WO2021062980A1 - Transmission - Google Patents

Transmission Download PDF

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Publication number
WO2021062980A1
WO2021062980A1 PCT/CN2020/076747 CN2020076747W WO2021062980A1 WO 2021062980 A1 WO2021062980 A1 WO 2021062980A1 CN 2020076747 W CN2020076747 W CN 2020076747W WO 2021062980 A1 WO2021062980 A1 WO 2021062980A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
intermediate shaft
friction
shaft
synchronizer
Prior art date
Application number
PCT/CN2020/076747
Other languages
French (fr)
Chinese (zh)
Inventor
郑云兵
Original Assignee
郑云兵
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 郑云兵 filed Critical 郑云兵
Publication of WO2021062980A1 publication Critical patent/WO2021062980A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means

Definitions

  • the invention relates to a gear transmission, which is mainly applied to a 2-speed transmission in an electric vehicle.
  • the current transmission is mainly composed of a power input shaft connected with a power input gear, a power output shaft connected with a power output gear, a gear selector and a synchronizer are located on the power input shaft, an intermediate shaft and an intermediate shaft gear are connected, and the shift operation
  • the lever is connected with the gear selector, the synchronizer has a synchronizer friction part located in the gear sleeve, the power input shaft, the power output shaft and the intermediate shaft are connected with the housing through the bearing, and the power input shaft, the power output shaft and the shift lever One end extends out of the outer shell; the synchronizer friction member and the lubricating oil of the transmission are located in the same room or directly contact each other at the same time.
  • the power is transmitted by connecting the power input shaft and the power output shaft, or by connecting the power input shaft and the intermediate shaft, and then connected to the power output shaft through the intermediate shaft to transmit power and form Variable speed;
  • Synchronizer synchronization requires the speed of the two shafts to be docked, which makes the docking lighter and safer.
  • the synchronizer relies on the friction force of the friction part of the synchronizer to synchronize the speed of the two shafts.
  • the friction of the friction part of the synchronizer The greater the force, the shorter the shift time can be, and vice versa the longer the shift time.
  • the friction working surface of the friction member of the synchronizer is hereinafter referred to as "friction working surface" for short. It can be seen from the above that the existing transmissions of this type have the frictional working surface contacting the lubricating oil of the transmission, and the area of the frictional working surface is too small, which in turn causes the insufficient friction of the synchronizer friction member.
  • the frictional working surface will contact the lubricant of the transmission, and the area of the frictional working surface is too small, which in turn causes the insufficient friction of the synchronizer friction member.
  • the invention provides a transmission in which the friction working surface does not contact the lubricating oil of the transmission, and the friction working surface has a large area, thereby increasing the friction force of the synchronizer friction member.
  • the housing (1) is composed of a gear chamber (2) and a gear selection chamber (3), and the output shaft (26) is connected to the housing (1) via a bearing (10) It is located in the speed ratio gear chamber (2), and is located on the output shaft (26) in the speed ratio gear chamber (2). It is fixedly connected with gear A (27) and gear B (28).
  • the thick intermediate shaft ( 5) The thin intermediate shaft (4) penetrates into the hollow of the thin intermediate shaft (4), both ends of the thin intermediate shaft (4) respectively extend out of the two ends of the thick intermediate shaft (5), the thin intermediate shaft (4) and the thick intermediate shaft (5) Through bearing contact, one end of the thin intermediate shaft (4) and the thick intermediate shaft (5) is connected to the housing (1) through the bearing, and the housing (1) is fixedly connected with a plurality of shaft lockers (20), the thin intermediate shaft ( 4) There is a shaft lock (20) in the ring groove of the thick intermediate shaft (5), and one end of the thin intermediate shaft (4) and the thick intermediate shaft (5) is located in the speed ratio gear chamber (2) The other end is located in the gear selection chamber (3), and a gear R (6) is fixedly connected to the thin intermediate shaft (4) located in the speed ratio gear chamber (2), and the thick gear R (6) is located in the speed ratio gear chamber (2).
  • Gear S (7) is fixedly connected to the intermediate shaft (5), gear R (6) is meshed and connected with gear A (27), and gear S (7) is meshed and connected with gear B (28); a tubular friction seat (8) It is hollow and sleeved on the thick intermediate shaft (5) located in the gear selection chamber (3).
  • the hollow wall of the tubular friction seat (8) and the outer circle of the thick intermediate shaft (5) are toothed meshing connection, the friction seat (8) One axial end surface is connected with a thrust bearing (43), and the other end surface is connected with a friction plate (9).
  • One end of the friction seat (8) connected with the thrust bearing (43) faces the speed ratio gear chamber (2).
  • the shift frame (11) has a shift frame friction disc (31) and a tubular The shift cavity (32), the tubular synchronizer cavity (33) and the tubular shaft part (34) of the shift frame, the axial end surface of the shift frame friction disc (31) is the friction working surface, the shift frame friction disc (31) ) Facing the friction seat (8) and corresponding to and adjacent to the friction plate (9), a gear selection gear (14) is fixedly connected in the shift cavity (32), and the gear selection gear (14) is located between the gear T (13) In the middle of the axial direction of gear U (15), the gear selection gear (14) is a ring gear with internal teeth, and the gear selection gear (14) and external gear T (13) and gear U (15) are Corresponding gears that can be meshed, there is a gap between the gear selection gear (14) and gear T (13) and gear U (15) in the axial direction.
  • the synchronizer cavity (33) and the shift cavity (32) are connected at the junction There is a secondary friction plate (16), the friction plate (17), the spring seat (18) and the spring plate are located in the synchronizer cavity (33), and the friction plate (17) corresponds to the secondary friction plate (16) Relationship, the tubular shaft part (34) of the shift frame is connected to the housing (1) via a bearing, and the shift frame (11) is externally fixedly connected to the thrust bearing (29), which is preferably located in the shift cavity ( At 32), the thrust bearing (29) is connected with the pusher (22), the pusher (22) and the housing (1) are in a toothed meshing connection relationship, and the pusher (22) has a joystick extending out of the housing ( 1) Outer; the tubular shaft part (34) of the shift frame is toothed and connected with the input shaft (19), the input shaft (19) is connected with the input shaft seat (21) through the bearing, and the input shaft seat (21) is connected with the housing (1) ) Fixed connection, the shaft locker (20) is fixedly connected to the input shaft seat
  • the friction plate (9), the shift frame friction plate (31), the secondary friction plate (16) and the friction plate (17) are the friction parts of the synchronizer, and the contact surface between the friction plate and the friction plate is the friction On the working surface, the friction disc includes a friction disc (17) and a shift frame friction disc (31).
  • the advancer is an elastic element or an elastic element, the elastic element mainly includes a spring, and the elastic element mainly includes a pneumatic element that generates elasticity by compressed air, or an electric element that generates elasticity by electromagnetic force.
  • the friction plate (9) and the secondary friction plate (16) can be made of the friction block of the existing clutch plate or the material of the automobile brake friction block.
  • the friction plate (9) and the secondary friction plate (16) can also be a combination of an independent steel disc and a friction block, that is, a composite body in which friction blocks are connected to both sides of the steel disc in the axial direction, that is, with the existing There are the same structure and material of automobile clutch plates, and the same structure and principle of friction generated by extrusion.
  • An oil seal is provided between the thick intermediate shaft (5) and the thin intermediate shaft (4) and the shell.
  • the toothed meshing connection is a connection in which an externally toothed shaft is inserted into a tube shaft with internal teeth and meshed. The externally toothed shaft and the internally toothed tube shaft can move axially with each other. But they cannot rotate each other.
  • the fixed connection can also be understood as a state where the two are integrated or welded together.
  • the gear shift frame (11) can be cylindrical or frame-shaped, and can also be cylindrical with a grid wall.
  • the gear teeth of the gear selection gear (14) may also be located on two sides.
  • the thin intermediate shaft (4), the thick intermediate shaft (5), the output shaft (26), the input shaft (19) and the shift frame (11) are all coaxial, and are mutually parallel or nearly parallel.
  • the said axial direction is the axial direction of the thin intermediate shaft (4).
  • the function of the shaft locking device (20) is to prevent the axial movement of the shaft to be locked, but not to restrict the rotation of the shaft.
  • the transmission uses an input shaft (19) to connect with external power, and a hydraulic device (24) to connect with external gears to control power.
  • the gear selection gear (14) can be composed of an outer ring and an inner gear ring, and a rotation gap of 1-2 tooth widths can be left between the outer ring and the inner gear ring, and the gap is equally divided by a spring.
  • the main function of the advancer (12) is that when the shift frame (11) moves axially, before the gear selection gear (14) contacts and meshes with the gear T (13) or the gear U (15), In advance, let the friction seat (8) or friction disc (17) connected to the advancer (12) contact the shift frame (11) through the friction plate and generate friction, and give the friction seat connected to the advancer (12) (8) Or the friction disc (17) provides elasticity, so that the friction seat (8) or the friction disc (17) rotates synchronously with the shift frame (11).
  • the friction seat (8) and the friction disk (17) can be converted to each other; if the friction disk (17) is connected to the friction plate, the friction disk (17) is the friction seat, and the friction seat (8) is not If the friction plate is connected, it can be changed to a friction plate.
  • the input shaft (19) drives the shift frame (11) to rotate.
  • the gear selection gear (14) in the shift frame (11) does not mesh with the gear T (13). Without meshing with gear U (15), neither the thin intermediate shaft (4) nor the thick intermediate shaft (5) rotate at this time.
  • the signal will cause the hydraulic piston (25) to push the pusher (22) through the hydraulic (24), and the pusher (22) will change through the thrust bearing (29).
  • the stopper (11) is pushed to the end of the input shaft (19).
  • the secondary friction plate (16) on the shifter (11) first comes into contact with the friction disc (17), and then passes through the advancer (12).
  • the shift frame friction disc (31) on the shift frame (11) first contacts the friction plate (9) At this time, through the elastic force of the advancer (12), a strong friction force is generated between the shift frame friction disc (31) and the friction plate (9), so that the thick intermediate shaft (5) and the shift frame (11) Synchronous rotation, at this time the shift frame (11) continues to be advanced, so that the gear T (13) sleeves into the gear selection gear (14) and meshes with the gear (14), and the gear T (13) and the gear selection gear ( 14) After the meshing connection, the rotational power of the input shaft (19) is transmitted to the thick intermediate shaft (5) through the shift frame (11), and then to the output shaft through gear S (7) and gear B (28) (26) Parallel output. At this time, the thin intermediate shaft (4) is idling without load.
  • the diameter ratio of gear R (6) and gear A (27) is preset to be 1:1.4, and the diameter ratio of gear S (7) to gear B (28) is preset to be 1.4 to 1.
  • the ratio of low gear to high gear is 1:1.96.
  • the speed ratio can be adjusted as needed.
  • the friction working surface in the transmission will not contact the lubricating oil, and the friction part can be as large as the diameter of the inner cavity of the gear selection chamber (3).
  • the larger the friction working surface area the more pressure it can bear. Therefore, the friction member of the synchronizer has stronger friction force, and the transmission can also work normally.
