entrained in the air flow from blocking the connecting net body, so that the air flow is ensured to flow smoothly.
According to one embodiment of the invention, a guide cover body is arranged between the mounting sleeve and the air inlet and outlet holes, and the guide cover body is of a conical structure; the inner wall of the air guide sleeve body is provided with an air guide groove. Therefore, the air flow is guided to flow in or out from the air inlet and outlet holes on the shell by the air guide cover body, so that the filtering effect of the air flow entering and exiting the shell is ensured. The flow guiding groove is used for guiding the flow direction of the air flow and can be generally arranged in a linear or spiral structure.
Further, guide vanes are arranged on the inner wall of the guide hood body, one ends of the guide vanes are hinged with the guide hood body through a hinge shaft, and the guide vanes can rotate around the hinge shaft. The guide vane can turn around the hinge shaft under the blowing of the air flow, thereby being beneficial to strengthening the collision impact probability of the air flow piece and improving the air flow balance. In addition, the arrangement of the guide vanes and the guide grooves increases the surface area inside the guide cover body, and is also beneficial to collecting particles in the airflow.
According to one embodiment of the invention, the end of the piston facing the air inlet and outlet hole is provided with a first groove, and the first groove is matched with the elastic piece.
The end of the cone spring arranged at one end of the cylindrical spring is embedded in the first groove, the end of the cone spring arranged at the other end of the cylindrical spring is abutted with the inner wall of the shell, and the air inlet and outlet holes are formed in the cone spring.
Further, one end of the piston, which is far away from the first groove, is provided with a second groove, and the second groove is used for being matched with the release bearing.
According to one embodiment of the invention, the solenoid valve assembly comprises at least a fast inlet valve, a fast outlet valve, a slow inlet valve and a slow outlet valve.
Therefore, through the cooperation of the connecting cavity, the two air inlet valves and the two air outlet valves, up to 16 exhaust and air inlet combination modes can be realized, the exhaust or air inlet rate of the shell can be fast or slow, and the amount of exhaust or air inlet can be more or less, so that the omnibearing control is realized.
Drawings
FIG. 1 is a schematic diagram of an integrated clutch release system for differential response of an AMT transmission according to embodiment 1 of the present invention;
FIG. 2 is a schematic diagram of a piston structure of an integrated clutch release system for differential response of an AMT transmission according to embodiment 2 of the present invention;
FIG. 3 is a schematic cross-sectional view of the piston of FIG. 2;
FIG. 4 is a schematic view of a part of the enlarged structure of the portion A in FIG. 3;
FIG. 5 is a schematic diagram of the elastic member of an integrated clutch release system for differential response of an AMT transmission according to embodiment 2 of the present invention;
FIG. 6 is a schematic view of the stopper shown in FIG. 5;
FIG. 7 is a schematic view of the stop member shown in FIG. 6 at another angle;
FIG. 8 is a schematic diagram of an filtered component of an integrated clutch release system for differential response of an AMT transmission according to embodiment 3 of the present invention;
FIG. 9 is a schematic view of the filter assembly of FIG. 8 in a disassembled configuration;
FIG. 10 is a schematic view of the fairing of FIG. 8;
fig. 11 is a schematic structural view of the pod shown in fig. 8.
Reference numerals: a clutch actuator 11; a connecting cavity 12; a solenoid valve group 13; a housing 20; an air inlet and outlet hole 21; a release bearing 22; a piston 30; a first groove 31; a second groove 32; lubrication grooves 33; a return groove 34; an expansion section 35; a corner 36; an elastic member 40; a cylindrical spring 41; a conical spring 42; a stopper 43; a spacing matrix 44; a fitting hole 45; a limit projection 46; an arc-shaped plate 47; a tank 48; a filter assembly 50; a mounting sleeve 51; a fan 52; a first filter plate 54; a pod body 55; a diversion trench 56; a guide vane 57; a hinge shaft 58; a rectifying member 60; a rectifying base block 61; a second filter plate 63; a third spring 64; a connecting net body 65; a fold 66.
