CN110014830B - Mechanical double-overrunning clutch self-adaptive automatic speed changing bridge with planetary system output - Google Patents

Abstract

The invention discloses a mechanical double-overrunning clutch self-adaptive automatic speed changing bridge with planetary system output, which comprises a drive axle shell and a planetary gear system, wherein a speed changing system is positioned in the axle shell and comprises a low-speed transmission mechanism, a reverse transmission mechanism and a self-adaptive speed changing assembly; the reverse gear transmission mechanism is provided with a transmission ratio I for transmitting reverse gear power from the auxiliary shaft to the hollow main shaft, the low-speed gear transmission mechanism is provided with a transmission ratio II for transmitting low-speed gear power from the auxiliary shaft to the hollow main shaft, and the transmission ratio I is larger than or equal to the transmission ratio II; the invention has simple and compact integral structure, the reverse gear transmission and the low-speed and high-speed gear transmission share a transmission route, the adaptability is stronger, the coordination is smooth and natural, the integral efficiency is improved, the whole speed change system is positioned in the axle housing body, the integral structure is compact, the strength and the rigidity of the integral axle are improved, the occupied volume is small, the output torque can be improved by adopting the planetary speed reduction output, and a high-speed motor can be used as a power source.

Description

Planetary system output mechanical double overrunning clutch adaptive automatic transaxle

technical field

The invention relates to a motor vehicle transmission, in particular to a mechanical double overrunning clutch self-adaptive automatic transmission axle output by a planetary system.

Background technique

The mechanical transmission system generally has complex working conditions, and needs to allocate torque to realize the transmission of different loads and speeds. Taking electric vehicles as an example, the driving environment is complex and changeable. In addition, the electric drive method commonly used in the existing electric vehicles is that the motor drives the fixed speed ratio, and the high efficiency and reasonable range are narrow and limited, resulting in a vicious circle, resulting in the following problems:

1. It can only work within the torque range of a certain working condition.

2. In order to meet the road conditions under the condition of constant speed ratio, the speed of the motor can only be increased, and the manufacturing cost of the motor can be increased.

3. The motor heats up, and the use efficiency and life are reduced;

4. To meet the torque requirements of electric vehicles in complex working conditions, we can only increase the motor current and speed by continuously increasing the motor current and speed. We can only ignore the harm of high current discharge to the battery, and we can only use the peak power, peak torque and The motor is driven by a high peak current, which does not follow the discharge characteristics of the power battery pack at all;

5. Due to the long duration of high-current discharge, the capacity of the power battery pack drops sharply, and the peak high-current discharge causes the battery to heat up rapidly, and the temperature rises causes a sharp increase in the internal resistance of the cell, and the battery is greatly impacted and irreparable. Damage, storage capacity and battery life are sharply reduced, and the number of charging cycles is rapidly reduced, which will bring about the problem of shorter and shorter cruising range;

6. Low energy recovery efficiency;

7. The use of high-speed motor acceleration and deceleration mechanism is essentially to increase power and torque, and cannot achieve high-efficiency conversion. Under low-speed and heavy-load conditions, it will bring about the problems of rapid deterioration of motor performance and low efficiency under resistance to rotation; high current power supply and frequent High current impact, the battery, controller, electrical appliances and cables caused by overload will not be damaged, especially if the battery greatly shortens the cycle mission, the economy is poor;

However, the prior art has fatal flaws that cannot be overcome due to the above driving method and technical route utilizing a constant speed ratio.

The existing automatic transmission is multi-attribute control, using solenoid valves and servo motors to achieve upshifts and downshifts through mechanical parts such as synchronizers, shift forks and gear rings. There are many parts and components in the machine, and the power must be cut off. At this time, the speed of the motor rises to the highest instantaneously, and the driving power of the car suddenly disappears, and the speed of the vehicle drops rapidly under the action of driving resistance. In a short period of time, there is a strong sense of frustration and poor reliability; there are problems such as safety, comfort, and reliability.

In order to solve the above problems, the inventors of the present application have invented a series of cam adaptive automatic transmission devices, which can detect the driving torque-rotation speed and the driving resistance-vehicle speed signal according to the driving resistance, so that the output power of the motor or engine and the driving conditions of the vehicle are always in the best position. In the best matching state, the balance control of the vehicle driving torque and the comprehensive driving resistance is realized. The load of the cam adaptive automatic transmission changes the transmission ratio with the change of the driving force, and the gear shift is automatically adjusted according to the change of the driving resistance without cutting off the driving force. , so that the motor or engine can always output torque at high speed in the high-efficiency area; it can meet the requirements of stable operation of motor vehicles in mountainous areas, hills and heavy loads, and improve safety; the friction disc is used to form a separate and combined structure, which has the advantages of sensitive response, and the shaft The size is small, which solves the above-mentioned problems of electric vehicles very well. Although it has the above advantages, the cam adaptive automatic transmission device is suitable for the one-way power transmission of electric motorcycles and electric bicycles due to the mechanical automatic transmission structure, and is not suitable for the transmission of motor vehicles and mechanical devices that require two-way drive. The reverse gear mechanism will not only increase the overall volume of the transmission and the complexity of the structure, but also cannot be well integrated with the cam adaptive automatic transmission.

Therefore, it is necessary to improve the above-mentioned cam adaptive automatic transmission device, and add a reverse gear mechanism with strong adaptability. It can solve the problem of forward and reverse driving on high-efficiency roads under complex conditions under two-way driving conditions, and the setting is simple and compact, and the cam adaptive automatic transmission mechanism cooperates smoothly and naturally, reducing manufacturing costs and ensuring transmission stability. .

SUMMARY OF THE INVENTION

In view of this, the purpose of the present invention is to provide a mechanical double overrunning clutch self-adaptive automatic transmission axle with planetary system output, adding a reverse gear mechanism with strong adaptability, and the device can not only adapt itself to the change of driving resistance without cutting off the driving force. It can automatically shift gears under the circumstance of driving, and can solve the problem of forward and reverse driving on high-efficiency roads under complex conditions under two-way driving conditions, and the setting is simple and compact, and the cam adaptive automatic transmission mechanism cooperates smoothly. Naturally, reduce the manufacturing cost and ensure the stability of the transmission.