  • the present invention achieves the objective.
  • the beneficial effects of the present invention are that the friction working surface in the transmission does not contact with the lubricating oil of the transmission, and the friction working surface has a large area, thereby increasing the friction force of the synchronizer friction member.
  • Fig. 1 is an external view of the first embodiment of the present invention.
  • Fig. 2 is a top view of Fig. 1.
  • Fig. 3 is an internal view of the first embodiment of the present invention, that is, the internal view of Fig. 1.
  • Figure 4 is a cross-sectional view of Figure 2 A-A, which is also a further cross-sectional view of Figure 3
  • Fig. 5 is a view showing that the shift carrier friction disc (31) on the shift carrier (11) has been in contact with the friction plate (9) and friction is generated during the hooking action from neutral to high gear.
  • Figure 6 is a view of the engagement action from neutral to high gear, and is a view that has been fully engaged; in this figure, the rotational power of the input shaft (19) can be transmitted to the thick intermediate shaft (5) through the shift frame (11) ), and then pass gear S (7) and gear B (28) to the output shaft (26) and output. At this time, the thin intermediate shaft (4) is in a no-load idling state.
  • Fig. 7 is a view showing that the secondary friction plate (16) has been in contact with the friction disc (17) and friction is generated during the hook-in action from the neutral gear to the low-speed gear.
  • Fig. 8 is a view of the engagement action of neutral gear to low-speed gear, and is a view that has been completely engaged; in this figure, the rotational power of the input shaft (19) can be transmitted to the thin intermediate shaft (4) through the shift frame (11) It is passed through gear R (6) and gear A (27) to the output shaft (26) and output. At this time, the thick intermediate shaft (5) is in a no-load idling state.
  • Fig. 9 is a view of the shift frame (11), the thin intermediate shaft (4) and the thick intermediate shaft (5) in Fig. 4, and some connected parts.
  • Figure 10 is a cross-sectional view of the shift frame (11) and a view of each part of the shift frame (11).
  • the tubular shaft part (34) of the shift frame in this view is separable from the rest of the shift frame (11) Set up.
  • Fig. 11 is a B-B cross-sectional view of the component of Fig. 9, in which the gear T (13) and the thick intermediate shaft (5) are integrated.
  • Figure 12 is a CC cross-sectional view of the component of Figure 9.
  • the gear selection gear (14) and the gear U (15) are not in meshing state, but the rear gear U (15) is visually seen; however, the gear selection gear ( 14)
  • the gear selection gear ( 14) For the meshing state with gear U (15), please refer to this view.
  • Fig. 13 is a D-D cross-sectional view of the part of Fig. 9.
  • Fig. 14 is an E-E cross-sectional view of the component of Fig. 9.
  • the thin intermediate shaft (4) and the friction disc (17) are in toothed meshing connection.
  • Fig. 15 is an internal view of the second embodiment.
  • Fig. 16 is an internal view of the third embodiment.
  • Figure 17 is an axial view of the relationship between the shift frame (11) and the gear selection gear (14), the shift frame (11) and the push frame (22), and the push frame (22) and the housing (1).
  • the cut-away part is combined with the view of the non-cut-away part.
  • Figure 18 is a gear selection gear (14) composed of an outer ring (44) and an inner gear ring (45).
  • gear selection gear (14) composed of an outer ring (44) and an inner gear ring (45).
  • Tooth width rotation gap, and the gap is equally divided left and right by the ring gear positioning spring (39).
  • the amount of the rotation gap is provided and limited by the combination of the outer ring groove (41) and the ring gear catch (40);
  • the ring gear (45) can passively rotate left and right within a limited range, and the direction of rotation is shown by the schematic arrow (42).
  • the inner ring gear (45) can passively rotate left and right within a limited range, which can solve the problem that the gear teeth (14) and the corresponding gears are aligned with each other and cannot be inserted into each other.
  • Shift frame tubular shaft part 35. Compressed air elastic device , 36. Pneumatic piston, 37. Electric elastic device, 38. Mandrel, 39. Gear ring positioning spring, 40. Gear ring card bamboo shoot, 41. Outer ring groove, 42. Signal arrow, 43. Thrust bearing, 44 .Outer ring, 45. Inner gear ring.
  • the housing (1) is composed of a speed ratio gear chamber (2) and a gear selection chamber (3), and the output shaft (26) is connected to the housing (1) via a bearing (10) It is located in the speed ratio gear chamber (2), and is located on the output shaft (26) in the speed ratio gear chamber (2). It is fixedly connected with gear A (27) and gear B (28).
  • the thick intermediate shaft ( 5) The thin intermediate shaft (4) penetrates into the hollow of the thin intermediate shaft (4), both ends of the thin intermediate shaft (4) respectively extend out of the two ends of the thick intermediate shaft (5), the thin intermediate shaft (4) and the thick intermediate shaft (5) Through bearing contact, one end of the thin intermediate shaft (4) and the thick intermediate shaft (5) is connected to the housing (1) through the bearing, and the housing (1) is fixedly connected with a plurality of shaft lockers (20), the thin intermediate shaft ( 4) There is a shaft lock (20) in the ring groove of the thick intermediate shaft (5), and one end of the thin intermediate shaft (4) and the thick intermediate shaft (5) is located in the speed ratio gear chamber (2) The other end is located in the gear selection chamber (3), and a gear R (6) is fixedly connected to the thin intermediate shaft (4) located in the speed ratio gear chamber (2), and the thick gear R (6) is located in the speed ratio gear chamber (2).
  • Gear S (7) is fixedly connected to the intermediate shaft (5), gear R (6) is meshed and connected with gear A (27), and gear S (7) is meshed and connected with gear B (28); a tubular friction seat (8) It is hollow and sleeved on the thick intermediate shaft (5) located in the gear selection chamber (3).
  • the hollow wall of the tubular friction seat (8) and the outer circle of the thick intermediate shaft (5) are toothed meshing connection, the friction seat (8) One axial end surface is connected with a thrust bearing (43), and the other end surface is connected with a friction plate (9).
  • One end of the friction seat (8) connected with the thrust bearing (43) faces the speed ratio gear chamber (2).
  • the shift frame (11) has a shift frame friction disc (31) and a tubular The shift cavity (32), the tubular synchronizer cavity (33) and the tubular shaft part (34) of the shift frame, the axial end surface of the shift frame friction disc (31) is the friction working surface, the shift frame friction disc (31) ) Facing the friction seat (8) and corresponding to and adjacent to the friction plate (9), a gear selection gear (14) is fixedly connected in the shift cavity (32), and the gear selection gear (14) is between the gear T (13) and The gear U (15) is in the middle of the axial direction.
  • the gear selection gear (14) is a ring gear with internal teeth.
  • the gear selection gear (14) and the external gear T (13) and gear U (15) are in meshing correspondence.
  • This advancer (12) is also a spring leaf.
  • the spring leaf contacts the thrust bearing (43) and provides the thrust bearing (43) and the friction seat (8) Axial elasticity.
  • An oil seal is provided between the thick intermediate shaft (5) and the thin intermediate shaft (4) and the shell.
  • the "toothed meshing connection” is a connection in which an externally toothed shaft is inserted into an internally toothed tube shaft and meshed.
  • the externally toothed shaft and the internally toothed tube shaft can be axially connected to each other. Move, but cannot rotate each other.
  • the fixed connection, the connection in which the two are fixed together, can also be understood as a state where the two are integrated or welded together.
  • the gear teeth of the gear selection gear (14) may also be located on the two end surfaces.
  • the thin intermediate shaft (4), the thick intermediate shaft (5), the output shaft (26), the input shaft (19) and the shift frame (11) are all coaxial, and are mutually parallel or nearly parallel.
  • the said axial direction is the axial direction of the thin intermediate shaft (4).
  • the function of the shaft locking device (20) is to prevent the axial movement of the shaft to be locked, but does not restrict the rotation of the shaft.
  • the transmission uses an input shaft (19) to connect external power, and a hydraulic device (24) to connect external gear to control power.
  • the gear selection gear (14) can be composed of an outer ring and an inner gear ring, and a rotation gap of 1-2 tooth widths can be left between the outer ring and the inner gear ring, and the gap is equally divided left and right by a spring.
  • the friction plate (9), the shift frame friction plate (31), the secondary friction plate (16) and the friction plate (17) mentioned above are the synchronizer friction parts.
  • the input shaft (19) drives the shift frame (11) to rotate.
  • the gear selection gear (14) in the shift frame (11) does not mesh with the gear T (13). Without meshing with gear U (15), neither the thin intermediate shaft (4) nor the thick intermediate shaft (5) rotate at this time.
  • the signal will cause the hydraulic piston (25) to push the pusher (22) through the hydraulic (24), and the pusher (22) will change through the thrust bearing (29).
  • the stopper (11) is pushed to the end of the input shaft (19).
  • the secondary friction plate (16) on the shifter (11) first comes into contact with the friction disc (17), and then passes through the advancer (12).
  • the shift frame friction disc (31) on the shift frame (11) first contacts the friction plate (9) At this time, through the elastic force of the advancer (12), a strong friction force is generated between the shift frame friction disc (31) and the friction plate (9), so that the thick intermediate shaft (5) and the shift frame (11) Synchronous rotation, at this time the shift frame (11) continues to be advanced, so that the gear T (13) sleeves into the gear selection gear (14) and meshes with the gear (14), and the gear T (13) and the gear selection gear ( 14) After the meshing connection, the rotational power of the input shaft (19) is transmitted to the thick intermediate shaft (5) through the shift frame (11), and then to the output shaft through gear S (7) and gear B (28) (26) Parallel output. At this time, the thin intermediate shaft (4) is idling without load.
  • the diameter ratio of gear R (6) and gear A (27) is preset to be 1:1.4, and the diameter ratio of gear S (7) to gear B (28) is preset to be 1.4 to 1.
  • the ratio of low gear to high gear is 1:1.96.
  • the speed ratio can be adjusted as needed.
  • the compressed air elastic device (35) is fixedly connected with the housing (1), and the pneumatic piston (36) is connected with the thrust bearing (43) on the friction seat (8);
  • the pressure piston (36) is the piston of the compressed air elastic device (35).
  • the compressed air elastic device (35) is a pneumatic element that generates elasticity by compressed air.
  • the inward pressure of the pneumatic piston (36) is caused by elastic force.
  • the compressed air elastic device (35) is the aforementioned advancer (12).
  • the working mode of the transmission in the second embodiment can be the first The transmission of each embodiment is understood.
  • the electric elastic device (37) is fixedly connected to the housing (1), and the ejector rod (38) is connected to the thrust bearing (43) on the friction seat (8); the ejector rod ( 38) is the iron core of the electric elastic device (37).
  • the electric elastic device (37) is an electric component that uses electromagnetic force to generate elasticity, and is also the aforementioned advancer (12).
  • the working mode of the electric elastic device (37) in the third embodiment is that it is always energized or energized before the speed change. After the electric elastic device (37) is energized, the ejector rod (38), which is the iron core, is driven by electromagnetic force. When the gear shifting action ends, the electric elastic device (37) can be powered off to save electric energy.