Detailed Description
The technical scheme of the invention is further described in detail below with reference to the detailed description and the accompanying drawings. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.
Example 1
FIG. 1 schematically illustrates an integrated clutch release system for differential response of an AMT transmission in accordance with an embodiment of the present invention. As shown in the figure, the device comprises a clutch actuating mechanism 11, a connecting cavity 12 and an electromagnetic valve group 13; the clutch actuator 11 includes a housing 20 with an air inlet and outlet 21 at one end, and a hollow cavity in the housing 20 is a clutch actuator cavity. The connecting cavity 12 is communicated with the shell 20 through an air inlet and outlet hole 21, and the electromagnetic valve group 13 is matched with the connecting cavity 12 and used for regulating and controlling air inlet and air outlet of the connecting cavity 12; a piston 30 is arranged in the shell 20, an elastic piece 40 is arranged between the piston 30 and the inner wall of the shell 20, and one end of the elastic piece 40, which is far away from the piston 30, is opposite to the air inlet and outlet holes 21; the piston 30 is capable of reciprocating inside the housing 20; the end of the piston 30 remote from the elastic member 40 is provided with a release bearing 22.
The electromagnetic valve group 13 includes at least a fast air inlet valve, a fast air outlet valve, a slow air inlet valve and a slow air outlet valve. The solenoid valve group 13 is operatively connected to and controlled by the transmission control unit. The transmission control unit is also connected to a speed sensor for monitoring the operating state of the clutch. Thus, by connecting the cavity 12 with the two air inlet valves and the two air outlet valves, up to 16 exhaust and air inlet combination modes can be realized, the exhaust or air inlet rate of the shell 20 can be fast or slow, and the amount of exhaust or air inlet can be more or less, so that the omnibearing control is realized. The specific control mode is as follows:
1. starting working conditions: the control unit of the gearbox controls the exhaust valve to be opened, controls the pressure of the cavity of the clutch actuator to slowly decrease, and under the action of the clutch release finger, the clutch is slowly closed to realize smooth starting; after judging that the clutch has no speed difference through the speed sensor signal, controlling the pressure of a clutch actuator cavity to quickly drop, and realizing quick closing of the clutch;
2. the clutch is opened before gear shifting: before the gear box starts to shift gears, the gear box control unit controls the air inlet valve to open, and the air is inflated into the clutch actuator cavity under the action of air source pressure to overcome the elasticity of the clutch release fingers until the clutch is completely released;
3. closing the clutch after shifting: after gear shifting of the gearbox is completed, the control unit of the gearbox controls the exhaust valve to be opened, controls the pressure of the cavity of the clutch actuator to be slowly reduced, and under the action of the clutch release finger, the clutch is slowly closed to realize smooth combination of the clutch, and after judging that the clutch has no speed difference through a speed sensor signal, the control unit controls the pressure of the cavity of the clutch actuator to be rapidly reduced to realize rapid closing of the clutch;
4. braking condition: and judging the running state of the vehicle according to the vehicle speed signal, the engine rotating speed signal and the brake signal, when the vehicle brakes to a low-speed state, the gearbox control unit controls the air inlet valve to be opened, and the inside of the clutch actuator cavity is rapidly inflated under the action of air source pressure, so that the elasticity of the clutch release finger is overcome, the clutch is completely released, and the vehicle is prevented from flameout.
Example 2
FIGS. 2-7 schematically illustrate an integrated clutch release system for differential response of an AMT transmission according to another embodiment of the present invention, differing from example 1 in that:
the elastic member 40 engaged with the piston 30 includes a cylindrical spring 41 provided in the middle portion and cone springs 42 provided at both ends of the cylindrical spring 41, and one end of the cone spring 42 having a large caliber is provided away from the cylindrical spring 41. The small-caliber end of the cone spring 42 is fixedly connected with the cylindrical spring 41, for example, the cone spring 42 and the cylindrical spring 41 can be matched in a welding way.
