CN109990057B - Mechanical type double-overrunning clutch main shaft output self-adaptive automatic transmission - Google Patents
Mechanical type double-overrunning clutch main shaft output self-adaptive automatic transmission Download PDFInfo
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- CN109990057B CN109990057B CN201910285560.9A CN201910285560A CN109990057B CN 109990057 B CN109990057 B CN 109990057B CN 201910285560 A CN201910285560 A CN 201910285560A CN 109990057 B CN109990057 B CN 109990057B
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- 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
- F16H3/091—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 including a single countershaft
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- 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
- F16H2003/0818—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 comprising means for power-shifting
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- 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
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- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/72—Electric energy management in electromobility
Abstract
The invention discloses a mechanical self-adaptive automatic transmission with double overrunning clutch main shaft output, which comprises a main shaft for outputting power and a speed change system on the main shaft, wherein the speed change system comprises a low-speed gear transmission mechanism, a reverse gear transmission mechanism and a self-adaptive speed change component; the reverse gear transmission mechanism is provided with a transmission ratio I for transmitting reverse gear power from the auxiliary shaft to the 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 main shaft, and the transmission ratio I is larger than or equal to the transmission ratio II; the mechanical self-adaptive automatic transmission has the advantages that the reasonable matching of the two overrunning clutches is utilized, the transmission ratio of the reverse gear structure and the low-speed gear mechanism is reasonably set, the overall structure is simple and compact, the reverse gear transmission, the low-speed gear transmission and the high-speed gear transmission share a transmission route, the interference is avoided, the overall performance of the mechanical self-adaptive automatic transmission is ensured, the adaptability is strong, the mechanical self-adaptive automatic transmission is smoothly and naturally matched with the self-adaptive automatic transmission mechanism, and the mechanical self-adaptive automatic transmission is not only suitable for the field of electric vehicles, but also suitable for the field of other torque-variable mechanical transmissions.
Description
Technical Field
The invention relates to a motor vehicle transmission, in particular to a mechanical type self-adaptive automatic transmission with double overrunning clutch main shaft output.
Background
The mechanical transmission system generally has complex working conditions, needs to distribute torque to realize transmission of different loads and rotating speeds, and has complex and changeable driving environment by taking an electric vehicle as an example. In addition, the electric driving method generally adopted by the existing electric automobile is that a motor drives a fixed speed ratio, a high-efficiency reasonable interval is narrow and limited, and vicious circle is caused, so that the following problems are caused:
1. and the device can only work within the torque range of a certain working condition.
2. Under the condition of a fixed speed ratio, the rotating speed of the motor can only be increased to meet the road working condition, and the manufacturing cost of the motor is increased.
3. The motor generates heat, and the service efficiency and the service life are reduced;
4. if the requirement of the complex working condition of the electric automobile on the torque is to be met, the current and the rotating speed of the motor can only be continuously increased, the damage of heavy current discharge to the battery can only be considered, the peak power, the peak torque and the peak heavy current of the motor can only be utilized to drive the motor, and the discharge characteristic of a power battery pack is not followed completely;
5. the electric capacity of the power battery pack is rapidly reduced due to long duration of large-current discharge, the internal resistance of the battery cell is rapidly increased due to rapid temperature rise and temperature rise of the battery due to peak large-current discharge, the battery is subjected to great impact and irretrievable damage is caused, the electric storage capacity and the service life of the battery cell are sharply reduced, the number of charging cycles is rapidly reduced, and the problem of shorter and shorter endurance mileage is caused;
6. the energy recovery efficiency is low;
7. the high-speed motor acceleration and deceleration mechanism is essentially used for increasing power and torque, high-efficiency conversion cannot be realized, and the problems of rapid deterioration of the motor performance and low efficiency under rotation resistance can be caused under the working condition of low speed and heavy load; the battery, the controller, the electric appliance and the cable are damaged due to overload, especially the battery shortens the cycle life greatly and has poor economy;
however, the prior art has fatal defects and cannot overcome the defects of the driving method and the technical route which utilize the fixed speed ratio.
The existing automatic transmission adopts a solenoid valve and a servo motor, and realizes gear up and gear down through mechanical parts such as a synchronizer, a shifting fork, a gear ring and the like. The hydraulic control system has the advantages that the hydraulic control system is large in structural parts, power needs to be cut off, the speed of the motor instantly rises to the maximum, the driving power of the automobile disappears suddenly, the speed of the automobile drops under the action of driving resistance, the algorithm is complex, timely synchronous control is difficult to achieve, the cutting switching time is required to be short, the pause feeling is strong, the reliability is poor, and the like; there are problems of safety, comfort, reliability, etc.
In order to solve the above problems, the inventor of the present invention has invented a series of cam adaptive automatic transmission devices, which can detect driving torque-rotation speed and driving resistance-vehicle speed signals according to driving resistance, so that the output power of a motor or an engine is always in the best matching state with the vehicle driving condition, thereby realizing the balance control of the driving torque and the comprehensive driving resistance of the vehicle, the load of the cam adaptive automatic transmission device changes the transmission ratio along with the change of the driving force, the gear shifting and speed changing are automatically carried out along with the change of the driving resistance in a self-adaptive manner under the condition of not cutting off the driving force, and the motor or the engine always outputs torque at a high speed in a high efficiency region; the motor vehicle can run stably in mountainous areas, hills and heavy load conditions, and the safety is improved; the friction disc is adopted to form a separation and combination structure, so that the electric vehicle has the advantage of sensitive response, is small in axial size, and well solves the problems of the electric vehicle. Although the cam self-adaptive automatic speed changing device has the advantages that the cam self-adaptive automatic speed changing device is suitable for unidirectional power transmission of electric motorcycles and electric bicycles and is not suitable for speed changers of motor vehicles and mechanical devices needing bidirectional driving due to the adoption of a mechanical automatic speed changing structure, the overall size and the structural complexity of the speed changer can be increased if a traditional reverse gear transmission mechanism is adopted, and the cam self-adaptive automatic speed changing device cannot be well fused with the cam self-adaptive automatic speed changing device.