  • the advancer (12) adopts an electric elastic device (37)
  • the rest of the structure, components and working methods are the same as the transmission of the first embodiment; because the electric elastic device (37)
  • the role of the spring is the same as that of the first embodiment, and the working mode of the electric elastic device (37) is predictable. Therefore, the working mode of the transmission in the third embodiment can be the same as that of the first embodiment. Compare and understand.
  • the transmission of the present invention can be produced with existing equipment and materials.

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Abstract

A transmission, used in an electric car, and a speed ratio gear case (2) and a gear selection case (3) being provided in an outer housing (1) of the transmission. No lubricating oil able to contact or splash into a friction component of a synchronizer is provided in the gear selection case (3). A fine intermediate shaft (4) penetrates a tubular coarse intermediate shaft (5), both ends of the fine intermediate shaft (4) extending out from the coarse intermediate shaft (5), and the coarse intermediate shaft (5) and the fine intermediate shaft (4) being positioned in the speed ratio gear case (2) and the gear selection case (3). The coarse intermediate shaft (5) and the fine intermediate shaft (4) positioned in the speed ratio gear case (2) are meshed with gears (27, 28) of an output shaft (26) by means of gears (6, 7) connected to each. The coarse intermediate shaft (5) and the fine intermediate shaft (4) positioned in the gear selection case (2) are each connected to gears (13, 15) and a synchronizer component, and gear selection is completed by power connection of the gears (13, 15) and the synchronizer component to a gear selection gear (14) in a gearshift rack (11) and a synchronizer component of an additional part. An advancer (12) is provided in the synchronizer, and before a gear to be meshed makes contact, the advancer (12) is used to cause the synchronizer friction part to make contact in advance and produces a frictional force, thus causing the gearshift rack (11) to be synchronized with the coarse intermediate shaft (5) and the fine intermediate shaft (4). The gearshift rack (11) is connected to an input shaft (19), and is connected to a hydraulic device (24) by means of a bearing, causing external gear selection signal power to be implemented. Thus, the frictional force of the friction component of the synchronizer is greater.

Description

变速器transmission 技术领域Technical field
本发明涉及一种有挡位的变速器，主要应用于电动汽车中的2挡变速器。The invention relates to a gear transmission, which is mainly applied to a 2-speed transmission in an electric vehicle.
背景技术Background technique
目前的这种变速器主要有，由动力输入轴与动力输入齿轮连接，动力输出轴与动力输出齿轮连接，选挡器和同步器位于动力输入轴上，中间轴和中间轴齿轮连接，换档操纵杆与选挡器连接，同步器中有位于齿套内的同步器摩擦件，动力输入轴和动力输出轴以及中间轴通过轴承与外壳连接，动力输入轴和动力输出轴以及换档操纵杆的一端伸出外壳之外而成；所述的同步器摩擦件与变速器的润滑油，位于同一室内，或同时直接相互接触。现有的这种变速器在工作中，通过选择由动力输入轴和动力输出轴连接传输动力，或通过选择由动力输入轴与中间轴连接，再经中间轴与动力输出轴连接而传动动力以及形成变速；以同步器同步需要对接两轴的转速，而使得对接更轻便安全，而该同步器是依靠同步器摩擦件的摩擦力，进行同步要对接两轴的转速，该同步器摩擦件的摩擦力越大，换挡时间可以越短，反之换挡时间越长。现有的这种变速器，因同步器摩擦件与变速器的润滑油位于同一室内，使得在工作中飞溅的变速器润滑油，随时都会接触同步器摩擦件的摩擦工作面，或因同步器摩擦件与变速器润滑油直接相互接触，使同步器摩擦件的摩擦工作面也接触变速器的润滑油；而同步器摩擦件的摩擦工作面要接触润滑油，就会使得同步器摩擦件的摩擦系数小，进而引起该同步器摩擦件的摩擦力很小。现有的这种变速器，因同步器摩擦件要位于齿套内，因此同步器摩擦件的摩擦工作面面积过小，进而使该同步器摩擦件能承受的压力过小。所述的同步器摩擦件的摩擦工作面，以下简称为“摩擦工作面”。由上述可见，现有的这种变速器存在有，摩擦工作面会与变速器的润滑油接触，以及摩擦工作面的面积过小，进而引起同步器摩擦件摩擦力小的不足。The current transmission is mainly composed of a power input shaft connected with a power input gear, a power output shaft connected with a power output gear, a gear selector and a synchronizer are located on the power input shaft, an intermediate shaft and an intermediate shaft gear are connected, and the shift operation The lever is connected with the gear selector, the synchronizer has a synchronizer friction part located in the gear sleeve, the power input shaft, the power output shaft and the intermediate shaft are connected with the housing through the bearing, and the power input shaft, the power output shaft and the shift lever One end extends out of the outer shell; the synchronizer friction member and the lubricating oil of the transmission are located in the same room or directly contact each other at the same time. In the work of the existing transmission, the power is transmitted by connecting the power input shaft and the power output shaft, or by connecting the power input shaft and the intermediate shaft, and then connected to the power output shaft through the intermediate shaft to transmit power and form Variable speed; Synchronizer synchronization requires the speed of the two shafts to be docked, which makes the docking lighter and safer. The synchronizer relies on the friction force of the friction part of the synchronizer to synchronize the speed of the two shafts. The friction of the friction part of the synchronizer The greater the force, the shorter the shift time can be, and vice versa the longer the shift time. In the existing transmission, because the synchronizer friction part and the lubricant oil of the transmission are located in the same room, the transmission lubricant splashing during work will always contact the friction working surface of the synchronizer friction part, or the friction part of the synchronizer will be in contact with the lubricant. Transmission lubricating oil is in direct contact with each other, so that the friction working surface of the synchronizer friction member also contacts the lubricating oil of the transmission; and the friction working surface of the synchronizer friction member must contact the lubricant, which will make the friction coefficient of the synchronizer friction member small, and then The friction caused by the friction member of the synchronizer is very small. In the existing transmission, because the synchronizer friction member is located in the gear sleeve, the friction working surface area of the synchronizer friction member is too small, and the pressure that the synchronizer friction member can bear is too small. The friction working surface of the friction member of the synchronizer is hereinafter referred to as "friction working surface" for short. It can be seen from the above that the existing transmissions of this type have the frictional working surface contacting the lubricating oil of the transmission, and the area of the frictional working surface is too small, which in turn causes the insufficient friction of the synchronizer friction member.
技术问题technical problem
为了克服现有的这种变速器，存在有摩擦工作面会与变速器的润滑油接触，以及摩擦工作面的面积过小，进而引起同步器摩擦件摩擦力小的不足。本发明提供一种变速器，该变速器中的摩擦工作面不与变速器的润滑油接触，且摩擦工作面面积大，进而使同步器摩擦件的摩擦力更大。In order to overcome the existing transmissions of this kind, the frictional working surface will contact the lubricant of the transmission, and the area of the frictional working surface is too small, which in turn causes the insufficient friction of the synchronizer friction member. The invention provides a transmission in which the friction working surface does not contact the lubricating oil of the transmission, and the friction working surface has a large area, thereby increasing the friction force of the synchronizer friction member.
技术解决方案Technical solutions
本发明解决其技术问题所采用的技术方案是：外壳（1）由速比齿轮室（2）和选挡室（3）组成，输出轴（26）经轴承（10）与外壳（1）连接并位于速比齿轮室（2）内，位于速比齿轮室（2）内的输出轴（26）上，固定连接有齿轮A（27）和齿轮B（28），在管状的粗中间轴（5）的中空内穿入细中间轴（4），细中间轴（4）的2端分别都伸出粗中间轴（5）的两端，细中间轴（4）与粗中间轴（5）经轴承接触，细中间轴（4）与粗中间轴（5）的一端经轴承连接在外壳（1）上，外壳（1）上固定连接有多个锁轴器（20），细中间轴（4）与粗中间轴（5）的环槽内都有个锁轴器（20）的部分卡入，细中间轴（4）与粗中间轴（5）的一端位于速比齿轮室（2）内，另一端位于选挡室（3）内，位于速比齿轮室（2）内的细中间轴（4）上固定连接有齿轮R（6），位于速比齿轮室（2）内的粗中间轴（5）上固定连接有齿轮S（7），齿轮R（6）与齿轮A（27）啮合连接，齿轮S（7）与齿轮B（28）啮合连接；管状的摩擦座（8）以中空，套在位于选挡室（3）内的粗中间轴（5）上，管状的摩擦座（8）的中空壁与粗中间轴（5）的外圆为齿式啮合连接，摩擦座（8）的一个轴向端面连接有推力轴承（43），另一个端面上连接有摩擦片（9），该摩擦座（8）连接有推力轴承（43）的一端朝向速比齿轮室（2），位于该选挡室（3）内的粗中间轴（5）端头，固定连接齿轮T（13）；在选挡室（3）内，伸出粗中间轴（5）的细中间轴（4）段上，从伸出处至轴头端依次连接齿轮U（15）、摩擦盘（17）和弹簧座（18），细中间轴（4）与齿轮U（15）以及弹簧座（18）为固定连接，细中间轴（4）与摩擦盘（17）为齿式啮合连接关系，弹簧座（18）上固定连接提前器（12），所述的提前器（12）为弹簧片，该弹簧片接触摩擦盘（17），并向摩擦盘（17）提供轴向弹力；选挡室（3）内的齿轮T（13）、齿轮U（15）、摩擦盘（17）和弹簧座（18）的径向外套有换挡架（11），所述的弹簧片也被套在换挡架（11）内，该换挡架（11）有换挡架摩擦盘（31）、管状的换挡腔（32）、管状的同步器腔（33）和换挡架管状轴部分（34），换挡架摩擦盘（31）的轴向端面为摩擦工作面，换挡架摩擦盘（31）朝向摩擦座（8），并与摩擦片（9）对应且临近，换挡腔（32）内固定连接有选挡齿轮（14），选挡齿轮（14）介于齿轮T（13）与齿轮U（15）轴向的中间，选挡齿轮（14）为有内齿的齿圈，选挡齿轮（14）与外齿的齿轮T（13）以及齿轮U（15）是可啮合的对应齿轮，选挡齿轮（14）与齿轮T（13）以及齿轮U（15）的轴向间留有间隙，同步器腔（33）与换挡腔（32）交接处内，连接有副摩擦片（16），所述的摩擦盘（17）和弹簧座（18）以及弹簧片位于该同步器腔（33）内，该摩擦盘（17）与副摩擦片（16）为对应关系，换挡架管状轴部分（34）经轴承与外壳（1）连接，换挡架（11）外固定连接受推轴承（29），该受推轴承（29）最好位于换挡腔（32）处，受推轴承（29）与推架器（22）连接，推架器（22）与外壳（1）为齿式啮合连接关系，推架器（22）有操纵杆伸出外壳（1）外；换挡架管状轴部分（34）与输入轴（19）齿式啮合连接，输入轴（19）经轴承与输入轴座（21）连接，输入轴座（21）与外壳（1）固定连接，锁轴器（20）固定连接在输入轴座（21）上，并有部分锁轴器（20）体卡入输入轴（19）的环槽内；外壳（1）上固定连接有液压器（24），液压器（24）中的液压器活塞（25），通过轴状销（23）与推架器（22）伸出外壳（1）外的操纵杆连接，外壳（1）的选挡室（3）内固定连接有提前器（12），这个提前器（12）也为弹簧片，该弹簧片接触推力轴承（43），并为该推力轴承（43）以及摩擦座（8）提供轴向的弹力。所述的摩擦片（9）、换挡架摩擦盘（31）、副摩擦片（16）和摩擦盘（17）是同步器摩擦件，摩擦片与摩擦盘的接触面，就是所述的摩擦工作面，所述的摩擦盘包括摩擦盘（17）和换挡架摩擦盘（31）。所述的提前器为弹性件或弹性元件，弹性件主要有弹簧，弹性元件主要有以压缩空气产生弹性的气动元件，又或是用电磁力产生弹性的电动元件。所述的摩擦片（9）和副摩擦片（16），可采用现有离合器片的摩擦块或汽车刹车摩擦块的材料。所述的摩擦片（9）和副摩擦片（16），也可以为独立的钢盘与摩擦块的结合体，也就是钢盘轴向两边都连接有摩擦块的复合体，也就是与现有汽车离合器片相同的结构和材料，以及相同的挤压产生摩擦的结构与原理。所述的粗中间轴（5）与细中间轴（4）以及外壳之间，都设置有油封。所述的齿式啮合连接，是一种外齿式轴***在有内齿式的管轴中并啮合的连接，外齿式轴与内齿式的管轴之间，可以相互轴向移动，但不能相互转动。所述的固定连接，式两者固定在一起的连接，也可以理解为两者是一体的或是焊接在一起的状态。所述的换挡架（11），可以为筒状或框架状，还可以为网格壁的筒状。所述选挡齿轮（14）的轮齿，也可以位于两个侧面上。所述的细中间轴（4）、粗中间轴（5）、输出轴（26）、输入轴（19）以及换挡架（11）都是同轴向的，并且为相互平行或接***行。所述的轴向，就是细中间轴（4）的轴向。所述的锁轴器（20）的作用，为阻止被锁轴的轴向移动，但不限制该轴的转动。该变速器以输入轴（19）连接外部动力，以液压器（24）连接外部挡位控制动力。所述的选挡齿轮（14）可以由外圈和内齿圈组成，外圈和内齿圈之间可以留有1-2个齿宽的转动间隙，并以弹簧将该间隙左右等分。