The cylindrical spring 41 and the conical spring 42 are matched, so that the sliding distance of the piston 30 can be limited. By utilizing the elastic element 40 to be matched with the piston 30, the piston 30 and the elastic element 40 deform and displace, compared with the traditional cylindrical spring 41, the conical spring 42 is matched with the piston 30, the conical spring 42 is tightly connected with the piston 30, larger displacement friction between the conical spring 42 and the piston 30 is avoided, and the conical spring 42 structure can prevent the elastic element 40 from blocking the air inlet and outlet holes 21. The arrangement of the cone spring 42 in the elastic piece 40 enables the stress site of the piston 30 to move outwards on one hand, and the arrangement of the cone spring 42 transmits the elastic force of the elastic piece 40 to the piston 30 through a larger contact ring, so that the response effect of the piston 30 can be improved; on the other hand, the cone spring 42 can reduce the probability of axial deviation in the deformation direction process of the elastic member 40, that is, ensure the coaxiality between the stress direction of the piston 30 and the axial line thereof, and ensure the stable stress of the piston 30, thereby ensuring the smooth movement of the piston 30 along the axial line direction, avoiding the jamming caused by the deformation disorder of the elastic member 40, and reducing the abrasion degree of the piston 30.
In addition, the end of the elastic member 40 away from the piston 30 is abutted with the inner side wall of the housing 20 through the larger contact ring at the end of the conical spring 42, so that the probability that the elastic member 40 shields the air inlet and outlet holes 21 can be reduced, and the smooth flow of the air flow in the housing 20 is ensured. Generally, an engagement groove may be provided on the inner sidewall of the housing 20 for engaging the conical spring 42 at the end of the elastic member 40. The engaging groove can avoid the position of the air inlet and outlet hole 21 as much as possible when the air inlet and outlet hole is arranged.
In the present embodiment, the tip of the cylindrical spring 41 protrudes into the interior of the cone spring 42. In this way, in the process of compression deformation of the cylindrical spring 41 and the conical spring 42, the cylindrical spring 41 and the conical spring 42 are compressed to a certain length, the combined structure of the cylindrical spring 41 and the conical spring 42 enables multi-point contact between the tail end of the compressed elastic piece 40 and the piston 30, that is, the contact surface between the conical spring 42 and the piston 30 is increased, and in extreme cases, the tail end of the cylindrical spring 41 can also be in contact with the end surface of the piston 30, so that the contact pressure between the elastic piece 40 and the piston 30 is relatively dispersed, and the failure of the piston 30 caused by excessive extrusion of the piston 30 can be avoided.
The cone spring 42 is provided with a limiting piece 43 at one end far away from the cylindrical spring 41; the stopper 43 is made of a flexible material. In this way, the ends of the cone springs 42 provided at both ends of the elastic member 40 are elastically engaged with the piston 30 or the housing 20 through the stopper 43.
Therefore, a certain distance is formed between the elastic member 40 and the end surface of the piston 30 and between the elastic member and the inner side wall of the housing 20 by using the limiting member 43, and thus, the limiting member 43 is made of a relatively flexible material, and the piston 30 local deformation caused by direct contact between the hard material such as the cylindrical spring 41 and the conical spring 42 and the piston 30 can be avoided.
In addition, after the cone spring 42 and the cylindrical spring 41 are compressed by the limiting member 43, a certain distance exists between the end face of the piston 30 and the inner side wall of the housing 20 and the tail end of the elastic member 40, so that the air flow can flow inside and outside the elastic member 40 conveniently, the stability of the air pressure inside the housing 20 can be ensured, and the piston 30 moving and blocking caused by unstable air pressure inside can be avoided.
Further, the limiting member 43 includes a limiting base 44, an assembly hole 45 is disposed in the middle of the limiting base 44, the assembly hole 45 penetrates through the limiting base 44, and the end of the conical spring 42 is sleeved inside the assembly hole 45. In this way, the connection stability between the stopper 43 and the coned spring 42 can be improved.