Therefore, a reverse gear transmission mechanism with high adaptability is added to the improved cam self-adaptive automatic speed change device, the device can automatically shift and change speed under the condition that the driving force is not cut off along with the change of the driving resistance in a self-adaptive manner, can solve the problem that a road with high efficiency runs forward and backward under complex conditions under the condition of bidirectional driving, is simple and compact in arrangement, is smoothly and naturally matched with the cam self-adaptive automatic speed change mechanism, reduces the manufacturing cost, and ensures the stability of transmission.
Disclosure of Invention
In view of the above, the present invention provides a mechanical dual overrunning clutch main shaft output adaptive automatic transmission, and a reverse gear transmission mechanism with strong adaptability is added, the device can not only self-adaptively perform gear shifting and speed changing under the condition of not cutting off driving force along with the change of driving resistance, but also solve the problem of forward and reverse driving of high efficiency roads under complex conditions under the condition of bidirectional driving, and has the advantages of simple and compact arrangement, smooth and natural matching with a cam adaptive automatic speed changing mechanism, reduced manufacturing cost and ensured transmission stability.
The invention relates to a self-adaptive automatic transmission of mechanical double-overrunning clutch main shaft output, which comprises a main shaft and a speed change system on the main shaft, wherein the speed change system comprises a low-speed gear transmission mechanism, a reverse gear transmission mechanism and a self-adaptive speed change component;
the self-adaptive speed change assembly comprises a driving friction piece, a driven friction piece and a speed change elastic element;
the driving friction piece and the driven friction piece form a friction transmission pair in a way that friction surfaces are mutually matched;
the speed-changing elastic element applies pretightening force for enabling the driven friction piece and the driving friction piece to be in fit transmission, the driven friction piece is in transmission fit with the main shaft through a first axial cam pair and outputs power through the main shaft, and when the power is output through the main shaft by the first axial cam pair, axial component force opposite to the pretightening force of the speed-changing elastic element is applied to the driven friction piece; the driving power is input to the active friction piece through a first overrunning clutch;
the driving power is also input into the auxiliary shaft;
the low-speed transmission mechanism comprises a second overrunning clutch, and the auxiliary shaft transmits low-speed power to the driven friction piece through the second overrunning clutch and outputs the power by the main shaft;
the reverse gear transmission mechanism is arranged in a mode that the reverse gear power can be transmitted to the driven friction piece, and the power is output or disconnected by the main shaft;
the reverse gear transmission mechanism has a transmission ratio I for transmitting reverse gear power from the auxiliary shaft to the driven friction piece, the low-speed gear transmission mechanism has a transmission ratio II for transmitting low-speed gear power from the auxiliary shaft to the driven friction piece, and the transmission ratio I is larger than or equal to the transmission ratio II.
Further, the second overrunning clutch and the reverse gear transmission mechanism transmit power to the driven friction piece through the second axial cam pair.
Further, the second axial cam pair is formed by matching a cam shaft sleeve with an end face cam and an end face cam arranged on a driven friction piece, the cam shaft sleeve is sleeved on the main shaft in a rotating matching mode, the driven friction piece is sleeved on the main shaft through a first axial cam pair in a transmission matching mode, and a power output piece for outputting power is arranged on the main shaft in a transmission matching mode.
The driving power is input from the outer ring of the first overrunning clutch, and the inner ring of the first overrunning clutch is in transmission connection with the driving friction piece; the driving power is also input into the auxiliary shaft through the outer ring of the first overrunning clutch.
Further, the low-speed transmission mechanism also comprises a low-speed driven gear and a low-speed driving gear meshed with the low-speed driven gear, the outer ring of the second overrunning clutch is arranged in a transmission matching mode or directly forms the low-speed driven gear, and the low-speed driving gear is arranged on the auxiliary shaft in a transmission matching mode; the reverse gear transmission mechanism comprises a reverse gear driving gear and a reverse gear driven gear meshed with the reverse gear driving gear, the reverse gear driving gear can be arranged on the auxiliary shaft in an engaging or separating mode, and the reverse gear driven gear and an inner ring of the second overrunning clutch are in transmission fit with the cam shaft sleeve and are arranged on the main shaft in a rotating fit manner; the transmission ratio I is larger than the transmission ratio II.
Furthermore, the reverse driving gear is arranged on the auxiliary shaft in a mode of being capable of being connected or separated through an electromagnetic gear shifting mechanism, and the electromagnetic gear shifting mechanism is used for switching the power source to rotate positively and negatively.
Further, electromagnetism gearshift includes initiative swing arm, the pivot of shifting gears, shifts the shift fork and two electromagnetism selector, two electromagnetism selector are used for driving the initiative swing arm around the axis swing of the pivot of shifting gears and drive the pivot of shifting gears around the axis of the pivot of shifting gears rotates, the pivot of shifting gears drives the shift fork of shifting gears around the axis swing is shifted and is accomplished.
Furthermore, the electromagnetic gear shifting mechanism is also provided with a positioning mechanism, the positioning mechanism comprises a positioning marble with pretightening force and a positioning base seat, the positioning marble is arranged on the driving swing arm or a positioning component which is connected with the driving swing arm in a follow-up manner, the positioning base seat is arranged on the transmission box body, and a positioning pit which can be matched with the positioning marble and is in joint or separation correspondence with the reverse gear transmission mechanism is arranged on the positioning base seat; the electromagnetic gear shifting mechanism is further provided with a position sensing assembly for detecting whether gear shifting is in place or not.
Furthermore, the speed-changing elastic element is a speed-changing disc spring, the speed-changing disc spring is sleeved outside the main shaft, one end of the speed-changing disc spring is abutted against the driven friction piece through a plane bearing, the other end of the speed-changing disc spring is abutted against a pre-tightening force adjusting assembly, and the plane bearing is a plane rolling bearing with double rows of small balls along the radial direction; the pretightning force adjusting part includes adjustable ring and adjusting nut, adjusting nut is located box external screw-thread fit and sets up in the main shaft, and the adjustable ring both ends are supported adjusting nut and variable speed dish spring axial slidable overcoat respectively and are worn out the box in main shaft and normal running fit.