所述的提前器（12）的主要作用是，当换挡架（11）轴向移动时，在选挡齿轮（14）要与齿轮T（13）或齿轮U（15）接触并啮合前，提前让提前器（12）所连接的摩擦座（8）或摩擦盘（17），通过摩擦片与换挡架（11）接触并产生摩擦力，以及给提前器（12）所连接的摩擦座（8）或摩擦盘（17）提供弹力，进而使摩擦座（8）或摩擦盘（17）与换挡架（11）同步转动。The technical solution adopted by the present invention to solve its technical problem is: the housing (1) is composed of a gear chamber (2) and a gear selection chamber (3), and the output shaft (26) is connected to the housing (1) via a bearing (10) It is located in the speed ratio gear chamber (2), and is located on the output shaft (26) in the speed ratio gear chamber (2). It is fixedly connected with gear A (27) and gear B (28). The thick intermediate shaft ( 5) The thin intermediate shaft (4) penetrates into the hollow of the thin intermediate shaft (4), both ends of the thin intermediate shaft (4) respectively extend out of the two ends of the thick intermediate shaft (5), the thin intermediate shaft (4) and the thick intermediate shaft (5) Through bearing contact, one end of the thin intermediate shaft (4) and the thick intermediate shaft (5) is connected to the housing (1) through the bearing, and the housing (1) is fixedly connected with a plurality of shaft lockers (20), the thin intermediate shaft ( 4) There is a shaft lock (20) in the ring groove of the thick intermediate shaft (5), and one end of the thin intermediate shaft (4) and the thick intermediate shaft (5) is located in the speed ratio gear chamber (2) The other end is located in the gear selection chamber (3), and a gear R (6) is fixedly connected to the thin intermediate shaft (4) located in the speed ratio gear chamber (2), and the thick gear R (6) is located in the speed ratio gear chamber (2). Gear S (7) is fixedly connected to the intermediate shaft (5), gear R (6) is meshed and connected with gear A (27), and gear S (7) is meshed and connected with gear B (28); a tubular friction seat (8) It is hollow and sleeved on the thick intermediate shaft (5) located in the gear selection chamber (3). The hollow wall of the tubular friction seat (8) and the outer circle of the thick intermediate shaft (5) are toothed meshing connection, the friction seat (8) One axial end surface is connected with a thrust bearing (43), and the other end surface is connected with a friction plate (9). One end of the friction seat (8) connected with the thrust bearing (43) faces the speed ratio gear chamber (2). ), the end of the thick intermediate shaft (5) located in the gear selection chamber (3) is fixedly connected to the gear T (13); in the gear selection chamber (3), the thin intermediate shaft extending from the thick intermediate shaft (5) (4) In paragraph (4), connect gear U (15), friction disc (17) and spring seat (18) in order from the extension to the shaft head end, thin intermediate shaft (4) and gear U (15) and spring seat (18) ) Is a fixed connection, the thin intermediate shaft (4) and the friction disc (17) are in a toothed meshing connection, and the spring seat (18) is fixedly connected to the advancer (12), and the advancer (12) is a spring leaf, The spring plate contacts the friction disk (17) and provides axial elasticity to the friction disk (17); the gear T (13), gear U (15), friction disk (17) and spring seat in the gear selection chamber (3) The radial casing of (18) has a shift frame (11), and the spring sheet is also sleeved in the shift frame (11). The shift frame (11) has a shift frame friction disc (31) and a tubular The shift cavity (32), the tubular synchronizer cavity (33) and the tubular shaft part (34) of the shift frame, the axial end surface of the shift frame friction disc (31) is the friction working surface, the shift frame friction disc (31) ) Facing the friction seat (8) and corresponding to and adjacent to the friction plate (9), a gear selection gear (14) is fixedly connected in the shift cavity (32), and the gear selection gear (14) is located between the gear T (13) In the middle of the axial direction of gear U (15), the gear selection gear (14) is a ring gear with internal teeth, and the gear selection gear (14) and external gear T (13) and gear U (15) are Corresponding gears that can be meshed, there is a gap between the gear selection gear (14) and gear T (13) and gear U (15) in the axial direction. The synchronizer cavity (33) and the shift cavity (32) are connected at the junction There is a secondary friction plate (16), the friction plate (17), the spring seat (18) and the spring plate are located in the synchronizer cavity (33), and the friction plate (17) corresponds to the secondary friction plate (16) Relationship, the tubular shaft part (34) of the shift frame is connected to the housing (1) via a bearing, and the shift frame (11) is externally fixedly connected to the thrust bearing (29), which is preferably located in the shift cavity ( At 32), the thrust bearing (29) is connected with the pusher (22), the pusher (22) and the housing (1) are in a toothed meshing connection relationship, and the pusher (22) has a joystick extending out of the housing ( 1) Outer; the tubular shaft part (34) of the shift frame is toothed and connected with the input shaft (19), the input shaft (19) is connected with the input shaft seat (21) through the bearing, and the input shaft seat (21) is connected with the housing (1) ) Fixed connection, the shaft locker (20) is fixedly connected to the input shaft seat (21), and part of the shaft locker (20) is locked into the ring groove of the input shaft (19); the housing (1) is fixedly connected There is a hydraulic device (24), the hydraulic device piston (25) in the hydraulic device (24) is connected with the joystick of the push frame (22) that protrudes out of the housing (1) through a shaft pin (23), and the housing (1) ) Is fixedly connected with an advancer (12) in the gear selection chamber (3), this advancer (12) is also a spring leaf, which contacts the thrust bearing (43), and is the thrust bearing (43) and the friction seat (8) Provide axial elasticity. The friction plate (9), the shift frame friction plate (31), the secondary friction plate (16) and the friction plate (17) are the friction parts of the synchronizer, and the contact surface between the friction plate and the friction plate is the friction On the working surface, the friction disc includes a friction disc (17) and a shift frame friction disc (31). The advancer is an elastic element or an elastic element, the elastic element mainly includes a spring, and the elastic element mainly includes a pneumatic element that generates elasticity by compressed air, or an electric element that generates elasticity by electromagnetic force. The friction plate (9) and the secondary friction plate (16) can be made of the friction block of the existing clutch plate or the material of the automobile brake friction block. The friction plate (9) and the secondary friction plate (16) can also be a combination of an independent steel disc and a friction block, that is, a composite body in which friction blocks are connected to both sides of the steel disc in the axial direction, that is, with the existing There are the same structure and material of automobile clutch plates, and the same structure and principle of friction generated by extrusion. An oil seal is provided between the thick intermediate shaft (5) and the thin intermediate shaft (4) and the shell. The toothed meshing connection is a connection in which an externally toothed shaft is inserted into a tube shaft with internal teeth and meshed. The externally toothed shaft and the internally toothed tube shaft can move axially with each other. But they cannot rotate each other. The fixed connection, the connection in which the two are fixed together, can also be understood as a state where the two are integrated or welded together. The gear shift frame (11) can be cylindrical or frame-shaped, and can also be cylindrical with a grid wall. The gear teeth of the gear selection gear (14) may also be located on two sides. The thin intermediate shaft (4), the thick intermediate shaft (5), the output shaft (26), the input shaft (19) and the shift frame (11) are all coaxial, and are mutually parallel or nearly parallel. The said axial direction is the axial direction of the thin intermediate shaft (4). The function of the shaft locking device (20) is to prevent the axial movement of the shaft to be locked, but not to restrict the rotation of the shaft. The transmission uses an input shaft (19) to connect with external power, and a hydraulic device (24) to connect with external gears to control power. The gear selection gear (14) can be composed of an outer ring and an inner gear ring, and a rotation gap of 1-2 tooth widths can be left between the outer ring and the inner gear ring, and the gap is equally divided by a spring. The main function of the advancer (12) is that when the shift frame (11) moves axially, before the gear selection gear (14) contacts and meshes with the gear T (13) or the gear U (15), In advance, let the friction seat (8) or friction disc (17) connected to the advancer (12) contact the shift frame (11) through the friction plate and generate friction, and give the friction seat connected to the advancer (12) (8) Or the friction disc (17) provides elasticity, so that the friction seat (8) or the friction disc (17) rotates synchronously with the shift frame (11).
所述的摩擦座（8）和摩擦盘（17），是可以相互转换的；如果摩擦盘（17）连接了摩擦片，则摩擦盘（17）就是摩擦座，而摩擦座（8）不与摩擦片连接，则可以改为摩擦盘。The friction seat (8) and the friction disk (17) can be converted to each other; if the friction disk (17) is connected to the friction plate, the friction disk (17) is the friction seat, and the friction seat (8) is not If the friction plate is connected, it can be changed to a friction plate.