The mechanical double overrunning clutch adaptive automatic transmission axle output by the planetary system of the present invention includes an axle housing, a transmission located in the axle housing, a planetary gear train and a differential, and the transmission includes a hollow main shaft and a speed change on the hollow main shaft. a system, the transmission system includes a planetary gear train, a low-speed gear transmission mechanism, a reverse gear transmission mechanism and an adaptive transmission assembly;

The adaptive shifting assembly includes a driven friction piece, an active friction piece and a shift elastic element;

The active friction piece and the driven friction piece form a friction transmission pair in a way that the friction surfaces cooperate with each other, and the variable-speed elastic element applies a pre-tightening force to make the driven friction piece fit with the active friction piece for transmission, and the driven friction piece passes through the first axial cam. The pair is matched with the hollow main shaft for transmission, and when the first axial cam pair outputs power through the hollow main shaft, it exerts an axial component force opposite to the pre-tightening force of the shifting elastic element on the driven friction piece; the driving power is input to a first overrunning clutch Thereby, the power is input to the active friction member; the hollow main shaft outputs the power to the differential through the planetary gear train, and the two half shafts of the differential are respectively connected with respective transmission shafts, and one of the transmission shafts The shaft rotates and fits through the hollow main shaft and is supported on the axle housing by rotation and fit;

It also includes a secondary shaft, and the driving power is also input to the secondary shaft;

The low-speed gear transmission mechanism includes a second overrunning clutch, and the secondary shaft transmits the low-speed gear power to the driven friction member through the second overrunning clutch;

The reverse gear transmission mechanism is arranged in a manner that can transmit the reverse gear power to the driven friction member or disconnect the reverse gear power;

The reverse gear transmission mechanism has a transmission ratio I for transmitting the reverse gear power from the countershaft to the driven friction member, and the low-speed gear transmission mechanism has a transmission ratio II for transmitting the low-speed gear power from the countershaft to the driven friction member, and the transmission ratio is I is greater than or equal to the transmission ratio II;

The planetary gear train includes an outer ring gear, planetary gears, a planet carrier and a sun gear, and the outer ring gear is fixed to the axle housing.

Further, both the second overrunning clutch and the reverse gear transmission mechanism transmit power to the driven friction member through the second axial cam pair.

Further, the differential case extends left and right to form a left extension shaft segment and a right extension shaft segment that are rotatably supported on the axle housing, and the hollow main shaft inputs power to the sun gear and outputs the power to the The right extension shaft section, the right half shaft of the differential is connected with a right transmission shaft, and the right transmission shaft passes through the hollow main shaft in rotation and is supported on the axle housing in rotation; the second axial cam The pair is formed by a cam shaft sleeve with an end face cam and an end face cam carried by the driven friction piece. on the hollow spindle.

The inner ring of the first overrunning clutch is rotatably fitted over the camshaft sleeve and is driven and matched with the active friction member; the driving power is input to the outer ring of the first overrunning clutch and simultaneously input the power to the countershaft through the outer ring of the first overrunning clutch;

The sun gear is coaxially matched with the hollow main shaft, the differential is in driving cooperation with the planet carrier, and the differential case is coaxial with the hollow main shaft.

Further, the low-speed gear transmission mechanism further includes a low-speed gear driven gear and a low-speed gear driving gear meshing with the low-speed gear driven gear, and the outer ring of the second overrunning clutch is configured to cooperate with or directly form a low-speed gear driven gear, The low-speed driving gear is arranged in cooperation with the countershaft; the reverse gear transmission mechanism includes a reverse gear driving gear and a reverse gear driven gear meshing with the reverse gear driving gear, and the reverse gear driving gear can be engaged or disengaged. It is arranged on the secondary shaft, the reverse gear driven gear and the inner ring of the second overrunning clutch are in driving cooperation with the camshaft sleeve and are arranged in the hollow main shaft in rotation coordination; the transmission ratio I is greater than the transmission ratio II.

Further, the reverse gear driving gear is provided on the countershaft in a manner that can be engaged or disengaged by an electromagnetic shifting mechanism, and the electromagnetic shifting mechanism is simultaneously used for switching the forward and reverse power input.

Further, the electromagnetic shift mechanism includes an active swing arm, a shift shaft, a shift fork and two electromagnetic shifters, the two electromagnetic shifters are used to drive the active swing arm to swing around the axis of the shift shaft and The shifting shaft is driven to rotate around the shifting axis, and the shifting rotating shaft drives the shifting fork to swing around the axis to complete the shifting.

Further, the electromagnetic shifting mechanism is also provided with a positioning mechanism, and the positioning mechanism includes a positioning pin with a pre-tightening force that is arranged on the active swing arm or is arranged on the positioning component that is connected with the active swing arm in a follow-up manner, and a positioning pin arranged on the axle housing. The positioning base of the body, the positioning base is provided with a positioning recess that can be matched with the positioning pin and the position is corresponding to the engagement or separation of the reverse gear transmission mechanism; the electromagnetic shifting mechanism is also provided with a detection gear shift Is the position sensing assembly in place.

Further, the speed change elastic element is a speed change disc spring, the speed change disc spring is sleeved on the hollow main shaft, and one end of the speed change disc spring is pressed against the driven friction member through a plane bearing, and the plane bearing is a plane rolling bearing with double rows of small balls along the radial direction;

A transmission sleeve is provided in cooperation with the outer ring of the first overrunning clutch, and the transmission sleeve is used for inputting power in cooperation with the motor rotor, and is axially extended to form a journal that is rotatably supported on the axle housing, and the active friction member, Both the driven friction part and the speed change disc spring are located in the cavity between the transmission sleeve and the hollow main shaft.