Preferably, one side of the limiting base 44 is provided with a limiting protrusion 46, and the limiting protrusion 46 is far away from the body of the cone spring 42; an arc-shaped plate 47 is arranged on one side of the limiting base body 44 away from the limiting projection 46, and a groove 48 is arranged on the outer surface of the arc-shaped plate 47.
The plurality of limiting protrusions 46 are uniformly distributed on one end face of the limiting member 43 and are abutted against the inner wall of the housing 20 or the end face of the piston 30, during the process of changing the air pressure in the housing 20, the piston 30 is displaced, the elastic member 40 is stressed to deform, and during the process, the limiting protrusions 46 are also deformed due to the flexible material of the limiting protrusions. For example, the limiting protrusion 46 is compressed during the compression process of the elastic member 40, so that the contact area between the limiting member 43 and the housing 20 or the piston 30 is increased, thereby reducing the pressure of the housing 20 or the piston 30, reducing the deformation probability of the piston 30, and prolonging the service life. The arrangement of the limiting protrusions 46 can help to ensure the stability of the contact sites between the conical spring 42 and the housing 20 or the piston 30, and the plurality of limiting protrusions 46 which are uniformly dispersed form gripping force on the housing 20 or the piston 30, so that axial deflection of the conical spring 42 in the expansion process can be avoided, the deformation direction of the elastic piece 40 is ensured to be stable, and further the stability of the piston 30 in the moving process is ensured.
When the elastic member 40 is compressed under force, the groove 48 can be movably matched with the body of the cone spring 42, and the cone spring 42 is compressed, so that one section close to the tail end is clamped inside the groove 48.
In addition, the end of the piston 30 facing the air inlet and outlet hole 21 is provided with a first groove 31, and the first groove 31 is matched with the elastic piece 40.
The tip of the cone spring 42 provided at one end of the column spring 41 is fitted inside the first groove 31, the tip of the cone spring 42 provided at the other end of the column spring 41 abuts against the inner wall of the housing 20, and the air inlet/outlet hole 21 is provided inside the cone spring 42.
Further, the end of the piston 30 remote from the first recess 31 is provided with a second recess 32, the second recess 32 being adapted to cooperate with the release bearing 22.
Further, the side wall of the piston 30 is provided with lubrication grooves 33. Lubrication groove 33 may be provided in a spiral or annular configuration opening around the side wall of piston 30. The interior of the piston 30 is provided with a lubrication channel which communicates with the lubrication groove 33. The end surface of the piston 30 provided with the first groove 31 is provided with a return groove 34, and the return groove 34 is communicated with the lubrication channel. One end of the notch of the return groove 34 is communicated with the lubrication groove 33 at the side of the piston 30, an expansion part 35 extending towards the middle part of the piston 30 is arranged at the bottom of the return groove 34, and the bottom end of the expansion part 35 is communicated with the lubrication channel. The return groove 34 is provided at the edge of the end face of the piston 30 and is not connected to the first groove 31 but is blocked by a rib or the like of the end face of the piston 30. In this way, in the process of lubricating the piston 30 with the lubricating oil, the lubricating oil is coated on the surface of the piston 30 through the lubricating groove 33 on the side of the piston 30, and the coating area of the lubricating oil is enlarged by friction of the surface, scraping of the lubricating groove 33 and the like in the process of reciprocating the piston 30, so that the lubricating oil is uniformly coated. And the excessive lubrication oil can re-enter the lubrication passage through the return groove 34 communicating with the lubrication groove 33, avoiding waste and preventing the lubrication oil from entering the inside of the first groove 31.
Further, the side of the expansion portion 35 near the outer wall of the piston 30 is streamlined to help guide the excessive lubricant to smoothly enter the expansion portion 35 along the streamlined side wall, and the side of the expansion portion 35 near the center of the piston 30 is provided with a corner portion 36, and the corner portion 36 may be provided with a multi-stage continuous bending structure for intercepting the lubricant inside the expansion portion 35. Furthermore, the corner 36 may be provided with an interception plate extending obliquely to the streamline side. The interception plate can be integrally formed with the piston 30, so that the interception plate also has certain flexibility, and can deform or incline along with the flow of the air flow in the process of changing the air pressure in the shell 20, thereby also helping to strengthen the interception effect of the lubricating oil in the expansion part 35.