Further, an intermediate driving gear is arranged in transmission fit with an outer ring of the first overrunning clutch, and an intermediate driven gear in transmission fit with the intermediate driving gear is arranged in transmission fit with the auxiliary shaft;
the middle driving gear is arranged on the camshaft sleeve in a rotating fit mode through a needle bearing, the inner ring of the second overrunning clutch extends towards the two axial ends to form a first end shaft sleeve and a second end shaft sleeve which are respectively sleeved on the main shaft in a transmission fit mode, the first end shaft sleeve is supported on the transmission box body in a rotating fit mode, and the second end shaft sleeve and the camshaft sleeve are integrally formed and supported on the transmission box body in a rotating fit mode;
one axial end of an outer ring of the first overrunning clutch is in transmission fit with the middle driving gear, the other end of the outer ring of the first overrunning clutch is fixedly connected with a support sleeve, the support sleeve is supported on the main shaft in a rotating fit mode, and a power output end of the main shaft penetrates through and is supported on the transmission box in a rotating fit mode; the driven friction piece, the driving friction piece and the speed change elastic element are positioned in an inner space formed by the support sleeve and the first overrunning clutch.
Furthermore, the first end shaft sleeve is supported on the transmission box body in a rotating fit mode through a first rolling bearing, the second end shaft sleeve is supported on the transmission box body in a rotating fit mode through a second rolling bearing, the second rolling bearing is located between the reverse gear driven gear and the middle driving gear, and the middle driving gear is in rotating fit with the second rolling bearing through a first plane bearing; the support sleeve is supported on the main shaft in a rotating fit manner through a fourth rolling bearing;
the power output part comprises an output shaft section, the output end of the main shaft forms an output shaft sleeve section, one end of the output shaft section extends into the output shaft sleeve section to form transmission fit, and the other end of the output shaft section extends out of an end cover fixedly connected to the transmission box body in a rotating fit mode.
The invention has the beneficial effects that: the mechanical type double-overrunning clutch spindle output self-adaptive automatic transmission has all the advantages of the existing cam self-adaptive automatic transmission, such as the capability of detecting a driving torque-rotating speed and a driving resistance-vehicle speed signal according to the driving resistance, so that the output power of a motor and the driving condition of a vehicle are always in the best matching state, the balance control of the driving torque of the vehicle and the comprehensive driving resistance is realized, and the self-adaptive automatic transmission automatically shifts and changes speed along with the change of the driving resistance under the condition of not cutting off the driving force; the motor vehicle can be used in mountainous areas, hills and heavy load conditions, so that the motor load changes smoothly, the motor vehicle runs stably, and the safety is improved;
the mechanical self-adaptive automatic transmission has the advantages that the transmission ratio of the reverse gear structure and the low-speed gear mechanism is reasonably set by utilizing the reasonable matching of the two overrunning clutches, so that the overall structure is simple and compact, the reverse gear transmission, the low-speed gear and the high-speed gear share a transmission route, and no interference occurs, the overall performance of the mechanical self-adaptive automatic transmission is ensured, the adaptability is strong, the mechanical self-adaptive automatic transmission is smoothly and naturally matched with the self-adaptive automatic speed change mechanism, the manufacturing cost is reduced, the transmission stability is ensured, and the mechanical self-adaptive automatic transmission is not only suitable for the field of electric vehicles, but also suitable for the field of other variable torque mechanical transmissions.
Drawings
The invention is further described below with reference to the figures and examples.
FIG. 1 is a schematic axial sectional view of the present invention;
FIG. 2 is a schematic diagram of an electromagnetic shift configuration;
FIG. 3 is a cross-sectional view of the electromagnetic shift structure;
FIG. 4 is a schematic view of an alternative output member configuration of the present invention;
FIG. 5 is a schematic structural view of the present invention employing a friction plate construction;
FIG. 6 is an enlarged view of the friction plate structure.
Detailed Description
Fig. 1 is a schematic axial section structure, fig. 2 is a schematic electromagnetic shift structure, and fig. 3 is a sectional electromagnetic shift structure, as shown in the drawings: the invention relates to a mechanical double-overrunning clutch spindle output self-adaptive automatic transmission, which comprises a spindle 1 and a speed change system on the spindle 1, wherein the speed change system comprises a low-speed gear transmission mechanism, a reverse gear transmission mechanism and a self-adaptive speed change component;
the self-adaptive speed change assembly comprises a driving friction piece, a driven friction piece and a speed change elastic element; the driving friction piece and the driven friction piece form a friction transmission pair in a way that friction surfaces are mutually matched;
in this embodiment, the driving friction member is a torus axial inner taper sleeve 18, and the driven friction member is a torus axial outer taper sleeve 2;
the inner cone sleeve 18 and the outer cone sleeve 2 form a friction transmission pair in a way that friction surfaces are matched with each other, as shown in fig. 1 and 4, the inner cone sleeve 18 is provided with an axial inner conical surface and sleeved outside the outer cone sleeve, the outer cone sleeve 2 is provided with an axial outer conical surface matched with the axial inner conical surface of the inner cone sleeve, and friction engagement transmission or separation is formed by the mutually matched conical surfaces, which is not described again;
certainly, the friction transmission pair can also adopt a friction plate structure as shown in fig. 5 and 6, the active friction piece 18 'and the inner ring of the first overrunning clutch are integrally formed or in transmission fit, the active friction piece 18' is provided with an active friction plate group 18a ', the driven friction piece 2' is provided with a driven friction plate group 2a 'matched with the active friction plate 18 a', the matching structure is similar to that of the existing friction plate type clutch, but the friction plates of the structure can be detachably arranged, and can be increased or decreased according to the needs of the integral structure, so as to ensure the axial dimension;
the variable-speed elastic element 19 applies pre-tightening force for enabling the annular body axial outer taper sleeve 2 and the annular body axial inner taper sleeve 18 to be in fit transmission, the annular body axial outer taper sleeve is in transmission fit with the main shaft 1 through a first axial cam pair, and when power is output by the first axial cam pair through the main shaft, axial component force opposite to the pre-tightening force of the variable-speed elastic element is applied to the annular body axial outer taper sleeve; the first axial cam pair 27 is an axial cam (including an end cam or a spiral cam) which is matched with each other, when the annular body axial outer taper sleeve rotates, the first axial cam pair 27 generates two component forces in the axial direction and the circumferential direction, wherein the component force in the circumferential direction outputs power, and the axial component force acts on the annular body axial outer taper sleeve and is applied to the speed change elastic element, that is, the turning direction of the first axial cam pair is related to the power output rotating direction; as shown in the figure, the annular body axial outer taper sleeve 2 is sleeved on the main shaft 1 in a transmission matching manner through the first axial cam pair 27, so that the first axial cam pair 27 is a spiral cam, the first axial cam pair 27 is formed by matching a spiral cam on the main shaft 1 with a spiral cam of the annular body axial outer taper sleeve 2, the spiral cam on the main shaft 1 and the spiral cam of the annular body axial outer taper sleeve 2 can be spiral cam grooves respectively, balls are embedded in the spiral cam grooves, transmission loss is reduced, and sensitivity is ensured, and further description is omitted; the driving power is input to the annular body axial inner taper sleeve through a first overrunning clutch 4, and the driving power can be realized through reasonable mechanical layout, and the description is omitted.