Further, both the second overrunning clutch and the reverse gear transmission mechanism transmit power to the second axial cam pair through the third axial cam pair to transmit the power to the driven friction member, and the third axial cam pair is sleeved by a rotating fit. The end surface cam of the second camshaft sleeve of the hollow main shaft is formed in cooperation with the end surface cam at the end of the camshaft sleeve facing away from the driven friction member;

An intermediate driving gear is provided on the camshaft sleeve or the second camshaft sleeve in cooperation with the outer ring of the first overrunning clutch and is rotated and matched with the outer ring of the first overrunning clutch. ;

The inner ring of the second overrunning clutch extends to the axial outer end to form a shaft sleeve that is driven and fitted over the hollow main shaft, the shaft sleeve is rotatably supported on the axle housing, and the other end is matched with the second cam shaft sleeve for transmission;

One axial end of the outer ring of the first overrunning clutch is driven and matched with the intermediate driving gear, and the other end is fixedly connected to the transmission sleeve. The power output end of the hollow main shaft passes through and is rotatably supported on the axle housing.

Further, the outer circle of the shaft sleeve of the first overrunning clutch is rotatably supported on the axle housing through the first rolling bearing; the second camshaft sleeve is rotatably supported on the axle housing through the second rolling bearing, and the second rolling bearing is located in the reverse gear. Between the driven gear and the intermediate driving gear, the intermediate driving gear axially extends to form a journal, and the journal is also supported on the axle housing through a fifth rolling bearing in a rotatable fit. The first plane bearing is rotatably matched; the inner circle of the transmission sleeve is rotatably supported on the hollow main shaft through the fourth rolling bearing;

A transmission wheel disc is provided in driving connection with the planet carrier, and the transmission wheel disc is axially formed with a transmission shaft sleeve, and the transmission shaft sleeve drives the outer sleeve on the rightward extending shaft end of the differential housing.

The beneficial effects of the invention are: the mechanical double overrunning clutch adaptive automatic transmission axle output by the planetary system of the invention has all the advantages of the existing cam adaptive automatic transmission device, such as the ability to detect the driving torque-rotation speed and the driving force according to the driving resistance. Resistance-vehicle speed signal, so that the output power of the motor and the driving condition of the vehicle are always in the best matching state, realize the balanced control of the driving torque of the vehicle and the comprehensive driving resistance, and automatically shift gears automatically with the change of driving resistance without cutting off the driving force Variable speed; it can be used in mountainous areas, hills and heavy loads, so that the motor load changes smoothly, the motor vehicle runs smoothly, and the safety is improved;

Using the reasonable cooperation of the two overrunning clutches, the reverse gear structure and the low-speed gear mechanism are reasonably set to the transmission ratio, so that the overall structure is simple and compact. The overall performance of the invented mechanical self-adaptive automatic transmission has strong adaptability, smooth and natural cooperation with the self-adaptive automatic transmission mechanism, reduces manufacturing costs, and ensures the stability of transmission. It is not only suitable for the field of electric vehicles, but also suitable for other variable torque. In the field of mechanical transmission; the use of planetary deceleration output can improve the output torque, and high-speed motor can be used as the power source to improve the overall efficiency. It is suitable for the field of electric vehicles and other fields of variable torque mechanical transmission.

Description of drawings

The present invention will be further described below with reference to the accompanying drawings and embodiments.

Fig. 1 is the axial sectional structure schematic diagram of the present invention;

Figure 2 is a schematic diagram of an electromagnetic shifting structure;

Fig. 3 sectional view of electromagnetic shift structure;

Fig. 4 is the structure schematic diagram of the present invention adopting the friction plate structure;

Figure 5 is an enlarged view of the friction plate structure.

Detailed ways

1 is a schematic diagram of an axial cross-sectional structure of the present invention, FIG. 2 is a schematic diagram of an electromagnetic shift structure, and FIG. 3 is a cross-sectional view of an electromagnetic shift structure, as shown in the figure: the mechanical double overrunning clutch self-adaptive automatic output of the planetary system of the present invention A transmission axle, including an axle housing 20 and a transmission, a planetary gear train and a differential located in the axle housing, the transmission comprising a hollow main shaft 1 and a speed change system on the hollow main shaft 1, the speed change system comprising a planetary gear train, a low speed Gear transmission mechanism, reverse gear transmission mechanism and adaptive transmission assembly;

The adaptive shifting assembly includes a driven friction piece, an active friction piece and a shift elastic element;

The active friction member and the driven friction member form a friction transmission pair in the way that the friction surfaces cooperate with each other. As shown in Figure 1, the active friction member 18 and the driven friction member 2 are respectively the inner cone sleeve of the toroid body and the axial direction of the toroid body. The outer cone sleeve, the axial inner cone sleeve of the annular body is provided with an axial inner cone surface and is sleeved on the axial outer cone sleeve of the annular body, and the axial outer cone sleeve of the annular body is provided with the axial inner cone sleeve of the annular body. The axially outer conical surface that matches with the axially inner conical surface of each other forms frictional engagement, transmission or separation through the cooperating conical surfaces, which will not be repeated here;

Of course, the friction transmission pair can also adopt the friction plate structure as shown in Figure 4 and Figure 5, the active friction member 18' and the inner ring of the first overrunning clutch are integrally formed or cooperated in transmission, and the active friction member 18' is provided with active friction The plate group 18a', the driven friction piece is provided with a driven friction plate group that cooperates with the active friction plate 18a', and the matching structure is similar to the existing friction plate clutch, but the friction plate of this structure is detachable. The overall structure needs to be disassembled to ensure the axial dimension;