Excess lubricating oil can be stored by the expansion part 35, so that the lubricating oil is prevented from entering the first groove 31, and the abnormal fit between the elastic piece 40 and the piston 30 caused by the transitional use amount of the lubricating oil is prevented. On the other hand, the provision of the expansion portion 35 increases the surface area of the piston 30, improves the sensitivity thereof in response to the change in the air pressure inside the housing 20, and ensures the smooth operation of the piston 30.
Example 3
Fig. 8 to 11 schematically show an integrated clutch release system for differential response of an AMT transmission according to still another embodiment of the invention, which is different from example 1 in that:
the air inlet and outlet holes 21 are matched with the filter assembly 50, the filter assembly 50 comprises a mounting sleeve 51, one end of the mounting sleeve 51 is communicated with the air inlet and outlet holes 21, a fan 52 is arranged in the mounting sleeve 51, the fan 52 can be matched with an output shaft of a motor, and the fan 52 is driven to rotate by the motor. The motor cooperates with the fastening links for fixing inside the mounting sleeve 51. The side wall of the mounting sleeve 51 is also provided with an assembly hole 45, so that the circuit connection of the motor is facilitated. The fan 52 is provided with first filter plates 54 on both sides, and the first filter plates 54 are provided on both side edges of the mounting bush 51.
Therefore, the filter assembly 50 is utilized to filter the air flow entering and exiting the housing 20, the fan 52 drives the air flow to flow, and the first filter plate 54 filters out the particles entrained in the air flow, so that excessive particles in the chamber of the piston 30, namely the housing 20, can be avoided, and the unsmooth sliding or sliding failure of the piston 30 caused by the increase of friction force of the sliding surface of the piston 30 can be prevented.
The fan 52 is driven by the motor to rotate, so that the airflow is guided to flow in the direction of the air inlet and outlet holes 21 of the housing 20, and the response speed of the piston 30 and other components is improved.
In addition, the first filter sheet 54 is provided with a rectifier 60 on a side remote from the fan 52. The rectifying member 60 can be used for rectifying the air flow entering and exiting the housing 20, so as to prevent the air pressure from being unstable caused by the turbulence of the air flow, thereby ensuring the stable operation of the piston 30 and avoiding the occurrence of jamming.
The rectifying member 60 includes a rectifying base block 61 and a second filter plate 63 which are disposed opposite to each other, and the rectifying base block 61 is connected to the second filter plate 63 through a connection net 65. The rectifying base block 61 may be provided in a conical or umbrella-shaped cover structure, and an open end, that is, an end having a larger diameter, is connected to the connecting net body 65. The connecting web 65 is provided with continuous folds 66, the folds 66 being distributed around the axis of the connecting web 65; the second filter plate 63 is disposed opposite the first filter plate 54, and a third spring 64 is connected between the first filter plate 54 and the second filter plate 63.
The air flow in the connecting cavity 12 is filtered by the filter assembly 50 and enters the air inlet and outlet holes 21 of the shell 20 and is matched with the rectifying piece 60. Specifically, the air flow second filter plate 63 enters the inside of the rectifying member 60 and is discharged from the side through the connection net 65, which contributes to the improvement of the air flow balance. Because the connection mesh body 65 is a mesh structure, the air flow is divided by the mesh holes on the connection mesh body, the effect of uniform air flow can be achieved, and a large amount of high-speed air flow is prevented from directly entering the inside of the shell 20. The provision of the pleated portions 66 to the connecting web 65 also helps to enhance the dividing and mixing effect of the air flow. The air flow changes the flow direction inside the connection net body 65 and flows towards the connection net body 65, and due to the arrangement of the fold portions 66, the air flow changes the flow direction again before being discharged from the rectifying member 60, and the discharged air flows are caused to collide and meet again in a smaller space range, which contributes to improving the mixing effect of the air flows entering the inside of the housing 20.