The driving power is also input into the auxiliary shaft;
the low-speed gear transmission mechanism comprises a second overrunning clutch, and the auxiliary shaft transmits low-speed gear power to the annular body axial outer taper sleeve through the second overrunning clutch;
the reverse gear transmission mechanism is arranged in a mode of transmitting reverse gear power to the annular body axial outer taper sleeve 2 or disconnecting the reverse gear power; the reverse gear transmission mechanism can be disconnected from the transmission of the annular body axial outer taper sleeve and the auxiliary shaft 12, and the purpose of the invention can be achieved;
the reverse gear transmission mechanism has a transmission ratio I for transmitting reverse gear power from the auxiliary shaft 12 to the annular body axial outer taper sleeve 2, the low-speed gear transmission mechanism has a transmission ratio II for transmitting low-speed gear power from the auxiliary shaft 12 to the annular body axial outer taper sleeve 2, and the transmission ratio I is larger than or equal to the transmission ratio II; when the reverse gear is driven, the second overrunning clutch is used for 6 overrunning, the rotating speed of the inner ring 6a (the rotating direction is the same as that of the reverse gear) is slower than that of the outer ring 6b (both the low-speed gear and the reverse gear are input by the auxiliary shaft), overrunning is formed, the reverse gear transmission mechanism smoothly drives, and otherwise, the reverse gear transmission mechanism is locked.
In this embodiment, the second overrunning clutch 6 and the reverse gear transmission mechanism transmit power to the annular body axial outer taper sleeve 2 through the second axial cam pair 26; the second axial cam pair is preferably of a cam structure with bidirectional output, because the low-speed transmission mechanism and the reverse transmission mechanism have different transmission directions.
In this embodiment, the second axial cam pair 26 is formed by matching a cam shaft sleeve 16 with an end cam and an end cam with an annular body axial outer taper sleeve 2, the cam shaft sleeve 16 is sleeved on the main shaft 1 in a rotating fit manner, the annular body axial outer taper sleeve 2 is sleeved on the main shaft 1 in a transmission fit manner through a first axial cam pair 27, a power output part 11 for outputting power is arranged on the main shaft 1 in a transmission fit manner, the embodiment is a power output gear combination structure integrally formed through an output shaft section, and a bevel gear can be output to a differential to form a rear axle and the like; in addition, the output of the main shaft can also adopt a structure as shown in fig. 4, a power output part 11 ' is arranged on the shaft section of the main shaft extending out of the box body in a transmission matching manner, the power output part 11 ' is a transmission shaft sleeve, a transmission wing ring for connecting and transmitting with the hub is formed on the outer circle of the transmission shaft sleeve, the structure can be directly used for installing the driving hub, and a rolling bearing 25 ' is arranged at the end part of the main shaft extending out of the transmission shaft sleeve and used for installing a flat fork or a supporting beam with the rotary support, which is not described again.
The driving power is input from the outer ring 4b of the first overrunning clutch 4, and as shown in the figure, the rotor of the motor is fixedly connected with the outer ring 4b through a transmission part to form power input transmission; the inner ring 4a of the first overrunning clutch 4 is in transmission connection with the annular body axial inner taper sleeve 18; the driving power is also input into the auxiliary shaft 12 through the outer ring of the first overrunning clutch, that is, the driving power is input in two paths, and the mode of inputting the auxiliary shaft 12 can adopt any existing mechanical transmission structure, such as gears, chains, even direct-connected transmission and the like, and is not described herein again.
In this embodiment, the low-speed transmission mechanism further includes a low-speed driven gear and a low-speed driving gear 7 engaged with the low-speed driven gear, the outer ring 6b of the second overrunning clutch 6 is arranged in a transmission matching manner or directly forms the low-speed driven gear, and the low-speed driving gear 7 is arranged on the auxiliary shaft 12 in a transmission matching manner; the reverse gear transmission mechanism comprises a reverse gear driving gear 9 and a reverse gear driven gear 8 meshed with the reverse gear driving gear 9, the reverse gear driving gear 9 can be arranged on the auxiliary shaft in an engaging (transmission) or separating (rotation) mode, the reverse gear driven gear 8 and an inner ring 6a of the second overrunning clutch 6 are in transmission fit with the cam shaft sleeve 16 and are arranged on the main shaft 1 in a rotating fit mode, and in the embodiment, the inner ring 6a of the second overrunning clutch 6 is integrally formed with the cam shaft sleeve 16; as shown in the drawings, the reverse gear driving gear 9 is disposed on the auxiliary shaft 12 in a rotationally engaged manner (needle bearing), and the engagement or disengagement of the auxiliary shaft is formed by a coupling member slidably and drivingly disposed on the auxiliary shaft, which belongs to a conventional engagement structure and is not described herein again; the transmission ratio I is larger than the transmission ratio II so as to ensure the smoothness of transmission and avoid the occurrence of locking.