该变速器在工作时，输入轴（19）带动换挡架（11）转动，当选择为空挡时，换挡架（11）中的选挡齿轮（14）不与齿轮T（13）啮合，也不与齿轮U（15）啮合， 此时细中间轴（4）和粗中间轴（5）都不转。当外部输入低速挡的液压力控制信号，该信号通过液压器（24）使液压器活塞（25），推动推架器（22），推架器（22）通过受推轴承（29）将换挡架（11）推向输入轴（19）端，在推进的过程中，换挡架（11）上的副摩擦片（16）先与摩擦盘（17）接触，此时通过提前器（12）的弹力，使副摩擦片（16）与摩擦盘（17）之间产生强大的摩擦力，从而使细中间轴（4）与换挡架（11）同步转动，此时换挡架（11）继续被推进，使得齿轮U（15）套进选挡齿轮（14）内并与挡齿轮（14）啮合连接，齿轮U（15）与选挡齿轮（14）啮合连接后，输入轴（19）的旋转动力，通过换挡架（11）传递到细中间轴（4）上，再经齿轮R（6）与齿轮A（27），递到输出轴（26）上并输出，此时粗中间轴（5）为无负载的空转。在空挡时，当外部输入高速挡的液压力控制信号，该信号通过液压器（24）使液压器活塞（25），推动推架器（22），推架器（22）通过受推轴承（29）将换挡架（11）推向速比齿轮室（2）端，在推进的过程中，换挡架（11）上的换挡架摩擦盘（31）先与摩擦片（9）接触，此时通过提前器（12）的弹力，使换挡架摩擦盘（31）与摩擦片（9）之间产生强大的摩擦力，从而使粗中间轴（5）与换挡架（11）同步转动，此时换挡架（11）继续被推进，使得齿轮T（13）套进选挡齿轮（14）内并与挡齿轮（14）啮合连接，齿轮T（13）与选挡齿轮（14）啮合连接后，输入轴（19）的旋转动力，通过换挡架（11）传递到粗中间轴（5）上，再经齿轮S（7）与齿轮B（28），递到输出轴（26）上并输出，此时细中间轴（4）为无负载的空转。When the transmission is working, the input shaft (19) drives the shift frame (11) to rotate. When neutral is selected, the gear selection gear (14) in the shift frame (11) does not mesh with the gear T (13). Without meshing with gear U (15), neither the thin intermediate shaft (4) nor the thick intermediate shaft (5) rotate at this time. When the low-speed hydraulic pressure control signal is input from the outside, the signal will cause the hydraulic piston (25) to push the pusher (22) through the hydraulic (24), and the pusher (22) will change through the thrust bearing (29). The stopper (11) is pushed to the end of the input shaft (19). During the advancing process, the secondary friction plate (16) on the shifter (11) first comes into contact with the friction disc (17), and then passes through the advancer (12). ) The elastic force produces strong friction between the secondary friction plate (16) and the friction disc (17), so that the thin intermediate shaft (4) and the shift frame (11) rotate synchronously. At this time, the shift frame (11) ) Continues to be propelled so that the gear U (15) is inserted into the gear selection gear (14) and meshed and connected with the gear gear (14). After the gear U (15) is meshed and connected with the gear selection gear (14), the input shaft (19) ) Is transmitted to the thin intermediate shaft (4) through the shift frame (11), and then passed to the output shaft (26) and output via gear R (6) and gear A (27). The intermediate shaft (5) is idling without load. In neutral, when the external input high-speed hydraulic pressure control signal, the signal through the hydraulic (24) to make the hydraulic piston (25) push the pusher (22), the pusher (22) through the thrust bearing ( 29) Push the shift frame (11) to the end of the speed ratio gear chamber (2). During the advancing process, the shift frame friction disc (31) on the shift frame (11) first contacts the friction plate (9) At this time, through the elastic force of the advancer (12), a strong friction force is generated between the shift frame friction disc (31) and the friction plate (9), so that the thick intermediate shaft (5) and the shift frame (11) Synchronous rotation, at this time the shift frame (11) continues to be advanced, so that the gear T (13) sleeves into the gear selection gear (14) and meshes with the gear (14), and the gear T (13) and the gear selection gear ( 14) After the meshing connection, the rotational power of the input shaft (19) is transmitted to the thick intermediate shaft (5) through the shift frame (11), and then to the output shaft through gear S (7) and gear B (28) (26) Parallel output. At this time, the thin intermediate shaft (4) is idling without load.
将所述的齿轮R（6）与齿轮A（27）的直径比预设为1比1.4，齿轮S（7）与齿轮B（28）的直径比预设为1.4比1；则该变速器的低速挡与高速挡之比为1比1.96。该速比可以根据需要进行调整。The diameter ratio of gear R (6) and gear A (27) is preset to be 1:1.4, and the diameter ratio of gear S (7) to gear B (28) is preset to be 1.4 to 1. The ratio of low gear to high gear is 1:1.96. The speed ratio can be adjusted as needed.
从上述中可见，该变速器中的摩擦工作面不会接触到润滑油，且摩擦件可以大到接近选挡室（3）内腔的直径，摩擦工作面面积越大，能承受的压力就越大，进而使同步器摩擦件有更强摩擦力，同时该变速器也能正常工作，本发明实现了目的。It can be seen from the above that the friction working surface in the transmission will not contact the lubricating oil, and the friction part can be as large as the diameter of the inner cavity of the gear selection chamber (3). The larger the friction working surface area, the more pressure it can bear. Therefore, the friction member of the synchronizer has stronger friction force, and the transmission can also work normally. The present invention achieves the objective.
有益效果Beneficial effect
本发明的有益效果是，变速器中的摩擦工作面不与变速器的润滑油接触，且摩擦工作面面积大，进而使同步器摩擦件的摩擦力更大。The beneficial effects of the present invention are that the friction working surface in the transmission does not contact with the lubricating oil of the transmission, and the friction working surface has a large area, thereby increasing the friction force of the synchronizer friction member.
附图说明Description of the drawings
下面结合附图和实施例对本发明进一步说明。The present invention will be further described below in conjunction with the drawings and embodiments.
图1是本发明第一个实施例的外部视图。Fig. 1 is an external view of the first embodiment of the present invention.
图2是图1的俯视图。Fig. 2 is a top view of Fig. 1.
图3是本发明第一个实施例的内部视图，也就是图1的内部可视图。Fig. 3 is an internal view of the first embodiment of the present invention, that is, the internal view of Fig. 1.
图4是图2的A-A剖视图，也是图3的进一步剖视图Figure 4 is a cross-sectional view of Figure 2 A-A, which is also a further cross-sectional view of Figure 3
图5是从空挡向高速挡挂入动作过程中，换挡架（11）上的换挡架摩擦盘（31）已与摩擦片（9）接触并产生摩擦的视图。Fig. 5 is a view showing that the shift carrier friction disc (31) on the shift carrier (11) has been in contact with the friction plate (9) and friction is generated during the hooking action from neutral to high gear.
图6是从空挡向高速挡挂入动作，并且是已经完整挂入的视图；在该图中，输入轴（19）的旋转动力，可以通过换挡架（11）传递到粗中间轴（5）上，再经齿轮S（7）与齿轮B（28），递到输出轴（26）上并输出，此时细中间轴（4）为无负载的空转状态。Figure 6 is a view of the engagement action from neutral to high gear, and is a view that has been fully engaged; in this figure, the rotational power of the input shaft (19) can be transmitted to the thick intermediate shaft (5) through the shift frame (11) ), and then pass gear S (7) and gear B (28) to the output shaft (26) and output. At this time, the thin intermediate shaft (4) is in a no-load idling state.
图7是从空挡向低速挡挂入动作过程中，副摩擦片（16）已与摩擦盘（17）接触并产生摩擦的视图。Fig. 7 is a view showing that the secondary friction plate (16) has been in contact with the friction disc (17) and friction is generated during the hook-in action from the neutral gear to the low-speed gear.
图8是空挡向低速挡挂入动作，并且是已经完整挂入的视图；在该图中，输入轴（19）的旋转动力，可以通过换挡架（11）传递到细中间轴（4）上，再经齿轮R（6）与齿轮A（27），递到输出轴（26）上并输出，此时粗中间轴（5）为无负载的空转状态。Fig. 8 is a view of the engagement action of neutral gear to low-speed gear, and is a view that has been completely engaged; in this figure, the rotational power of the input shaft (19) can be transmitted to the thin intermediate shaft (4) through the shift frame (11) It is passed through gear R (6) and gear A (27) to the output shaft (26) and output. At this time, the thick intermediate shaft (5) is in a no-load idling state.
图9是图4中的换挡架（11）、细中间轴（4）和粗中间轴（5），以及所连接的一些部件的视图。Fig. 9 is a view of the shift frame (11), the thin intermediate shaft (4) and the thick intermediate shaft (5) in Fig. 4, and some connected parts.
图10是换挡架（11）的剖视图，也是换挡架（11）各部分的视图，该视图中的换挡架管状轴部分（34），与换挡架（11）其余部分为可分离设置。Figure 10 is a cross-sectional view of the shift frame (11) and a view of each part of the shift frame (11). The tubular shaft part (34) of the shift frame in this view is separable from the rest of the shift frame (11) Set up.
图11是图9部件的B-B剖视图，该图中的齿轮T（13）与粗中间轴（5）是一体的。Fig. 11 is a B-B cross-sectional view of the component of Fig. 9, in which the gear T (13) and the thick intermediate shaft (5) are integrated.
图12是图9部件的C-C剖视图，在该视图中，选挡齿轮（14）与齿轮U（15）不是啮合状态，只是视觉上看到了后面的齿轮U（15）；但是，选挡齿轮（14）与齿轮U（15）的啮合状态，可参照该视图。Figure 12 is a CC cross-sectional view of the component of Figure 9. In this view, the gear selection gear (14) and the gear U (15) are not in meshing state, but the rear gear U (15) is visually seen; however, the gear selection gear ( 14) For the meshing state with gear U (15), please refer to this view.
图13是图9部件的D-D剖视图。Fig. 13 is a D-D cross-sectional view of the part of Fig. 9.
图14是图9部件的E-E剖视图，该图中，细中间轴（4）与摩擦盘（17）为齿式啮合连接。Fig. 14 is an E-E cross-sectional view of the component of Fig. 9. In the figure, the thin intermediate shaft (4) and the friction disc (17) are in toothed meshing connection.
图15是第二个实施例的内部视图。Fig. 15 is an internal view of the second embodiment.
图16是第三个实施例的内部视图。Fig. 16 is an internal view of the third embodiment.
图17是换挡架（11）与选挡齿轮（14）、换挡架（11）与推架器（22），以及推架器（22）与外壳（1）关系的轴向视图，也是剖视部分结合未剖视部分的视图。Figure 17 is an axial view of the relationship between the shift frame (11) and the gear selection gear (14), the shift frame (11) and the push frame (22), and the push frame (22) and the housing (1). The cut-away part is combined with the view of the non-cut-away part.