In addition, the rectifying member 60 is elastically connected to the first filter plate 54, so that the rectifying member 60 generates a certain amplitude of vibration under the blowing action of the air flow, which also helps to promote the mixing of the air flow. The vibration of the rectifying member 60 can also prevent the particulate matters entrained in the air flow from blocking the connecting net body 65, so as to ensure the smooth flow of the air flow.
Further, the connection net body 65 has a tapered structure, and a small opening end of the connection net body 65 is connected to the rectifying base block 61, and a large opening end is connected to the second filter plate 63.
Further, the connection net 65 is rotatably connected to the rectifying base block 61 and the second filter plate 63. Specifically, the end of the connection net 65 is connected to the rectifying base block 61 or the second filter plate 63 by a pivot bearing or the like.
Further, the connection net body 65 is of a multi-layer structure sleeved inside and outside, so that the airflows entering and exiting the rectifying member 60 are divided and converged for multiple times, the balance is improved, and the flow rates of the airflows with different flow directions tend to be constant.
In this way, the air flows from the larger diameter side of the connection net body 65 to the smaller diameter side during the flow of the air in the rectifying member 60, which contributes to the change of the flow direction of the air, and promotes the air flow to the outside of the connection net body 65. The rotation of the connecting net 65 also helps to generate a swirling flow in the discharged air flow, which can enhance the mixing effect of the air flow on the one hand and also helps to guide the air flow into the housing 20 rapidly on the other hand.
During the process of the air flow in the housing 20 entering the connecting cavity 12 through the air inlet and outlet holes 21, the filtering component 50 is also used for filtering, and the rectifying element 60 is used for rectifying, so that the flow of the air flow and the operation of the rectifying element 60 are similar to those described above, and the details are omitted here.
A guide cover body 55 is arranged between the mounting sleeve 51 and the air inlet and outlet holes 21, and the guide cover body 55 is of a conical structure; the inner wall of the pod body 55 is provided with a diversion trench 56. In this way, the air flow is guided by the air guide cover 55 to flow in or out from the air inlet and outlet holes 21 on the housing 20, so as to ensure the filtering effect on the air flow entering and exiting the housing 20. The flow guide grooves 56 are used to guide the flow direction of the air flow and may be generally arranged in a linear or spiral configuration. The side of the pod 55 opposite the second filter plate 63 in the fairing 60 may also be provided with a first filter plate 54, which first filter plate 54 acts identically to the first filter plate 54 provided at the end of the mounting sleeve 51 and is resiliently connected to the second filter plate 63 in the fairing 60 by a third spring 64.
Further, the inner wall of the guide cover body 55 is provided with guide vanes 57, one end of each guide vane 57 is hinged with the guide cover body 55 through a hinge shaft 58, and the guide vanes 57 can rotate around the hinge shaft 58. The guide vane 57 can turn around the hinge shaft 58 under the blowing of the air flow, thereby helping to strengthen the collision impact probability of the air flow piece and improve the air flow balance. In addition, the guide vane 57 and the guide groove 56 increase the surface area of the inner part of the guide cover 55, and also facilitate the collection of the particles in the airflow.
Conventional operations in the operation steps of the present invention are well known to those skilled in the art, and are not described herein.
While the foregoing embodiments have been described in detail in connection with the embodiments of the invention, it should be understood that the foregoing embodiments are merely illustrative of the invention and are not intended to limit the invention, and any modifications, additions, substitutions and the like made within the principles of the invention are intended to be included within the scope of the invention.