In this embodiment, the reverse driving gear 9 is disposed on the auxiliary shaft 12 in a manner that the electromagnetic shift mechanism 10 can be engaged or disengaged, the electromagnetic shift mechanism is simultaneously used for switching the power source to rotate in the forward direction and the reverse direction, and in the process of switching the electromagnetic shift mechanism to the reverse gear, a signal is directly sent to the motor control system to control the motor to rotate in the reverse direction, so as to realize the reverse gear; the method can be realized by adopting a common signal acquisition mechanism or a switch.
In this embodiment, the electromagnetic shift mechanism includes an active swing arm 104, a shift spindle 105, a shift fork 106, and two electromagnetic shifters (an electromagnetic shifter 101 and an electromagnetic shifter 102), where the two electromagnetic shifters are configured to drive the active swing arm to swing around an axis of the shift spindle and drive the shift spindle to rotate around the axis of the shift spindle, and the shift spindle drives the shift fork to swing around the axis and complete shifting; as shown in the drawings, in this embodiment, the electromagnetic shifters 101 and 102 are arranged in parallel and respectively used for driving (or releasing) two ends of the driving swing arm, so that the driving swing arm 104 can swing around a central line, the shift shaft is in line with the central line, and is connected to the driving swing arm 104 to drive the driving swing arm to swing around the axis of the shift rotating shaft and drive the shift rotating shaft to rotate around the axis, the shift rotating shaft 105 drives the shift fork 106 to swing around the axis and drive the clutch (synchronizer) 17 to complete shifting, shifting of the clutch (synchronizer) belongs to the prior art, and is not described herein again; of course, the two electromagnetic gear shifters (the electromagnetic gear shifter 101 and the electromagnetic gear shifter 102) may be of an opposite structure, and the driving swing arm is driven to swing back and forth from two sides, so that the purpose of the invention can be achieved, and further description is omitted; the electromagnetic gear shifter is of a structure with a reciprocating push rod, when the electromagnetic gear shifter is powered on, the reciprocating push rod pushes out and pushes the driving swing arm to swing and then return, a return spring structure is generally adopted for returning, and the details are not repeated.
In this embodiment, the electromagnetic shift mechanism is further provided with a positioning mechanism 103, the positioning mechanism 103 includes a positioning pin 103b with pretightening force, which is arranged on the driving swing arm or on a positioning component 107 connected with the driving swing arm in a following manner, and a positioning base 103c arranged on the transmission case, and a positioning pit which can be matched with the positioning pin 103b and is in engagement with or separation from the reverse gear transmission mechanism is arranged on the positioning base 103 c; as shown in the figure, in this embodiment, the positioning pin is disposed on the positioning part 107, the positioning part 107 is provided with a positioning hole 103a for disposing the positioning pin 103b, and a positioning spring 103d for applying a pre-tightening force to the positioning pin 103b to be outwardly positioned and matched with the positioning pit is disposed in the positioning hole; the positioning marble slides on the surface of the positioning base in the swinging process, and enters the pit under the action of pretightening force to form positioning when sliding to the positioning pit; the electromagnetic gear shifting mechanism is further provided with a position sensing assembly used for detecting whether gear shifting is in place or not, and the sensing assembly generally adopts a Hall element and magnetic steel corresponding to the Hall element.
In this embodiment, the speed-changing elastic element is a speed-changing disc spring 19, the speed-changing disc spring 19 is externally sleeved on the main shaft 1, one end of the speed-changing disc spring 19 abuts against the annular body axially outer taper sleeve 2 through a plane bearing 28, the other end of the speed-changing disc spring abuts against a pre-tightening force adjusting assembly (a structure shown in fig. 5, the structure shown in fig. 1 is a structure without the pre-tightening force adjusting assembly), as shown in fig. 5, the speed-changing disc spring 19 is externally sleeved on the main shaft 1, one end of the speed-changing disc spring abuts against the annular body axially outer taper sleeve 2 through the plane bearing 28, the plane bearing 28 is a plane rolling bearing with double rows of small balls along the radial direction, and the small ball fingers are smaller than balls with the same bearing capacity in the prior art; the double rows of balls are adopted, so that the parameters of the balls can be reduced under the condition that the plane bearing bears the same load, the double rows of balls have the characteristics of stable rotation, high rotating speed of the same load and strong bearing capacity, and the axial installation size can be reduced; the pretightening force adjusting assembly comprises an adjusting ring 29 and an adjusting nut 30, the adjusting nut 30 is arranged on the main shaft 1 in a threaded fit manner, the adjusting ring 34 is sleeved outside the main shaft 1 in an axially slidable manner, and two ends of the adjusting ring respectively abut against the adjusting nut 30 and the variable speed disc spring; in the structure, the adjusting ring penetrates out of the transmission box body, so that the adjusting nut is positioned outside the box body, and the final disc spring pretightening force can be adjusted through the external adjusting nut, so that the structure is simple and practical, and the adjustment is convenient; of course, the construction of the pretension adjusting assembly shown in FIG. 5 can be used in the embodiment shown in FIG. 1, and will not be described herein.