图18是由外圈（44）和内齿圈（45）组成的选挡齿轮（14），在该图中，外圈（44）和内齿圈（45）之间留有1-2个齿宽的转动间隙，并以齿圈定位弹簧（39）将该间隙左右等分，该转动间隙的量，由外圈凹槽（41）与齿圈卡笋（40）结合提供以及限制；在外圈（44）与换挡架（11）固定连接后，内齿圈（45）可以在限定范围内被动的左右转动，转动方向如示意箭头（42）所示。所述内齿圈（45）可以在限定范围内被动的左右转动，可以解决该挡齿轮（14）与对应的齿轮，发生轮齿与轮齿对顶而无法相互***的问题。Figure 18 is a gear selection gear (14) composed of an outer ring (44) and an inner gear ring (45). In this figure, there are 1-2 gears between the outer ring (44) and the inner gear ring (45). Tooth width rotation gap, and the gap is equally divided left and right by the ring gear positioning spring (39). The amount of the rotation gap is provided and limited by the combination of the outer ring groove (41) and the ring gear catch (40); After the ring (44) is fixedly connected with the shift frame (11), the ring gear (45) can passively rotate left and right within a limited range, and the direction of rotation is shown by the schematic arrow (42). The inner ring gear (45) can passively rotate left and right within a limited range, which can solve the problem that the gear teeth (14) and the corresponding gears are aligned with each other and cannot be inserted into each other.
图中，1.外壳，2.速比齿轮室，3.选挡室，4.细中间轴，5.粗中间轴，6.齿轮R，7.齿轮S，8.摩擦座，9.摩擦片，10.轴承，11.换挡架，12.提前器，13.齿轮T，14.选挡齿轮，15.齿轮U，16.副摩擦片，17.摩擦盘，18.弹簧座，19.输入轴，20.锁轴器，21.输入轴座，22.推架器，23.轴状销，24.液压器，25.液压器活塞，26.输出轴，27.齿轮A，28.齿轮B，29.受推轴承，30.推力槽，31.换挡架摩擦盘，32.换挡腔，33.同步器腔，34.换挡架管状轴部分，35.压缩空气弹力器，36. 空压活塞，37.电动弹力器，38.顶杆， 39.齿圈定位弹簧，40.齿圈卡笋，41.外圈凹槽，42.示意箭头，43.推力轴承，44.外圈，45. 内齿圈。In the figure, 1. housing, 2. speed ratio gear chamber, 3. gear selection chamber, 4. thin intermediate shaft, 5. thick intermediate shaft, 6. gear R, 7. gear S, 8. friction seat, 9. friction Plate, 10. Bearing, 11. Shift frame, 12. Advance device, 13. Gear T, 14. Shift gear, 15. Gear U, 16. Pair of friction plates, 17. Friction disc, 18. Spring seat, 19 .Input shaft, 20. Shaft lock device, 21. Input shaft seat, 22. Push frame device, 23. Shaft pin, 24. Hydraulic device, 25. Hydraulic device piston, 26. Output shaft, 27. Gear A, 28 .Gear B, 29. Thrust bearing, 30. Thrust groove, 31. Shift frame friction plate, 32. Shift cavity, 33. Synchronizer cavity, 34. Shift frame tubular shaft part, 35. Compressed air elastic device , 36. Pneumatic piston, 37. Electric elastic device, 38. Mandrel, 39. Gear ring positioning spring, 40. Gear ring card bamboo shoot, 41. Outer ring groove, 42. Signal arrow, 43. Thrust bearing, 44 .Outer ring, 45. Inner gear ring.
本发明的最佳实施方式The best mode of the present invention
在图3所示的第一个实施例中，外壳（1）由速比齿轮室（2）和选挡室（3）组成，输出轴（26）经轴承（10）与外壳（1）连接并位于速比齿轮室（2）内，位于速比齿轮室（2）内的输出轴（26）上，固定连接有齿轮A（27）和齿轮B（28），在管状的粗中间轴（5）的中空内穿入细中间轴（4），细中间轴（4）的2端分别都伸出粗中间轴（5）的两端，细中间轴（4）与粗中间轴（5）经轴承接触，细中间轴（4）与粗中间轴（5）的一端经轴承连接在外壳（1）上，外壳（1）上固定连接有多个锁轴器（20），细中间轴（4）与粗中间轴（5）的环槽内都有个锁轴器（20）的部分卡入，细中间轴（4）与粗中间轴（5）的一端位于速比齿轮室（2）内，另一端位于选挡室（3）内，位于速比齿轮室（2）内的细中间轴（4）上固定连接有齿轮R（6），位于速比齿轮室（2）内的粗中间轴（5）上固定连接有齿轮S（7），齿轮R（6）与齿轮A（27）啮合连接，齿轮S（7）与齿轮B（28）啮合连接；管状的摩擦座（8）以中空，套在位于选挡室（3）内的粗中间轴（5）上，管状的摩擦座（8）的中空壁与粗中间轴（5）的外圆为齿式啮合连接，摩擦座（8）的一个轴向端面连接有推力轴承（43），另一个端面上连接有摩擦片（9），该摩擦座（8）连接有推力轴承（43）的一端朝向速比齿轮室（2），位于该选挡室（3）内的粗中间轴（5）端头，固定连接齿轮T（13）；在选挡室（3）内，伸出粗中间轴（5）的细中间轴（4）段上，从伸出处至轴头端依次连接齿轮U（15）、摩擦盘（17）和弹簧座（18），细中间轴（4）与齿轮U（15）以及弹簧座（18）为固定连接，细中间轴（4）与摩擦盘（17）为齿式啮合连接关系，弹簧座（18）上固定连接提前器（12），该提前器（12）采用的是弹簧片，该弹簧片接触摩擦盘（17），并向摩擦盘（17）提供轴向弹力；选挡室（3）内的齿轮T（13）、齿轮U（15）、摩擦盘（17）和弹簧座（18）的径向外套有换挡架（11），所述的弹簧片也被套在换挡架（11）内，该换挡架（11）有换挡架摩擦盘（31）、管状的换挡腔（32）、管状的同步器腔（33）和换挡架管状轴部分（34），换挡架摩擦盘（31）的轴向端面为摩擦工作面，换挡架摩擦盘（31）朝向摩擦座（8），并与摩擦片（9）对应且临近，换挡腔（32）内固定连接有选挡齿轮（14），选挡齿轮（14）介于齿轮T（13）与齿轮U（15）轴向的中间，选挡齿轮（14）为有内齿的齿圈，选挡齿轮（14）与外齿的齿轮T（13）以及齿轮U（15）是可啮合的对应齿轮，选挡齿轮（14）与齿轮T（13）以及齿轮U（15）的轴向间留有间隙，同步器腔（33）与换挡腔（32）交接处内，连接有副摩擦片（16），所述的摩擦盘（17）和弹簧座（18）以及弹簧片位于该同步器腔（33）内，该摩擦盘（17）与副摩擦片（16）为对应关系，换挡架管状轴部分（34）经轴承与外壳（1）连接，换挡架（11）外固定连接受推轴承（29），该受推轴承（29）最好位于换挡腔（32）处，受推轴承（29）与推架器（22）连接，推架器（22）与外壳（1）为齿式啮合连接关系，推架器（22）有操纵杆伸出外壳（1）外；换挡架管状轴部分（34）与输入轴（19）齿式啮合连接，输入轴（19）经轴承与输入轴座（21）连接，输入轴座（21）与外壳（1）固定连接，锁轴器（20）固定连接在输入轴座（21）上，并有部分锁轴器（20）体卡入输入轴（19）的环槽内；外壳（1）上固定连接有液压器（24），液压器（24）中的液压器活塞（25），通过轴状销（23）与推架器（22）伸出外壳（1）外的操纵杆连接，外壳（1）的选挡室（3）内固定连接有提前器（12），这个提前器（12）也为弹簧片，该弹簧片接触推力轴承（43），并为该推力轴承（43）以及摩擦座（8）提供轴向的弹力。所述的粗中间轴（5）与细中间轴（4）以及外壳之间，都设置有油封。所述的“齿式啮合连接”，是一种外齿式轴***在有内齿式的管轴中并啮合的连接，外齿式轴与内齿式的管轴之间，可以相互轴向移动，但不能相互转动。所述的固定连接，式两者固定在一起的连接，也可以理解为两者是一体的或是焊接在一起的状态。所述选挡齿轮（14）的轮齿，也可以位于两个端面上。所述的细中间轴（4）、粗中间轴（5）、输出轴（26）、输入轴（19）以及换挡架（11）都是同轴向的，并且为相互平行或接***行。所述的轴向，就是细中间轴（4）的轴向。所述的锁轴器（20）的作用，为阻止被锁轴的轴向移动，但不限制该轴的转动。该变速器以输入轴（19）连接外部动力，以液压器（24）连接外部挡位控制动力。所述的选挡齿轮（14）可以由外圈和内齿圈组成，外圈和内齿圈之间可以留有1-2个齿宽的转动间隙，并以弹簧将该间隙左右等分。以上所述的摩擦片（9）、换挡架摩擦盘（31）、副摩擦片（16）和摩擦盘（17）就是同步器摩擦件。In the first embodiment shown in Figure 3, the housing (1) is composed of a speed ratio gear chamber (2) and a gear selection chamber (3), and the output shaft (26) is connected to the housing (1) via a bearing (10) It is located in the speed ratio gear chamber (2), and is located on the output shaft (26) in the speed ratio gear chamber (2). It is fixedly connected with gear A (27) and gear B (28). The thick intermediate shaft ( 5) The thin intermediate shaft (4) penetrates into the hollow of the thin intermediate shaft (4), both ends of the thin intermediate shaft (4) respectively extend out of the two ends of the thick intermediate shaft (5), the thin intermediate shaft (4) and the thick intermediate shaft (5) Through bearing contact, one end of the thin intermediate shaft (4) and the thick intermediate shaft (5) is connected to the housing (1) through the bearing, and the housing (1) is fixedly connected with a plurality of shaft lockers (20), the thin intermediate shaft ( 4) There is a shaft lock (20) in the ring groove of the thick intermediate shaft (5), and one end of the thin intermediate shaft (4) and the thick intermediate shaft (5) is located in the speed ratio gear chamber (2) The other end is located in the gear selection chamber (3), and a gear R (6) is fixedly connected to the thin intermediate shaft (4) located in the speed ratio gear chamber (2), and the thick gear R (6) is located in the speed ratio gear chamber (2). Gear S (7) is fixedly connected to the intermediate shaft (5), gear R (6) is meshed and connected with gear A (27), and gear S (7) is meshed and connected with gear B (28); a tubular friction seat (8) It is hollow and sleeved on the thick intermediate shaft (5) located in the gear selection chamber (3). The hollow wall of the tubular friction seat (8) and the outer circle of the thick intermediate shaft (5) are toothed meshing connection, the friction seat (8) One axial end surface is connected with a thrust bearing (43), and the other end surface is connected with a friction plate (9). One end of the friction seat (8) connected with the thrust bearing (43) faces the speed ratio gear chamber (2). ), the end of the thick intermediate shaft (5) located in the gear selection chamber (3) is fixedly connected to the gear T (13); in the gear selection chamber (3), the thin intermediate shaft extending from the thick intermediate shaft (5) (4) In paragraph (4), connect gear U (15), friction disc (17) and spring seat (18) in order from the extension to the shaft head end, thin intermediate shaft (4) and gear U (15) and spring seat (18) ) Is a fixed connection, the thin intermediate shaft (4) and the friction disc (17) are in a toothed meshing connection, and the spring seat (18) is fixedly connected to the advancer (12), and the advancer (12) uses a spring leaf, The spring plate contacts the friction disk (17) and provides axial elasticity to the friction disk (17); the gear T (13), gear U (15), friction disk (17) and spring seat in the gear selection chamber (3) The radial casing of (18) has a shift frame (11), and the spring sheet is also sleeved in the shift frame (11). The shift frame (11) has a shift frame friction disc (31) and a tubular The shift cavity (32), the tubular synchronizer cavity (33) and the tubular shaft part (34) of the shift frame, the axial end surface of the shift frame friction disc (31) is the friction working surface, the shift frame friction disc (31) ) Facing the friction seat (8) and corresponding to and adjacent to the friction plate (9), a gear selection gear (14) is fixedly connected in the shift cavity (32), and the gear selection gear (14) is between the gear T (13) and The gear U (15) is in the middle of the axial direction. The gear selection gear (14) is a ring gear with internal