Claims (7)
1. An integrated clutch release system for differential response of an AMT transmission comprises a clutch actuating mechanism (11), a connecting cavity (12) and an electromagnetic valve group (13); it is characterized in that the method comprises the steps of,
the clutch actuating mechanism (11) comprises a shell (20) with an air inlet and outlet hole (21) at one end, the connecting cavity (12) is communicated with the shell (20) through the air inlet and outlet hole (21), and the electromagnetic valve group (13) is matched with the connecting cavity (12) and used for regulating and controlling air inlet and air outlet of the connecting cavity (12);
a piston (30) is arranged in the shell (20), an elastic piece (40) is arranged between the piston (30) and the inner wall of the shell (20), and one end, far away from the piston (30), of the elastic piece (40) is arranged opposite to the air inlet and outlet hole (21); one end of the piston (30) far away from the elastic piece (40) is provided with a release bearing (22);
the elastic piece (40) comprises a cylindrical spring (41) and cone springs (42) which are respectively arranged at two ends of the cylindrical spring (41), and one large-caliber end of each cone spring (42) is far away from the cylindrical spring (41).
2. An integrated clutch release system for differential response of an AMT transmission as claimed in claim 1, wherein,
one end of the cone spring (42) away from the cylindrical spring (41) is provided with a limiting piece (43); the limiting piece (43) comprises a limiting base body (44), an assembly hole (45) is formed in the middle of the limiting base body (44), and the tail end of the conical spring (42) is sleeved in the assembly hole (45);
one side of the limiting base body (44) is provided with a limiting protrusion (46), and the limiting protrusion (46) is far away from the body of the conical spring (42); an arc-shaped plate (47) is arranged on one side, far away from the limiting protrusion (46), of the limiting base body (44), and a groove body (48) is arranged on the outer surface of the arc-shaped plate (47).
3. An integrated clutch release system for differential response of an AMT transmission as claimed in claim 1, wherein,
the air inlet and outlet hole (21) is matched with the filter assembly (50), the filter assembly (50) comprises a mounting sleeve (51), one end of the mounting sleeve (51) is communicated with the air inlet and outlet hole (21), a fan (52) is arranged in the mounting sleeve (51), the fan (52) can rotate, and first filter plates (54) are arranged on two sides of the fan (52).
4. An integrated clutch release system for differential response of an AMT transmission as claimed in claim 3, wherein,
a rectifying piece (60) is arranged on one side, far away from the fan (52), of the first filter plate (54), the rectifying piece (60) comprises a rectifying base block (61) and a second filter plate (63) which are oppositely arranged, and the rectifying base block (61) is connected with the second filter plate (63) through a connecting net body (65); the connecting net body (65) is provided with continuous fold parts (66); the second filter plate (63) is arranged opposite to the first filter plate (54), and a third spring (64) is connected between the first filter plate (54) and the second filter plate (63).
5. An integrated clutch release system for differential response of an AMT transmission as claimed in claim 3, wherein,
a guide cover body (55) is arranged between the mounting sleeve (51) and the air inlet and outlet holes (21), and the guide cover body (55) is of a conical structure; the inner wall of the diversion cover body (55) is provided with a diversion trench (56).
6. An integrated clutch release system for differential response of an AMT transmission as claimed in claim 1, wherein,
one end of the piston (30) facing the air inlet and outlet hole (21) is provided with a first groove (31), and the first groove (31) is matched with the elastic piece (40).
7. An integrated clutch release system for differential response of an AMT transmission as claimed in claim 1, wherein,
the electromagnetic valve group (13) at least comprises a fast air inlet valve, a fast air outlet valve, a slow air inlet valve and a slow air outlet valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410095888.5A CN117605769B (en) | 2024-01-24 | 2024-01-24 | Integrated clutch release system for differential response of AMT (automated mechanical transmission) |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410095888.5A CN117605769B (en) | 2024-01-24 | 2024-01-24 | Integrated clutch release system for differential response of AMT (automated mechanical transmission) |
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| CN117605769A true CN117605769A (en) | 2024-02-27 |
| CN117605769B CN117605769B (en) | 2024-04-09 |
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| CN202410095888.5A Active CN117605769B (en) | 2024-01-24 | 2024-01-24 | Integrated clutch release system for differential response of AMT (automated mechanical transmission) |
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Also Published As
| Publication number | Publication date |
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| CN117605769B (en) | 2024-04-09 |
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