In this embodiment, the intermediate driving gear 15 is disposed in transmission fit 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 reduced neck, the outer ring 4b of the first overrunning clutch 4 forms a stepped shaft sleeve, and the stepped shaft sleeve is sleeved on the stepped shaft to form transmission fit with the stepped shaft and has radial constraint capability, so as to ensure transmission and a certain supporting effect; the auxiliary shaft 12 is provided with an intermediate driven gear 14 in transmission fit with an intermediate driving gear 15;
the middle driving gear 15 is arranged on the cam shaft sleeve 16 in a rotating fit mode through a needle bearing 5, the inner ring 6a of the second overrunning clutch 6 extends towards the two axial ends to form a first end shaft sleeve (the left end in the figure) and a second end shaft sleeve (the right end in the figure) which are respectively sleeved on the main shaft 1 in a transmission fit mode, the first end shaft sleeve is supported on the transmission box body 20 in a rotating fit mode, and the second end shaft sleeve and the cam shaft sleeve 16 are integrally formed and supported on the transmission box body 20 in a rotating fit mode;
one axial end of an outer ring 4b of the first overrunning clutch 4 is in transmission fit with the middle driving gear 15, the other end of the outer ring is fixedly connected with a support sleeve 3, the support sleeve 3 is supported on the main shaft 1 in a rotating fit mode, and a power output end of the main shaft 1 penetrates through and is supported on the transmission box body 20 in a rotating fit mode; the annular body axial outer taper sleeve, the annular body axial inner taper sleeve and the speed-changing elastic element are positioned in an inner space formed by the support sleeve and the first overrunning clutch, so that the structure is compact and the bearing capacity is high;
in the structure of the embodiment, the power output and input section on the main shaft or/and the cam shaft sleeve is/are correspondingly and rotatably supported on the transmission box body, and in the structure, the cam shaft sleeve is sleeved on the main shaft to form a transmission and mutual support structure, so that larger torque can be transmitted without bending deformation, and the sizes of components under the condition of the same bearing capacity can be greatly reduced; aiming at each transmission bearing (power connection input and output section) part, the transmission bearing (power connection input and output section) parts are respectively supported in a transmission box body, so that a main shaft and a transmission shaft sleeve can be arranged longer, and additional bending moment generated by torque is transmitted to the box body due to the support, so that larger torque is transmitted per se, the rotating speed (the same component size) under large torque can be greatly improved, the indexes of large torque, high rotating speed and light weight are realized, the radial bearing and the shaft sleeve and the main shaft are mutually supported, the transmission has better stability and low noise under a high-speed state, compared with the prior art, the highest rotating speed for driving a motor and a high-speed reducer is more than or equal to 15000 r/min, the speed change mechanisms for efficient light-weight hub electric wheels and the like have greater advantages for energy conservation and environmental protection, and can be more suitable for pure electric vehicles taking energy conservation and environmental protection as main targets, of course, the invention is not only suitable for the field of electric vehicles, but also suitable for the field of other variable torque mechanical transmission.
In this embodiment, the first end shaft sleeve is supported by the transmission case 20 through a first rolling bearing 22 in a rotating fit manner, the second end shaft sleeve is supported by the transmission case 20 through a second rolling bearing 21 in a rotating fit manner (as shown, a support rib formed on the case is supported, and has a reinforcing effect on the case itself), the second rolling bearing 21 is located between the reverse driven gear 8 and the intermediate driving gear 15, and the intermediate driving gear 15 and the second rolling bearing 21 are rotatably supported through a first planar bearing 13 (planar rolling bearing); the power output end of the main shaft 1 penetrates through and is supported on the transmission box body 20 through a third rolling bearing 24 in a rotating matching mode, and the support sleeve is supported on the main shaft 1 through a fourth rolling bearing 23 in a rotating matching mode; if a variable speed adjusting assembly (as shown in fig. 5) is adopted, the adjusting ring is sleeved on the main shaft, and the main shaft is matched with the third rolling bearing and the fourth rolling bearing through the adjusting ring, which is not described in detail herein.
The power output part 11 comprises an output shaft section, the output end of the main shaft forms an output shaft sleeve section, one end of the output shaft section extends into the output shaft sleeve section to form transmission fit, and the other end of the output shaft section extends out of an end cover fixedly connected to the transmission box body in a rotating fit mode through a rolling bearing 25.
In the present invention, the left and right sides are based on the left and right sides of the attached drawings, and the recorded transmission connection includes all transmission connection structures in the prior art, including splines, flat keys, bolt fixing connection, and the like, and is not described herein again.
The above embodiments are merely the best structures of the present invention, and do not limit the scope of the present invention; the scheme is adjusted on the connection mode, and the realization of the vision of the invention is not influenced.
The fast-gear power transmission route of the embodiment:
power → the inner taper sleeve 18 in the axial direction of the torus → the outer taper sleeve 2 in the axial direction of the torus → the first axial cam pair → the main shaft 1 → the power output member 11 outputs power;
at this time, the second overrunning clutch overruns, and the resistance transmission route is as follows: the power output part 11 → the main shaft 1 → the first axial cam pair → the annular body axial outer taper sleeve 2 → the speed changing disc spring; the power output part 11 applies axial force to the annular body axial outer taper sleeve 2 through the first axial cam pair and compresses the speed change disc spring, when the driving resistance is increased to a certain degree, the axial force overcomes the speed change disc spring to separate the annular body axial inner taper sleeve 18 from the annular body axial outer taper sleeve 2, and power is transmitted through the following routes, namely a low-speed gear power transmission route:
power → the outer race 4b of the first overrunning clutch 4 → the counter shaft 12 → the low-speed drive gear → the outer race 6b of the second overrunning clutch 6 → the inner race 6a of the second overrunning clutch → the second axial cam pair → the torus axial outer taper sleeve 2 → the first axial cam pair → the main shaft → the pto 11 outputs power.
The low-speed power transmission route also passes through the following routes: and a second axial cam pair → a torus axial outer taper sleeve 2 → a compression speed change disc spring, so that reciprocating compression of the compression speed change disc spring in the low-speed gear transmission process is prevented, and the torus axial inner taper sleeve 18 and the torus axial outer taper sleeve 2 are prevented from being attached during low-speed gear transmission.
The transmission route shows that when the transmission mechanism runs, the annular body axial inner taper sleeve 18 and the annular body axial outer taper sleeve 8 are tightly attached under the action of the speed change disc spring to form an automatic speed change mechanism keeping a certain pressure, the pressure required by clutch meshing can be adjusted by increasing the axial thickness of the speed change shaft sleeve to achieve the transmission purpose, and at the moment, power drives the annular body axial inner taper sleeve 18, the annular body axial outer taper sleeve 2 and the main shaft 1 to enable the main shaft 1 to output power; the second overrunning clutch is in an overrunning state at the moment.