The variable speed elastic element 19 exerts a pre-tightening force to make the driven friction piece and the active friction piece fit and drive, and the driven friction piece is driven and matched with the hollow main shaft 1 through a first axial cam pair, and the first axial cam pair transmits the power through When the hollow main shaft is output, an axial component force opposite to the pre-tightening force of the shifting elastic element is applied to the driven friction piece; the first axial cam pair 27 is the cooperating axial cam (including the end face cam or the helical cam), and the driven friction When the component rotates, the first axial cam pair 27 generates two component forces in the axial direction and the circumferential direction, wherein the circumferential component force outputs power, and the axial component force acts on the driven friction member and is applied to the variable speed elastic element, that is to say, The rotation direction of the first axial cam pair is related to the rotation direction of the power output. According to the above description, those skilled in the art can know which rotation direction of the first axial cam pair 27 can be applied on the premise of knowing the power output direction. Which direction of the axial component force will not be repeated here; as shown in the figure, since the driven friction member 2 is driven and fitted on the hollow main shaft 1 through the first axial cam pair 27, the first axial cam The pair 27 is a helical cam, which will not be repeated here; the driving power is input to a first overrunning clutch to input the power to the active friction member; the hollow main shaft outputs the power to the differential through the planetary gear train, and the The planet carrier outputs the power to the differential 35, and the two half shafts of the differential 35 are respectively connected with their respective transmission shafts. As shown in the figure, the right half shaft of the differential 35 is connected with a right transmission shaft 34. The right transmission shaft 34 rotates and fits through the hollow main shaft 1 and is rotatably supported on the axle housing 20. As shown in the figure, the right drive shaft is rotatably supported on the axle housing 20 through the seventh radial bearing 38 ; and the left axle shaft drive connection of the differential 35 is provided with a left drive shaft 33 , and the left drive shaft 33 rotates It is supported by the axle housing 20. As shown in the figure, the left transmission shaft is rotatably supported by the axle housing 20 through the eighth radial bearing 37; the differential housing of the differential 35 extends to the left and right to form a left extension shaft. and the right extension shaft section, the left extension shaft section and the right extension shaft section are respectively supported on the axle housing 20 through their respective journal bearings for rotation fit;

It also includes a secondary shaft 12, and the driving power is also input to the secondary shaft 12;

The low-speed gear transmission mechanism includes a second overrunning clutch, and the secondary shaft transmits the low-speed gear power to the driven friction member through the second overrunning clutch;

The reverse gear transmission mechanism is set in such a way that it can transmit the reverse gear power to the driven friction member 2 or disconnect the reverse gear power; generally, it is set with a gear shifting structure, and the transmission between the reverse gear transmission mechanism and the driven friction member can also be disconnected. The transmission with the secondary shaft 12 can be disconnected, and the purpose of the invention can be achieved;

The reverse gear transmission mechanism has a transmission ratio I for transmitting the reverse gear power from the countershaft 12 to the hollow main shaft 1, and the low-speed gear transmission mechanism has a transmission ratio II for transmitting the low-speed gear power from the countershaft 12 to the hollow main shaft 1, The transmission ratio I is greater than or equal to the transmission ratio II; then in the reverse gear transmission, the second overrunning clutch, 6 overruns, the inner ring 6a (the rotation direction is the same as the reverse gear) rotates slower than the outer ring 6b (the low gear and the reverse gear are both driven by the auxiliary gear). shaft input power) to form overrun, and the reverse gear transmission mechanism will transmit smoothly, otherwise it will be locked.

The planetary gear train includes an outer ring gear 31 , planetary gears 30 , a planet carrier 32 and a sun gear 29 , and the outer ring gear is fixed to the axle housing 20 .

Since the transmission directions of the low-speed gear transmission mechanism and the reverse gear transmission mechanism are different, the axial cam pair is preferably a bidirectional output cam structure.

In this embodiment, the second overrunning clutch 6 and the reverse gear transmission mechanism both transmit power to the driven friction member 2 through the second axial cam pair 26, as shown in the figure; because the low-speed gear transmission mechanism and the reverse gear transmission mechanism The transmission directions of the mechanisms are different, therefore, the second axial cam pair is preferably a bidirectional output cam structure.

In this embodiment, the hollow main shaft 1 inputs power to the sun gear 30 and outputs the power to the differential from the planet carrier; the second axial cam pair 26 is composed of a cam sleeve 16 with an end cam and a driven friction member 2. The end face cams with 2 are formed by matching, the cam shaft sleeve 16 is rotatably fitted on the hollow main shaft 1, and the driven friction member 2 is driven and fitted on the hollow main shaft 1 through the first axial cam pair 27; An inner ring 4a of an overrunning clutch 4 is rotatably fitted over the camshaft sleeve 22, and the end extends to form an extension section to drive and cooperate with the active friction member 18. The transmission sleeve 3 is driven to cooperate with the outer ring 4b of the first overrunning clutch 4 and simultaneously input power to the The secondary shaft 12, the structural arrangement makes the structure of the present invention compact.

The driving power is input to the outer ring 4b of the first overrunning clutch 4. As shown in the figure, the transmission sleeve 3 is used to cooperate with the rotor of the motor through transmission and to cooperate with the outer ring 4b of the first overrunning clutch 4, as shown in the figure. It is shown that the transmission sleeve 3 forms a power input transmission through a transmission-matched transition transmission sleeve, and improves the connection rigidity; the inner ring 4a of the first overrunning clutch 4 is connected with the active friction member 18 in a transmission; the driving power is transmitted through the first overrunning The outer ring of the clutch is also input to the secondary shaft 12, that is, the driving power is input in two ways. The way of inputting the secondary shaft 12 can use any existing mechanical transmission structure, such as gears, chains, or even direct transmission, etc., which will not be repeated here. .