teeth. The gear selection gear (14) and the external gear T (13) and gear U (15) are in meshing correspondence. There is a gap between the gear, the gear selection gear (14) and the gear T (13) and the gear U (15) in the axial direction. In the junction of the synchronizer cavity (33) and the shift cavity (32), a secondary friction plate is connected (16), the friction disc (17), the spring seat (18) and the spring plate are located in the synchronizer cavity (33), the friction disc (17) and the secondary friction plate (16) are in a corresponding relationship, and the gear shift The tubular shaft part (34) of the frame is connected to the housing (1) via a bearing, and the shift frame (11) is externally fixedly connected to a thrust bearing (29), which is preferably located at the shift cavity (32), The thrust bearing (29) is connected with the pusher (22), the pusher (22) and the housing (1) are in a toothed meshing connection relationship, and the pusher (22) has a joystick extending out of the housing (1); The tubular shaft part (34) of the shift frame is toothed and connected with the input shaft (19), the input shaft (19) is connected with the input shaft seat (21) through the bearing, and the input shaft seat (21) is fixedly connected with the housing (1), The shaft locker (20) is fixedly connected to the input shaft seat (21), and part of the shaft locker (20) is inserted into the ring groove of the input shaft (19); the housing (1) is fixedly connected with a hydraulic device ( 24), the hydraulic piston (25) in the hydraulic device (24) is connected with the joystick of the pusher (22) out of the housing (1) through the shaft pin (23), and the gear selection of the housing (1) An advancer (12) is fixedly connected to the chamber (3). This advancer (12) is also a spring leaf. The spring leaf contacts the thrust bearing (43) and provides the thrust bearing (43) and the friction seat (8) Axial elasticity. An oil seal is provided between the thick intermediate shaft (5) and the thin intermediate shaft (4) and the shell. The "toothed meshing connection" is a connection in which an externally toothed shaft is inserted into an internally toothed tube shaft and meshed. The externally toothed shaft and the internally toothed tube shaft can be axially connected to each other. Move, but cannot rotate each other. The fixed connection, the connection in which the two are fixed together, can also be understood as a state where the two are integrated or welded together. The gear teeth of the gear selection gear (14) may also be located on the two end surfaces. The thin intermediate shaft (4), the thick intermediate shaft (5), the output shaft (26), the input shaft (19) and the shift frame (11) are all coaxial, and are mutually parallel or nearly parallel. The said axial direction is the axial direction of the thin intermediate shaft (4). The function of the shaft locking device (20) is to prevent the axial movement of the shaft to be locked, but does not restrict the rotation of the shaft. The transmission uses an input shaft (19) to connect external power, and a hydraulic device (24) to connect external gear to control power. The gear selection gear (14) can be composed of an outer ring and an inner gear ring, and a rotation gap of 1-2 tooth widths can be left between the outer ring and the inner gear ring, and the gap is equally divided left and right by a spring. The friction plate (9), the shift frame friction plate (31), the secondary friction plate (16) and the friction plate (17) mentioned above are the synchronizer friction parts.
该变速器在工作时，输入轴（19）带动换挡架（11）转动，当选择为空挡时，换挡架（11）中的选挡齿轮（14）不与齿轮T（13）啮合，也不与齿轮U（15）啮合， 此时细中间轴（4）和粗中间轴（5）都不转。当外部输入低速挡的液压力控制信号，该信号通过液压器（24）使液压器活塞（25），推动推架器（22），推架器（22）通过受推轴承（29）将换挡架（11）推向输入轴（19）端，在推进的过程中，换挡架（11）上的副摩擦片（16）先与摩擦盘（17）接触，此时通过提前器（12）的弹力，使副摩擦片（16）与摩擦盘（17）之间产生强大的摩擦力，从而使细中间轴（4）与换挡架（11）同步转动，此时换挡架（11）继续被推进，使得齿轮U（15）套进选挡齿轮（14）内并与挡齿轮（14）啮合连接，齿轮U（15）与选挡齿轮（14）啮合连接后，输入轴（19）的旋转动力，通过换挡架（11）传递到细中间轴（4）上，再经齿轮R（6）与齿轮A（27），递到输出轴（26）上并输出，此时粗中间轴（5）为无负载的空转。在空挡时，当外部输入高速挡的液压力控制信号，该信号通过液压器（24）使液压器活塞（25），推动推架器（22），推架器（22）通过受推轴承（29）将换挡架（11）推向速比齿轮室（2）端，在推进的过程中，换挡架（11）上的换挡架摩擦盘（31）先与摩擦片（9）接触，此时通过提前器（12）的弹力，使换挡架摩擦盘（31）与摩擦片（9）之间产生强大的摩擦力，从而使粗中间轴（5）与换挡架（11）同步转动，此时换挡架（11）继续被推进，使得齿轮T（13）套进选挡齿轮（14）内并与挡齿轮（14）啮合连接，齿轮T（13）与选挡齿轮（14）啮合连接后，输入轴（19）的旋转动力，通过换挡架（11）传递到粗中间轴（5）上，再经齿轮S（7）与齿轮B（28），递到输出轴（26）上并输出，此时细中间轴（4）为无负载的空转。When the transmission is working, the input shaft (19) drives the shift frame (11) to rotate. When neutral is selected, the gear selection gear (14) in the shift frame (11) does not mesh with the gear T (13). Without meshing with gear U (15), neither the thin intermediate shaft (4) nor the thick intermediate shaft (5) rotate at this time. When the low-speed hydraulic pressure control signal is input from the outside, the signal will cause the hydraulic piston (25) to push the pusher (22) through the hydraulic (24), and the pusher (22) will change through the thrust bearing (29). The stopper (11) is pushed to the end of the input shaft (19). During the advancing process, the secondary friction plate (16) on the shifter (11) first comes into contact with the friction disc (17), and then passes through the advancer (12). ) The elastic force produces strong friction between the secondary friction plate (16) and the friction disc (17), so that the thin intermediate shaft (4) and the shift frame (11) rotate synchronously. At this time, the shift frame (11) ) Continues to be propelled so that the gear U (15) is inserted into the gear selection gear (14) and meshed and connected with the gear gear (14). After the gear U (15) is meshed and connected with the gear selection gear (14), the input shaft (19) ) Is transmitted to the thin intermediate shaft (4) through the shift frame (11), and then passed to the output shaft (26) and output via gear R (6) and gear A (27). The intermediate shaft (5) is idling without load. In neutral, when the external input high-speed hydraulic pressure control signal, the signal through the hydraulic (24) to make the hydraulic piston (25) push the pusher (22), the pusher (22) through the thrust bearing ( 29) Push the shift frame (11) to the end of the speed ratio gear chamber (2). During the advancing process, the shift frame friction disc (31) on the shift frame (11) first contacts the friction plate (9) At this time, through the elastic force of the advancer (12), a strong friction force is generated between the shift frame friction disc (31) and the friction plate (9), so that the thick intermediate shaft (5) and the shift frame (11) Synchronous rotation, at this time the shift frame (11) continues to be advanced, so that the gear T (13) sleeves into the gear selection gear (14) and meshes with the gear (14), and the gear T (13) and the gear selection gear ( 14) After the meshing connection, the rotational power of the input shaft (19) is transmitted to the thick intermediate shaft (5) through the shift frame (11), and then to the output shaft through gear S (7) and gear B (28) (26) Parallel output. At this time, the thin intermediate shaft (4) is idling without load.
将所述的齿轮R（6）与齿轮A（27）的直径比预设为1比1.4，齿轮S（7）与齿轮B（28）的直径比预设为1.4比1；则该变速器的低速挡与高速挡之比为1比1.96。该速比可以根据需要进行调整。The diameter ratio of gear R (6) and gear A (27) is preset to be 1:1.4, and the diameter ratio of gear S (7) to gear B (28) is preset to be 1.4 to 1. The ratio of low gear to high gear is 1:1.96. The speed ratio can be adjusted as needed.
选挡齿轮（14）与齿轮T（13）或齿轮U（15）的对插时，如遇到轮齿对轮齿对顶的情况，可以由液压器（24）的推力结合轮齿弧度的作用，迫使同步器摩擦件让步而解决；也可以使用图18中所示的选挡齿轮（14）解决。When the gear selection gear (14) is inserted into the gear T (13) or the gear U (15), if there is a gear-to-gear-to-tooth-to-tooth situation, the thrust of the hydraulic device (24) can be combined with the gear tooth radian. The effect is to force the friction of the synchronizer to make concessions; it can also be solved by using the gear selection gear (14) shown in Figure 18.
从上述中可见，该变速器中的摩擦工作面不与变速器的润滑油接触，且摩擦工作面面积大，进而使同步器摩擦件的摩擦力更大，本发明实现了目的。It can be seen from the above that the friction working surface in the transmission does not contact the lubricating oil of the transmission, and the friction working surface area is large, which in turn makes the friction of the synchronizer friction member greater, and the present invention achieves the objective.