When the motor vehicle is started, the resistance is larger than the driving force, the resistance forces the cam shaft sleeve to rotate for a certain angle in the opposite direction, and the annular body axially compresses the speed change disc spring by the outer conical sleeve 2 under the action of the first axial cam pair; the annular body axial outer taper sleeve 2 and the annular body axial inner taper sleeve 18 are separated and synchronous, the second overrunning clutch is engaged, and the output power rotates at a low-speed gear speed; therefore, the low-speed starting is automatically realized, the starting time is shortened, and the starting force is reduced. Meanwhile, the speed change disc spring absorbs the motion resistance moment energy to transfer power to store potential energy for recovering the fast gear.
After the start is successful, the running resistance is reduced, when the component force is reduced to be less than the pressure generated by the speed change disc spring, the pressure of the speed change disc spring generated by the compression of the motion resistance is rapidly released and pushed, the annular body axial outer taper sleeve 2 and the annular body axial inner taper sleeve 18 are restored to the close fitting state, and the low-speed gear overrunning clutch is in an overrunning state.
In the driving process, the automatic gear shifting principle is the same as the principle of automatic gear shifting along with the change of the motion resistance, gear shifting is realized under the condition of not cutting off the driving force, the whole locomotive runs stably, safety and low consumption are realized, a transmission route is simplified, and the transmission efficiency is improved.
A reverse gear transmission route:
power → the outer race 4b of the first overrunning clutch 4 → the counter shaft 12 → the reverse drive gear → the reverse driven gear → the second axial cam pair 26 → the torus axial outer taper sleeve 2 → the first axial cam pair 27 → the main shaft 1 → the propeller shaft power output 11 outputs the reverse power.
At the moment, the transmission ratio of the reverse gear is larger than that of the low-speed gear and is reverse, the second overrunning clutch overruns, and the first overrunning clutch overruns to realize reverse gear transmission because the rotation is reverse and the rotating speed of the outer ring is higher than that of the inner ring; of course, both the low-speed transmission and the reverse transmission are downshifted transmissions, which are not described in detail herein.
Finally, the above embodiments are only for illustrating the technical solutions of the present invention and not for limiting, although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications or equivalent substitutions may be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, which should be covered in the claims of the present invention.
Claims (10)
1. A self-adaptive automatic transmission of mechanical double-overrunning clutch spindle output is characterized in that: the speed change system comprises a main shaft and a speed change system on the main shaft, wherein the speed change system comprises a low-speed transmission mechanism, a reverse transmission mechanism and a self-adaptive speed change assembly;
the self-adaptive speed change assembly comprises a driving friction piece, a driven friction piece and a speed change elastic element;
the driving friction piece and the driven friction piece form a friction transmission pair in a way that friction surfaces are mutually matched;
the speed-changing elastic element applies pretightening force for enabling the driven friction piece and the driving friction piece to be in fit transmission, the driven friction piece is in transmission fit with the main shaft through a first axial cam pair and outputs power through the main shaft, and when the power is output through the main shaft by the first axial cam pair, axial component force opposite to the pretightening force of the speed-changing elastic element is applied to the driven friction piece; the driving power is input to the active friction piece through a first overrunning clutch;
the driving power is also input into the auxiliary shaft;
the low-speed transmission mechanism comprises a second overrunning clutch, and the auxiliary shaft transmits low-speed power to the driven friction piece through the second overrunning clutch and outputs the power by the main shaft;
the reverse gear transmission mechanism is arranged in a mode that the reverse gear power can be transmitted to the driven friction piece, and the power is output or disconnected by the main shaft;
the reverse gear transmission mechanism has a transmission ratio I for transmitting reverse gear power from the auxiliary shaft to the driven friction piece, the low-speed gear transmission mechanism has a transmission ratio II for transmitting low-speed gear power from the auxiliary shaft to the driven friction piece, and the transmission ratio I is larger than or equal to the transmission ratio II.
2. The mechanical dual overrunning clutch spindle output adaptive automatic transmission of claim 1, wherein: and the second overrunning clutch and the reverse gear transmission mechanism transmit power to the driven friction piece through the second axial cam pair.
3. The mechanical dual overrunning clutch spindle output adaptive automatic transmission of claim 2, wherein: the second axial cam pair is formed by matching a cam shaft sleeve with an end face cam and an end face cam with a driven friction piece, the cam shaft sleeve is sleeved on the main shaft in a rotating matching mode, the driven friction piece is sleeved on the main shaft in a transmission matching mode through the first axial cam pair, and a power output piece for outputting power is arranged on the main shaft in a transmission matching mode;
the driving power is input from the outer ring of the first overrunning clutch, and the inner ring of the first overrunning clutch is in transmission connection with the driving friction piece; the driving power is also input into the auxiliary shaft through the outer ring of the first overrunning clutch.
4. The mechanical dual overrunning clutch spindle output adaptive automatic transmission of claim 3, wherein: the low-speed gear transmission mechanism further comprises a low-speed gear driven gear and a low-speed gear driving gear meshed with the low-speed gear driven gear, the outer ring of the second overrunning clutch is arranged in a transmission matching mode or directly forms the low-speed gear driven gear, and the low-speed gear driving gear is arranged on the auxiliary shaft in a transmission matching mode; the reverse gear transmission mechanism comprises a reverse gear driving gear and a reverse gear driven gear meshed with the reverse gear driving gear, the reverse gear driving gear can be arranged on the auxiliary shaft in an engaging or separating mode, and the reverse gear driven gear and an inner ring of the second overrunning clutch are in transmission fit with the cam shaft sleeve and are arranged on the main shaft in a rotating fit manner; the transmission ratio I is larger than the transmission ratio II.
5. The mechanical dual overrunning clutch spindle output adaptive automatic transmission of claim 4, wherein: the reverse gear driving gear is arranged on the auxiliary shaft in a manner of jointing or separating through an electromagnetic gear shifting mechanism, and the electromagnetic gear shifting mechanism is used for switching the forward and reverse rotation of the power source.