The inner ring 4a of the first overrunning clutch 4 is rotatably fitted over the camshaft sleeve, and the end extends to form an extension section for transmission and cooperation with the active friction member 18. As shown in the figure, the inner ring 4a of the first overrunning clutch 4 is provided with a middle The transition sleeve, the middle transition sleeve is sleeved on the extension section through splines (with interference) to form a rigid transmission; the driving power is input to the outer ring 4b of the first overrunning clutch 4, and the power is simultaneously input to the auxiliary through the outer ring of the first overrunning clutch axis 12;

A transmission wheel 36 is provided in driving connection with the planet carrier 32. The sun gear 29 is coaxially driven and matched with the hollow main shaft 1 (the sun gear is sleeved on the hollow main shaft 1), and the differential housing of the differential is connected to the The planet carrier 32 is matched for transmission, and the differential housing is coaxial with the hollow main shaft 1; as shown in the figure, the planet carrier 32 is fixedly connected with the transmission wheel 36 in the circumferential direction, and the transmission wheel forms a transmission in the axial direction. A shaft sleeve, the transmission sleeve is a drive sleeve on the rightward extending shaft end of the differential housing; the hollow main shaft is supported on the axle housing 20 through a third bearing in a rotating fit.

In this embodiment, the low-speed transmission mechanism further includes a low-speed driven gear and a low-speed driving gear 7 meshing with the low-speed driven gear, and the outer ring 6b of the second overrunning clutch 6 is provided in a driving manner or directly formed The low-speed driven gear, the low-speed driving gear 7 is arranged on the countershaft 12 in cooperation with the transmission; the reverse gear transmission mechanism includes a reverse gear driving gear 9 and a reverse gear driven gear 8 meshing with the reverse gear driving gear 9, so The reverse gear driving gear 9 can be engaged (transmission) or disengaged (rotation) and is arranged on the countershaft, the reverse gear driven gear 8 and the inner ring 6a of the second overrunning clutch 6 are drivingly matched with the camshaft sleeve 16 and rotate. The inner ring 6a of the second overrunning clutch 6 is integrally formed with the camshaft sleeve 16 in this embodiment; as shown in the figure, the reverse gear driving gear 9 is rotatably matched (needle roller bearing) to the secondary shaft 12 , the engagement or disengagement of the auxiliary shaft is formed by the slidable and driveable coupling member disposed on the auxiliary shaft, which belongs to the conventional joint structure and will not be repeated here; the transmission ratio I is greater than the transmission ratio II, so as to Ensure the smoothness of the transmission and avoid locking.

In this embodiment, the reverse gear driving gear 9 is disposed on the countershaft 12 in a way that can be engaged or disengaged by the electromagnetic shifting mechanism 10 . When the mechanism is switched to reverse gear, the signal is directly sent to the motor control system to control the reverse rotation of the motor to achieve reverse gear; it can be achieved by using a general signal acquisition mechanism or switch.

In this embodiment, the electromagnetic shift mechanism includes an active swing arm 104, a shift shaft 105, a shift fork 106 and two electromagnetic shifters (electromagnetic shifter 101 and electromagnetic shifter 102). The two electromagnetic shifters are used to drive the active swing arm to swing around the axis of the shift shaft and drive the shift shaft to rotate around the shift axis, and the shift shaft drives the shift fork to swing around the axis to complete the shift As shown in the figure, in this embodiment, the electromagnetic shifters 101 and 102 are arranged in parallel, and are respectively used to drive (or release) both ends of the active swing arm, so that the active swing arm 104 can swing around a center line, so The shift shaft is connected to the active swing arm 104 with its axis coincident with the center line, which drives the active swing arm to swing around the axis of the shift shaft and drives the shift shaft to rotate around the axis, and the shift shaft 105 drives the shift shaft. The shift fork 106 swings around the axis and drives the clutch (synchronizer) 17 to complete gear shifting. The clutch (synchronizer) gear shift belongs to the prior art and will not be repeated here; of course, the two electromagnetic shifters (electromagnetic The shifter 101 and the electromagnetic shifter 102) can be opposite structures, and the active swing arm is driven to and fro swinging from both sides, which can also achieve the purpose of the invention, which will not be repeated here; the electromagnetic shifter has a reciprocating push rod. When the power is turned on, the reciprocating push rod pushes out and pushes the active swing arm to swing and then returns immediately. The return generally adopts a return spring structure, which will not be repeated here.

In this embodiment, the electromagnetic shifting mechanism is further provided with a positioning mechanism 103, and the positioning mechanism 103 includes a positioning mechanism with a pre-tightening force, which is disposed on the active swing arm or on the positioning member 107 that is connected to the active swing arm in a follow-up manner. The pin 103b and the positioning base 103c arranged on the axle housing, the positioning base 103c is provided with a positioning recess that can cooperate with the positioning pin 103b and the position is engaged with or disengaged from the reverse gear transmission mechanism; as shown in the figure, In this embodiment, the positioning pins are arranged on the positioning member 107, the positioning member 107 is provided with positioning holes 103a for setting the positioning pins 103b, and the positioning holes are provided with a pre-determination for the positioning pins 103b to be positioned and matched outwardly with the positioning pits. Tight positioning spring 103d; during the swinging process, the positioning pin slides on the surface of the positioning base, and when sliding to the positioning pit, the positioning pin enters the pit to form a positioning under the action of the pre-tightening force. Of course, the pit is a smooth structure, Positioning the bullet under a certain thrust will remove the pit and complete the subsequent shifting procedure; the electromagnetic shifting mechanism is also provided with a position sensing component for detecting whether the gear shift is in place, and the sensing component generally adopts a Hall element And the magnetic steel corresponding to the Hall element.

In this embodiment, the speed change elastic element is a speed change disc spring 19, the speed change disc spring 19 is sleeved on the hollow main shaft 1 and one end is pressed against the driven friction member 2 through a plane bearing 28, and the plane bearing 28 is radially doubled. The plane rolling bearing with small balls, the use of small balls is smaller than the balls with the same bearing capacity in the prior art; the use of double-row balls can reduce the parameters of the balls under the condition that the plane bearing bears the same load, and has the advantages of stable rotation, The same load has the characteristics of high speed, strong bearing capacity, and can reduce the axial installation size.