本发明的实施方式Embodiments of the present invention
在图15所示的第二个实施例中，压缩空气弹力器（35）与外壳（1）固定连接，空压活塞（36）与摩擦座（8）上的推力轴承（43）连接；空压活塞（36）是压缩空气弹力器（35）的活塞，该压缩空气弹力器（35），是以压缩空气产生弹性的气动元件，空压活塞（36）向内压是由弹力的，该压缩空气弹力器（35）也就是所述的提前器（12）。该第二个实施例中，除了这个提前器（12）采用压缩空气弹力器（35）以外，其余的结构与部件以及工作方式都与第一个实施例的变速器相同；由于压缩空气弹力器（35）的作用，与第一个实施例中的弹簧片是一样的，且压缩空气弹力器（35）的工作方式是可以预见的，因此该第二个实施例变速器的工作方式，可以第一个实施例的变速器进行理解。In the second embodiment shown in Fig. 15, the compressed air elastic device (35) is fixedly connected with the housing (1), and the pneumatic piston (36) is connected with the thrust bearing (43) on the friction seat (8); The pressure piston (36) is the piston of the compressed air elastic device (35). The compressed air elastic device (35) is a pneumatic element that generates elasticity by compressed air. The inward pressure of the pneumatic piston (36) is caused by elastic force. The compressed air elastic device (35) is the aforementioned advancer (12). In the second embodiment, except that the advancer (12) uses a compressed air elastic device (35), the rest of the structure, components and working methods are the same as the transmission of the first embodiment; due to the compressed air elastic device ( The function of 35) is the same as that of the spring leaf in the first embodiment, and the working mode of the compressed air elastic device (35) is predictable. Therefore, the working mode of the transmission in the second embodiment can be the first The transmission of each embodiment is understood.
在图16所示的第三个实施例中，电动弹力器（37）与外壳（1）固定连接，顶杆（38）与摩擦座（8）上的推力轴承（43）连接；顶杆（38）是电动弹力器（37）的铁芯，该电动弹力器（37），是用电磁力产生弹性的电动元件，也是所述的提前器（12）。电动弹力器（37）在该第三个实施例中的工作方式是，常通电或变速前通电，通电后的电动弹力器（37）以电磁力将顶杆（38）也就是铁芯，向外顶出而产生弹力并实现工作；当换挡动作结束后，可以给电动弹力器（37）断电，以节约电能。该第三个实施例中，除了这个提前器（12）采用电动弹力器（37）以外，其余的结构与部件以及工作方式都与第一个实施例的变速器相同；由于电动弹力器（37）的作用，与第一个实施例中的弹簧片是一样的，且电动弹力器（37）的工作方式是可以预见的，因此该第三个实施例变速器的工作方式，可以第一个实施例进行对照和理解。In the third embodiment shown in Figure 16, the electric elastic device (37) is fixedly connected to the housing (1), and the ejector rod (38) is connected to the thrust bearing (43) on the friction seat (8); the ejector rod ( 38) is the iron core of the electric elastic device (37). The electric elastic device (37) is an electric component that uses electromagnetic force to generate elasticity, and is also the aforementioned advancer (12). The working mode of the electric elastic device (37) in the third embodiment is that it is always energized or energized before the speed change. After the electric elastic device (37) is energized, the ejector rod (38), which is the iron core, is driven by electromagnetic force. When the gear shifting action ends, the electric elastic device (37) can be powered off to save electric energy. In the third embodiment, except that the advancer (12) adopts an electric elastic device (37), the rest of the structure, components and working methods are the same as the transmission of the first embodiment; because the electric elastic device (37) The role of the spring is the same as that of the first embodiment, and the working mode of the electric elastic device (37) is predictable. Therefore, the working mode of the transmission in the third embodiment can be the same as that of the first embodiment. Compare and understand.
工业实用性Industrial applicability
本发明的变速器，以现有的设备和材料就可以生产。The transmission of the present invention can be produced with existing equipment and materials.

Claims (3)

  1. 一种变速器，在外壳中有输入轴、输出轴、选挡齿轮、齿轮、轴承、油封以及同步设置，输入轴通过中间轴和齿轮与输出轴相连接，以输入轴接受外部动力输入，以输出轴输出动力，以齿轮啮合连接进行传递动力，以选挡齿轮进行选挡，其特征是：在变速器中设置有细中间轴（4）、粗中间轴（5）摩擦座（8）、摩擦片（9）、换挡架（11）、提前器（12）、副摩擦片（16）、摩擦盘（17）、弹簧座（18）以及由速比齿轮室（2）和选挡室（3）组成的外壳（1）；粗中间轴（5）为中空管状，细中间轴（4）位于粗中间轴（5）中空之中，细中间轴（4）和粗中间轴（5）一端位于速比齿轮室（2）中，另一端位于选挡室（3）中；摩擦片（9）、换挡架（11）、提前器（12）、副摩擦片（16）、摩擦盘（17）、弹簧座（18）、齿轮T（13）、选挡齿轮（14）和齿轮U（ 15）位于选挡室（3）中，换挡架（11）与选挡齿轮（14）连接，输入轴（19）与换挡架（11）齿式啮合连接，推架器（22）与换挡架（11）连接，细中间轴（4）连接有摩擦座或摩擦盘，粗中间轴（5）链接有摩擦座或摩擦盘，摩擦座（8）和摩擦盘（17）都连接有提前器（12），外壳上连接有提前器（12）；细中间轴（4）与齿轮U（ 15）连接，粗中间轴（5）与齿轮T（13）连接，细中间轴（4）与提前器（12），通过弹簧座（18）连接或直接连接；摩擦座和摩擦盘之间，通过摩擦片连接并产生摩擦力；摩擦座和摩擦盘在细中间轴（4）或粗中间轴（5）上可以轴向移动；换挡架（11）在外壳（1）中可以轴向移动；选挡齿轮（14）经换挡架（11）进行与细中间轴（4）或粗中间轴（5）同步，通过移动换挡架（11）推动选挡齿轮（14）与齿轮T（13）或齿轮U（ 15）啮合连接；所述的提前器为弹性件或弹性元件，其中弹性件主要有弹簧，而弹性元件主要有以压缩空气产生弹性的气动元件，又或是用电磁力产生弹性的电动元件；以将同步器摩擦件设置在一个，无润滑油或润滑油不能接触该同步器摩擦件的空间中，实现摩擦工作面不接触润滑油；细中间轴（4）以及粗中间轴（5），通过同步器与输入轴（19）同步转速。A type of transmission. The housing has an input shaft, an output shaft, gear selection gears, gears, bearings, oil seals, and synchronization settings. The input shaft is connected to the output shaft through an intermediate shaft and gears, and the input shaft receives external power input to output The shaft outputs power, which is transmitted by gear meshing connection, and gear selection is performed by gear selection. It is characterized in that a thin intermediate shaft (4), a thick intermediate shaft (5), friction seat (8), and friction plates are provided in the transmission. (9), shift frame (11), advancer (12), auxiliary friction plate (16), friction disc (17), spring seat (18), and the speed ratio gear chamber (2) and the gear selection chamber (3) ) Shell (1); the thick intermediate shaft (5) is a hollow tube, the thin intermediate shaft (4) is located in the hollow of the thick intermediate shaft (5), and one end of the thin intermediate shaft (4) and the thick intermediate shaft (5) is located In the speed ratio gear chamber (2), the other end is located in the gear selection chamber (3); friction plate (9), shift frame (11), advancer (12), secondary friction plate (16), friction disc (17) ), spring seat (18), gear T (13), gear selection gear (14) and gear U (15) are located in the gear selection chamber (3), and the shift frame (11) is connected with the gear selection gear (14), The input shaft (19) is toothed and connected with the shift frame (11), the push frame (22) is connected with the shift frame (11), the thin intermediate shaft (4) is connected with a friction seat or friction disc, and the thick intermediate shaft ( 5) There is a friction seat or friction disc in the link, the friction seat (8) and the friction disc (17) are connected with an advancer (12), and the housing is connected with an advancer (12); the thin intermediate shaft (4) and the gear U ( 15) Connection, the thick intermediate shaft (5) is connected with the gear T (13), the thin intermediate shaft (4) and the advancer (12) are connected through the spring seat (18) or directly connected; between the friction seat and the friction plate, The friction plate is connected and generates friction; the friction seat and the friction disk can move axially on the thin intermediate shaft (4) or the thick intermediate shaft (5); the shift frame (11) can move axially in the housing (1) ; The gear selection gear (14) is synchronized with the thin intermediate shaft (4) or the thick intermediate shaft (5) via the shift frame (11), and the gear selection gear (14) and gear T ( 13) or gear U (15) meshing connection; the advancer is an elastic member or an elastic element, wherein the elastic element is mainly a spring, and the elastic element is mainly a pneumatic element that generates elasticity with compressed air, or uses electromagnetic force Generate elastic electric components; to arrange the synchronizer friction part in a space where no lubricant or lubricant cannot contact the synchronizer friction part, so that the frictional working surface does not contact the lubricant; the thin intermediate shaft (4) and the thick The intermediate shaft (5) synchronizes the speed with the input shaft (19) through a synchronizer.
  2. 根据权利要求1所述的换挡架（11），其特征是：换挡架（11）可以为筒状或框架状，还可以为网格壁的筒状；所述的框架状包括闭合式框架和非闭合式框架。The shift frame (11) according to claim 1, characterized in that: the shift frame (11) can be cylindrical or frame-shaped, and can also be cylindrical with a grid wall; the frame shape includes a closed type Frame and non-closed frame.
  3. 根据权利要求1所述的选挡齿轮（14），其特征是：选挡齿轮（14）由外圈（44）和内齿圈（45）组成，齿圈卡笋（40）处在外圈凹槽（41）中，外圈（44）和内齿圈（45）之间留有转动间隙，并以弹簧将该间隙左右等分。The gear selection gear (14) according to claim 1, characterized in that: the gear selection gear (14) is composed of an outer ring (44) and an inner gear ring (45). In the groove (41), a rotation gap is left between the outer ring (44) and the inner gear ring (45), and the gap is equally divided left and right by a spring.
PCT/CN2020/076747 2019-09-30 2020-02-26 Transmission WO2021062980A1 (en)

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Citations (6)

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Publication number Priority date Publication date Assignee Title
US4685340A (en) * 1986-01-08 1987-08-11 Versatile Corporation Two speed power take-off
US20020139215A1 (en) * 2001-03-30 2002-10-03 Smith William E. Spring-loaded fork assembly for shift system
CN201517591U (en) * 2009-07-21 2010-06-30 南京高特齿轮箱制造有限公司 Continuous change speed gear box for large-reel and high-tension reeling machine
US20140150582A1 (en) * 2012-12-03 2014-06-05 Morrison Container Handling Solutions, Inc. Multiple speed gear box
CN208457121U (en) * 2018-07-17 2019-02-01 河南省瑞歌传动机械有限公司 A kind of electric car and its double-velocity transmission
CN208870979U (en) * 2018-08-24 2019-05-17 重庆康昌机械制造有限公司 Two-way automatic clutch two-stage speed change gear

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4685340A (en) * 1986-01-08 1987-08-11 Versatile Corporation Two speed power take-off
US20020139215A1 (en) * 2001-03-30 2002-10-03 Smith William E. Spring-loaded fork assembly for shift system
CN201517591U (en) * 2009-07-21 2010-06-30 南京高特齿轮箱制造有限公司 Continuous change speed gear box for large-reel and high-tension reeling machine
US20140150582A1 (en) * 2012-12-03 2014-06-05 Morrison Container Handling Solutions, Inc. Multiple speed gear box
CN208457121U (en) * 2018-07-17 2019-02-01 河南省瑞歌传动机械有限公司 A kind of electric car and its double-velocity transmission
CN208870979U (en) * 2018-08-24 2019-05-17 重庆康昌机械制造有限公司 Two-way automatic clutch two-stage speed change gear

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