6. The mechanical dual overrunning clutch spindle output adaptive automatic transmission of claim 5, wherein: the electromagnetic gear shifting mechanism comprises an active swing arm, a gear shifting rotating shaft, a gear shifting fork and two electromagnetic gear shifters, wherein the two electromagnetic gear shifters are used for driving the active swing arm to swing around the axis of the gear shifting rotating shaft and driving the gear shifting rotating shaft to rotate around the axis of the gear shifting rotating shaft, and the gear shifting rotating shaft drives the gear shifting fork to swing around the axis and complete gear shifting.
7. The mechanical dual overrunning clutch spindle output adaptive automatic transmission of claim 6, wherein: the electromagnetic gear shifting mechanism is also provided with a positioning mechanism, the positioning mechanism comprises a positioning marble with pretightening force and arranged on the driving swing arm or a positioning component which is in follow-up connection with the driving swing arm, and a positioning base arranged on the gearbox box body, wherein a positioning pit which can be matched with the positioning marble and is in joint or separation with the reverse gear transmission mechanism is arranged on the positioning base; the electromagnetic gear shifting mechanism is further provided with a position sensing assembly for detecting whether gear shifting is in place or not.
8. The mechanical dual overrunning clutch spindle output adaptive automatic transmission of claim 1, wherein: the speed-changing elastic element is a speed-changing disc spring, the speed-changing disc spring is sleeved outside the main shaft, one end of the speed-changing disc spring abuts against the driven friction piece through a plane bearing, the other end of the speed-changing disc spring abuts against a pre-tightening force adjusting assembly, and the plane bearing is a plane rolling bearing with double rows of small balls along the radial direction; the pretightning force adjusting part includes adjustable ring and adjusting nut, adjusting nut is located box external screw-thread fit and sets up in the main shaft, and the adjustable ring both ends are supported adjusting nut and variable speed dish spring axial slidable overcoat respectively and are worn out the box in main shaft and normal running fit.
9. The mechanical dual overrunning clutch spindle output adaptive automatic transmission of claim 3, wherein: an intermediate driving gear is arranged in transmission fit with an outer ring of the first overrunning clutch, and an intermediate driven gear in transmission fit with the intermediate driving gear is arranged in transmission fit with the auxiliary shaft;
the middle driving gear is arranged on the camshaft sleeve in a rotating fit mode through a needle bearing, the inner ring of the second overrunning clutch extends towards the two axial ends to form a first end shaft sleeve and a second end shaft sleeve which are respectively sleeved on the main shaft in a transmission fit mode, the first end shaft sleeve is supported on the transmission box body in a rotating fit mode, and the second end shaft sleeve and the camshaft sleeve are integrally formed and supported on the transmission box body in a rotating fit mode;
one axial end of the outer ring of the first overrunning clutch is in transmission fit with the middle driving gear, the other end of the outer ring of the first overrunning clutch is fixedly connected with a support sleeve, the support sleeve is supported on the main shaft in a rotating fit mode, and the power output end of the main shaft penetrates through and is supported on the transmission box in a rotating fit mode; the driven friction piece, the driving friction piece and the speed change elastic element are positioned in an inner space formed by the support sleeve and the first overrunning clutch.
10. The mechanical dual overrunning clutch spindle output adaptive automatic transmission of claim 9, wherein: the first end shaft sleeve is supported on the transmission box body in a rotating fit mode through a first rolling bearing, the second end shaft sleeve is supported on the transmission box body in a rotating fit mode through a second rolling bearing, the second rolling bearing is located between the reverse gear driven gear and the middle driving gear, and the middle driving gear is in rotating fit with the second rolling bearing through a first plane bearing; the support sleeve is supported on the main shaft in a rotating fit manner through a fourth rolling bearing;
the power output part comprises an output shaft section, the output end of the main shaft forms an output shaft sleeve section, one end of the output shaft section extends into the output shaft sleeve section to form transmission fit, and the other end of the output shaft section extends out of an end cover fixedly connected to the transmission box body in a rotating fit mode.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910285560.9A CN109990057B (en) | 2019-04-10 | 2019-04-10 | Mechanical type double-overrunning clutch main shaft output self-adaptive automatic transmission |
| PCT/CN2020/084042 WO2020207447A1 (en) | 2019-04-10 | 2020-04-09 | Mechanical dual-overrunning clutch shaft output adaptive automatic gearbox shaft assembly, gearbox and drive system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910285560.9A CN109990057B (en) | 2019-04-10 | 2019-04-10 | Mechanical type double-overrunning clutch main shaft output self-adaptive automatic transmission |
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| CN109990057A CN109990057A (en) | 2019-07-09 |
| CN109990057B true CN109990057B (en) | 2022-06-03 |
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| CN201910285560.9A Expired - Fee Related CN109990057B (en) | 2019-04-10 | 2019-04-10 | Mechanical type double-overrunning clutch main shaft output self-adaptive automatic transmission |
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Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2020207447A1 (en) * | 2019-04-10 | 2020-10-15 | 西南大学 | Mechanical dual-overrunning clutch shaft output adaptive automatic gearbox shaft assembly, gearbox and drive system |
| CN111043257B (en) * | 2019-12-04 | 2022-03-18 | 西南大学 | Self-adaptive automatic speed change assembly adopting multi-piece type large-torque friction clutch |
| CN110949125B (en) * | 2019-12-04 | 2023-01-20 | 西南大学 | Double-overrunning self-adaptive automatic speed change system with transmission sensing function |
| CN111059172B (en) * | 2019-12-04 | 2022-03-01 | 西南大学 | Mechanical heavy-load self-adaptive automatic speed change assembly |
| CN112901729B (en) * | 2019-12-04 | 2022-04-08 | 西南大学 | Self-adaptive automatic speed change assembly adopting multi-row combined overrunning clutch |
| CN112901728B (en) * | 2019-12-04 | 2022-04-12 | 西南大学 | Double-overrunning self-adaptive automatic speed change system adopting multi-row floating overrunning clutch |
| CN110985652B (en) * | 2019-12-31 | 2021-02-05 | 西南大学 | Load detection system suitable for intelligent transmission speed change mechanism |
| CN115235757B (en) * | 2022-09-25 | 2022-12-13 | 山东驰勤机械有限公司 | Gearbox body performance monitoring management system based on data processing |
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