A transmission sleeve 3 is provided in cooperation with the outer ring of the first overrunning clutch. When in use, the transmission sleeve 3 is used to input power in cooperation with the motor rotor, and axially extends to form the journal to rotate through the sixth rolling bearing 24. Supported on the axle housing, the active friction member 18, the driven friction member 2 and the speed change disc spring 19 are all located in the cavity between the transmission sleeve and the hollow main shaft; the structure is compact and the integration is strong, which is convenient for the arrangement of electric vehicles; And through the support and cooperation of the transmission sleeve 3, the overall structure of the transmission is made more rigid.

In this embodiment, an intermediate driving gear 15 is provided in cooperation with the outer ring 4b of the first overrunning clutch 4. As shown in the figure, the intermediate driving gear 15 forms a stepped shaft with a necked down, and the outer ring of the first overrunning clutch 4 4b is fixedly connected with a necked stepped shaft sleeve, the stepped shaft sleeve is sleeved on the stepped shaft to form a transmission fit, and has a radial restraint ability to ensure the formation of transmission and has a certain supporting effect; the auxiliary shaft 12 is set in a transmission fit There is an intermediate driven gear 14 matched with the intermediate driving gear 15;

In this embodiment, the second overrunning clutch 6 and the reverse gear transmission mechanism both transmit power to the second axial cam pair 26 through the third axial cam pair 26 ′ to transmit the power to the driven friction member 2 , the third axial cam pair 26 ′. The axial cam pair 26' is formed by the end face cam of the second cam shaft sleeve 25 which is rotatably fitted on the hollow main shaft and the end face cam of the end face of the cam shaft sleeve 16 facing away from the driven friction piece 2; the end face away from the driven friction piece 2 Refers to the distal end compared with the driven friction piece 2, as shown in the left end;

An intermediate driving gear 15 is provided with the outer ring 4b of the first overrunning clutch 4 in driving cooperation and is rotatably fitted on the camshaft sleeve or the second camshaft sleeve. As shown in the figure, the intermediate driving gear 15 passes through the needle roller bearing 5 The second camshaft sleeve 25 is provided in a rotational fit; the secondary shaft 12 is provided with an intermediate driven gear 14 in a transmission fit with the intermediate driving gear 5;

The inner ring 6b of the second overrunning clutch 6 extends to the outer end of the axial direction to form a shaft sleeve that is driven and fitted over the hollow main shaft 1. The outward refers to the outside of the transmission (the left end in the figure), and the shaft sleeve is rotatably supported on the bridge. The casing, the other end (right end) is in driving fit with the second camshaft sleeve 25;

One end of the outer ring 4b of the first overrunning clutch 4 is in driving fit with the intermediate driving gear 5, and the other end is fixedly connected to the transmission sleeve (transmission). body 20.

In this embodiment, the outer circle of the shaft sleeve of the inner ring 6b of the second overrunning clutch 6 is supported by the first rolling bearing 22 in a rotatable fit on the axle housing 20 ; Axle housing 20, the second rolling bearing 21 is located between the reverse driven gear 8 and the intermediate driving gear 5, the intermediate driving gear 5 axially extends to form a journal, and the journal is also rotated through the fifth rolling bearing 11 It is supported by the axle housing 20, and the intermediate driving gear 5 and the second rolling bearing 21 are rotatably matched by the first plane bearing 13 (plane rolling bearing); the inner circle of the transmission sleeve 3 is supported by the fourth rolling bearing 23. Hollow Spindle 1.

The power output end of the hollow main shaft 1 passes through and is rotatably supported on the axle housing 20 through the third rolling bearing 22. The differential and the hollow main shaft are arranged on both sides of the planetary gear train and are coaxially arranged. The transmission sleeve passes through the axle housing 20. The fourth rolling bearing 23 is rotatably supported on the hollow main shaft 1; as shown in the figure, each rolling bearing is supported on the supporting rib or end cover formed on the axle housing, which will not be repeated here; the formed supporting rib is opposite to the axle housing itself Also has a strengthening effect.

In the above structure of this embodiment, the power output and input segments located on the hollow main shaft or/and the camshaft sleeve are correspondingly rotatably supported on the axle housing. In this structure, the camshaft sleeve is sleeved on the hollow main shaft to form a transmission and mutual support structure , can transmit large torque without bending deformation, which can greatly reduce the size of components under the same bearing capacity; The hollow main shaft and the shaft sleeve of the transmission can be set longer, and due to the support, the additional bending moment generated by the torque is transmitted to the axle housing, so that it can transmit a large torque and greatly improve the speed under high torque ( The same component size), to achieve high torque, high speed and lightweight indicators, radial bearings and the mutual support of the bushing and the hollow main shaft, but also make the transmission have better stability and low noise at high speeds, compared to the current state. With technology, the maximum speed used to drive the motor and high-speed reducer is ≥15000 rpm, and it is used for high-efficiency and lightweight transmission mechanisms, which have great advantages in energy conservation and environmental protection, and are more suitable for pure electric energy conservation and environmental protection as the main goal. Vehicle use, of course, the present invention is not only applicable to the field of electric vehicles, but also applicable to other fields of variable torque mechanical transmission.

In the present invention, the recorded left and right are subject to the left and right of the attached drawings. The recorded transmission connection includes all transmission connection structures in the prior art, including splines, flat keys, bolt-fixed connections, etc., which will not be repeated here. Repeat.

The above embodiment is only the best structure of the present invention, and does not limit the protection scope of the present invention; the scheme of adjusting the connection mode does not affect the realization of the purpose of the present invention.

The fast gear power transmission route of this embodiment:

Power → active friction piece 18 → driven friction piece 2 → first axial cam pair → hollow main shaft 1 → planetary gear train → differential → output power;

At this time, the second overrunning clutch is overrun, and the resistance transmission route: differential → planetary gear train → hollow main shaft 1 → first axial cam pair → driven friction member 2 → speed change disc spring; The dynamic friction member 2 exerts an axial force and compresses the speed change disc spring. When the driving resistance increases to a certain level, the axial force overcomes the speed change disc spring, so that the active friction member 18 and the driven friction member 2 are separated, and the power is transmitted through the following route: That is, the low-speed power transmission route:

Power→outer ring 4b of first overrunning clutch 4→counter shaft 12→low gear driving gear→outer ring 6b of second overrunning clutch 6→inner ring 6a of second overrunning clutch→second axial cam pair 26'→from Dynamic friction piece 2→first axial cam pair 26→driven friction piece 2→axial cam pair 27→hollow main shaft→planetary gear train→differential→output power.

The low-speed power transmission route also goes through the following routes: the first axial cam pair 26 → the driven friction piece 2 → the compression speed change disc spring, to prevent the reciprocating compression of the compression speed change disc spring during the low speed transmission process, thereby preventing the low speed transmission. The friction member 18 is in contact with the driven friction member 2 .

It can be seen from the above transmission route that during the operation of the present invention, the active friction member 18 and the driven friction member 8 closely fit under the action of the speed change disc spring, forming an automatic speed change mechanism that maintains a certain pressure. At this time, the power drives the active friction member 18, the driven friction member 2, and the hollow main shaft 1, so that the hollow main shaft 1 outputs power through the planetary gear train and the differential; At this time, the second overrunning clutch is in an overrunning state.

When the motor vehicle starts, the resistance is greater than the driving force, and the resistance forces the camshaft sleeve to rotate a certain angle in the opposite direction. Under the action of the first axial cam pair, the driven friction piece 2 compresses the speed change disc spring; the driven friction piece 2 and the active friction piece 18 Separation, synchronization, engagement of the second overrunning clutch, the output power rotates at the low-speed gear speed; therefore, the low-speed gear start is automatically realized, which shortens the starting time and reduces the starting force. At the same time, the variable-speed disc spring absorbs the kinetic resistance torque energy, and accumulates potential energy to transmit power for restoring the fast gear.

After the startup is successful, the driving resistance is reduced. When the component force is reduced to less than the pressure generated by the speed change disc spring, the pressure of the speed change disc spring is quickly released due to the compression of the movement resistance. Under the push, the driven friction piece 2 and the active friction piece 18 are restored to tightness. Fitting state, the low-speed overrunning clutch is in the overrunning state.

During the driving process, the principle of automatic gear shifting is the same as the above, and the shifting is realized without cutting the driving force, so that the entire locomotive runs smoothly, is safe and low in consumption, and the transmission route is simplified to improve the transmission efficiency.

Reverse transmission line:

Power→outer ring 4b of first overrunning clutch 4→counter shaft 12→reverse drive gear→reverse driven gear→second axial cam pair 26'→first axial cam pair 26→driven friction member 2→shaft To cam pair 27 → hollow main shaft 1 → planetary gear train → differential → output reverse gear power.

At this time, since the transmission ratio of the reverse gear is greater than the transmission ratio of the low-speed gear and is reversed, the second overrunning clutch overruns. Since the rotation is reversed and the outer ring rotates faster than the inner circle, the first overrunning clutch overruns to realize reverse gear transmission; Of course, the low-speed gear transmission and the reverse gear transmission are both down-speed transmissions, which will not be repeated here.

Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit them. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solutions of the present invention can be Modifications or equivalent substitutions without departing from the spirit and scope of the technical solutions of the present invention should be included in the scope of the claims of the present invention.

Claims (10)

1. A mechanical double overrunning clutch adaptive automatic transmission axle output by a planetary system is characterized in that: comprising an axle housing and a transmission, a planetary gear train and a differential located in the axle housing, and the transmission comprises a hollow main shaft and a differential. A speed change system on the hollow main shaft, the speed change system includes a low-speed gear transmission mechanism, a reverse gear transmission mechanism and an adaptive transmission assembly; The adaptive shifting assembly includes a driven friction piece, an active friction piece and a shift elastic element; The active friction piece and the driven friction piece form a friction transmission pair in a way that the friction surfaces cooperate with each other, and the variable speed elastic element applies a pre-tightening force to make the driven friction piece fit with the active friction piece for transmission, and the driven friction piece passes through the first axial cam. The pair is matched with the hollow main shaft for transmission, and when the first axial cam pair outputs power through the hollow main shaft, it exerts an axial component force opposite to the pre-tightening force of the shifting elastic element on the driven friction piece; the driving power is input to a first overrunning clutch Thereby, the power is input to the active friction member; the hollow main shaft outputs the power to the differential through the planetary gear train, and the two half shafts of the differential are respectively connected with respective transmission shafts, and one of the transmission shafts The shaft rotates and fits through the hollow main shaft and is supported on the axle housing in a rotational fit; It also includes a secondary shaft, and the driving power is also input to the secondary shaft; The low-speed gear transmission mechanism includes a second overrunning clutch, and the secondary shaft transmits the low-speed gear power to the driven friction member through the second overrunning clutch; The reverse gear transmission mechanism is arranged in a manner that can transmit the reverse gear power to the driven friction member or disconnect the reverse gear power; The reverse gear transmission mechanism has a transmission ratio I for transmitting the reverse gear power from the countershaft to the driven friction member, and the low-speed gear transmission mechanism has a transmission ratio II for transmitting the low-speed gear power from the countershaft to the driven friction member, and the transmission ratio is I is greater than or equal to the transmission ratio II; The planetary gear train includes an outer ring gear, planetary gears, a planet carrier and a sun gear, and the outer ring gear is fixed to the axle housing. 2 . The mechanical double overrunning clutch adaptive automatic transmission axle with planetary system output according to claim 1 , wherein the second overrunning clutch and the reverse gear transmission mechanism both transmit power to the transmission through the second axial cam pair. 3 . driven friction. 3 . The mechanical double overrunning clutch adaptive automatic transmission axle with planetary system output according to claim 2 , wherein the housings of the differential are respectively extended to the left and right to form a rotational fit supported on the left side of the axle housing. 4 . The extension shaft section and the right extension shaft section, the hollow main shaft inputs the power to the sun gear and outputs the power to the right extension shaft section from the planet carrier, and the right half-shaft transmission connection of the differential is provided with a right transmission shaft, so The right transmission shaft rotatably passes through the hollow main shaft and is rotatably supported on the axle housing; the second axial cam pair is formed by a camshaft sleeve with an end face cam and an end face cam with the driven friction piece. The camshaft sleeve is rotatably fitted on the hollow main shaft, and the driven friction piece is fitted on the hollow main shaft through the first axial cam pair transmission; The inner ring of the first overrunning clutch is rotatably fitted over the camshaft sleeve and is driven and matched with the active friction member; the driving power is input to the outer ring of the first overrunning clutch and simultaneously input the power to the countershaft through the outer ring of the first overrunning clutch; The sun gear is coaxially matched with the hollow main shaft, the differential is in driving cooperation with the planet carrier, and the differential case is coaxial with the hollow main shaft. 4 . The mechanical double overrunning clutch adaptive automatic transmission axle of planetary system output according to claim 3 , wherein the low-speed transmission mechanism further comprises a low-speed driven gear and a low-speed driven gear meshing with the low-speed driven gear. 5 . a low-speed driving gear, the outer ring of the second overrunning clutch is arranged in cooperation with the outer ring or directly forms a low-speed driven gear, and the low-speed driving gear is arranged on the countershaft; the reverse gear transmission mechanism includes a reverse gear driving gear and a reverse driven gear meshing with the reverse drive gear, the reverse drive gear can be engaged or disengaged on the countershaft, the reverse driven gear and the inner ring of the second overrunning clutch and the camshaft sleeve The transmission fit and rotation fit are arranged on the hollow main shaft; the transmission ratio I is greater than the transmission ratio II. 5 . The mechanical double overrunning clutch adaptive automatic transmission axle of planetary system output according to claim 4 , wherein the reverse gear driving gear is arranged on the countershaft in a manner that can be engaged or disengaged by an electromagnetic shifting mechanism, 6 . The electromagnetic shifting mechanism is simultaneously used for switching the forward and reverse power input. 6 . The mechanical double overrunning clutch adaptive automatic transmission axle of planetary system output according to claim 5 , wherein the electromagnetic shifting mechanism comprises an active swing arm, a shifting shaft, a shifting fork and two Electromagnetic shifters, the two electromagnetic shifters are used to drive the active swing arm to swing around the axis of the shift shaft and drive the shift shaft to rotate around the axis of the shift shaft, and the shift shaft drives the shift fork Oscillate about the axis and complete the shift. 7 . The mechanical double overrunning clutch adaptive automatic transmission axle of planetary system output according to claim 6 , wherein the electromagnetic shifting mechanism is further provided with a positioning mechanism, and the positioning mechanism includes a positioning mechanism arranged on the active swing arm. 8 . Or a positioning pin with a pre-tightening force provided on the positioning part that is connected with the active swing arm and a positioning base provided on the axle housing, the positioning base is provided with a positioning pin that can cooperate with the positioning pin, and the position is the same as that of the reverse gear. The transmission mechanism engages or disengages the corresponding positioning dimples; the electromagnetic shifting mechanism is further provided with a position sensing component for detecting whether the gear shift is in place. 8 . The mechanical double overrunning clutch adaptive automatic transmission axle of planetary system output according to claim 3 , wherein the transmission elastic element is a transmission disc spring, and the transmission disc spring is sleeved on the hollow main shaft and has one end passing through the hollow main shaft. 9 . The plane bearing is against the driven friction piece, and the plane bearing is a plane rolling bearing with double rows of small balls along the radial direction; A transmission sleeve is provided in cooperation with the outer ring of the first overrunning clutch, and the transmission sleeve is used for inputting power in cooperation with the motor rotor, and is axially extended to form a journal that is rotatably supported on the axle housing, and the active friction member, Both the driven friction part and the speed change disc spring are located in the cavity between the transmission sleeve and the hollow main shaft. 9 . The planetary output mechanical double overrunning clutch adaptive automatic transmission axle according to claim 4 , wherein the second overrunning clutch and the reverse gear transmission mechanism both transmit power to the The second axial cam pair is thus transmitted to the driven friction piece, and the third axial cam pair is rotatably matched with the end face cam of the second cam shaft sleeve that is sleeved on the hollow main shaft and the end face of the end of the cam shaft sleeve facing away from the driven friction piece The cam cooperates to form; An intermediate driving gear is provided on the camshaft sleeve or the second camshaft sleeve in cooperation with the outer ring of the first overrunning clutch and is rotated and matched with the outer ring of the first overrunning clutch. ; The inner ring of the second overrunning clutch extends to the outer end of the shaft to form a shaft sleeve that is driven and fitted over the hollow main shaft, the shaft sleeve is rotatably supported on the axle housing, and the other end is driven and matched with the second cam shaft sleeve; One axial end of the outer ring of the first overrunning clutch is driven and matched with the intermediate driving gear, and the other end is fixedly connected to the transmission sleeve. The power output end of the hollow main shaft passes through and is rotatably supported on the axle housing. 10 . The mechanical double overrunning clutch adaptive automatic transmission axle with planetary system output according to claim 9 , wherein the outer circle of the shaft sleeve of the second overrunning clutch is rotatably supported on the axle housing through the first rolling bearing. 11 . ; The second camshaft sleeve is rotatably supported on the axle housing through a second rolling bearing, the second rolling bearing is located between the reverse driven gear and the intermediate driving gear, the intermediate driving gear extends axially to form a journal, and the second rolling bearing is located between the reverse driven gear and the intermediate driving gear. The journal is also rotatably supported on the axle housing through the fifth rolling bearing, the intermediate driving gear and the second rolling bearing are rotatably matched with the first plane bearing; the inner circle of the transmission sleeve is supported on the hollow main shaft through the fourth rolling bearing. ; A transmission wheel disc is provided in driving connection with the planet carrier, and the transmission wheel disc is axially formed with a transmission shaft sleeve, and the transmission shaft sleeve drives the outer sleeve on the rightward extending shaft end of the differential housing.

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