CN108757858B - Unpowered interruption automatic transmission - Google Patents
Unpowered interruption automatic transmission Download PDFInfo
- Publication number
- CN108757858B CN108757858B CN201810967492.XA CN201810967492A CN108757858B CN 108757858 B CN108757858 B CN 108757858B CN 201810967492 A CN201810967492 A CN 201810967492A CN 108757858 B CN108757858 B CN 108757858B
- Authority
- CN
- China
- Prior art keywords
- oil
- actuator
- gear
- executing
- executing element
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/32—Electric motors actuators or related electrical control means therefor
-
- 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
- F16H2306/00—Shifting
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses an automatic transmission without power interruption, which comprises a planetary gear speed change mechanism, a gear shifting executing mechanism and a transmission shell; the planetary gear speed change mechanism comprises a sun gear, a planet carrier and a gear ring; the gear shifting executing mechanism comprises a first executing element, a second executing element, an elastic mechanism and an actuator; the first executing element and the second executing element comprise friction plates and steel plates; the friction plate of the first executing element is connected with the gear ring, and the steel sheet is connected with the shell and can axially slide relative to the friction plate; the steel sheet of the second actuating element is connected with the planet carrier, and the friction plate is connected with the gear ring and can axially slide relative to the friction plate; the elastic mechanism is connected with the actuator and is used for interlocking and controlling the second executing element to be in a combining process in the process of separating the first executing element under the pushing of the actuator or in a separating process in the process of combining the first executing element. The invention has the advantages of no interruption of gear shifting, low cost and simple control.
Description
Technical Field
The invention relates to the field of speed changers, in particular to an automatic speed changer without power interruption.
Background
Various unpowered discontinuous transmissions are currently available for improving the power and smoothness of the shifting process. According to the different working principles, the unpowered discontinuous transmission is mainly divided into three types of double clutch type, double power source type and synchronous type.
The dual clutch transmission utilizes the overlap of the "on" state between the two clutches to achieve a power uninterrupted shift effect (e.g., CN201510342096.4 and CN 201510589161.3). The control is relatively complex and is commonly used on fixed-axis gear transmissions.
The double power source type transmission utilizes double power sources (2 motors or a combination of 1 motor and 1 engine, etc.) to realize power compensation in the gear shifting process (such as patents of CN201110181857.4 and CN201510381518.9, etc.). While such a configuration can achieve the same dual clutch configuration, it is apparent that the cost and control complexity is much higher than a dual clutch transmission.
The synchronous transmission utilizes the synchronous principle to realize the uninterrupted power switching between the high-speed gear and the low-speed gear (such as patents of CN201110094214.6, CN201710902598.7 and the like). However, the present invention is applicable to a transmission using a fixed-axis gear, and has a high dimensional accuracy requirement for a shift actuator, and the quality of the unpowered interruption is also affected as parts wear.
Disclosure of Invention
Therefore, it is desirable to provide an automatic transmission without power interruption to solve the problems of high cost and more complicated control of the automatic transmission without power interruption in the prior art.
In order to achieve the above object, the present inventors provide an automatic transmission without power interruption, including a planetary gear speed change mechanism, a gear shift executing mechanism, and a transmission housing, wherein the planetary gear speed change mechanism and the gear shift executing mechanism are disposed in the transmission housing;
the planetary gear speed change mechanism comprises a sun gear, a planet carrier and a gear ring; the gear ring and the sun gear are coaxially arranged, the planet gears are respectively meshed with the sun gear and the gear ring, and the planet carrier is respectively and movably connected with the sun gear and the planet gears;
the gear shifting executing mechanism comprises a first executing element, a second executing element, an elastic mechanism and an actuator; the first executing element and the second executing element comprise friction plates and steel plates which are arranged opposite to the friction plates;
the friction plate of the first actuating element is connected with the gear ring, and the steel sheet is connected with the shell in a key way and can axially slide relative to the friction plate;
the steel sheet of the second executing element is connected with the planet carrier, and the friction plate is connected with the gear ring key and can axially slide relative to the friction plate;
the elastic mechanism is connected with the actuator and is used for interlocking and controlling the second executing element to be in a combining process in the process of separating the first executing element or in a separating process in the process of combining the first executing element under the pushing of the actuator.
Further, the first executing element and the second executing element are respectively arranged at two end surfaces of the elastic mechanism in the extending direction, and one end surface of the elastic mechanism is connected with the first executing element or the second executing element.
Further, the elastic mechanism comprises a return spring, a supporting pressure plate and a movable pressure plate, wherein the supporting pressure plate and the movable pressure plate are arranged oppositely, and the return spring is arranged between the supporting pressure plate and the movable pressure plate.
Further, a first spline hub and a second spline hub are respectively arranged on the axial direction of the gear ring; the friction plate of the first executing element is connected with the gear ring through a first spline hub key and can axially slide; the friction plate of the second actuating element is connected with the gear ring through a second spline hub key and can axially slide.
Further, the first executing element and the second executing element comprise more than two friction plates and more than two steel plates, and the friction plates and the steel plates are arranged alternately.
Further, the actuator comprises an accumulator; the energy accumulator comprises an energy accumulator shell, a driving motor, an oil storage device and a piston push rod;
an oil cavity is formed in the energy accumulator shell and used for containing oil, a first oil port and a second oil port are formed in the energy accumulator shell, and an oil duct is connected to the first oil port;
the output shaft of the driving motor is arranged in the oil cavity, the output shaft of the driving motor is provided with a piston matched with the oil cavity, and the piston is used for extruding oil in the oil cavity to an oil duct under the pushing of the driving motor;
the oil duct is provided with a movable piston push rod, and the piston push rod is arranged opposite to the elastic mechanism and is used for moving to push the elastic mechanism to interlock the first execution unit and the second execution unit when receiving oil pressure;
the oil reservoir is communicated with the oil cavity through a second oil port, and the second oil port can be conducted or closed when the piston moves back and forth.
Further, the driving motor is a screw motor, and the piston is sleeved at the screw of the screw motor; the screw rod sleeve of the screw rod motor is provided with a screw rod nut, and the screw rod nut is propped against the piston and is used for pushing the piston when the screw rod rotates.
Further, the device also comprises a driving motor controller and an oil pressure sensor, wherein the driving motor controller is connected with the driving motor and used for controlling the starting and stopping of the driving motor and the rotation degree and the torsion in the working process; the oil pressure sensor is arranged at the inner wall of the oil cavity and is connected with the driving motor controller and used for detecting the oil pressure in the oil cavity of the energy accumulator.
Further, the first executing element and the second executing element further comprise limiting pieces; the limiting piece of the first executing element is arranged on the side surface of the steel sheet opposite to the shell; and the limiting piece of the second actuating element and the planet carrier are oppositely arranged on the side surface of the steel sheet.
Further, the planetary gear further comprises a power input shaft and a power output shaft, wherein the power input shaft is coaxially connected with the sun gear, the power output shaft is connected with the planet carrier, and the power output shaft can rotate when the planet carrier rotates; the power input shaft and the power output shaft are connected to the transmission shell through a supporting bearing of the power input shaft and a supporting bearing of the power output shaft respectively, a sealing ring of the power input shaft is sleeved on the supporting bearing of the power input shaft, and a sealing ring of the power output shaft is sleeved on the supporting bearing of the power output shaft.
The technical scheme is different from the prior art, and the unpowered automatic transmission comprises a planetary gear speed change mechanism, a gear shifting executing mechanism and a transmission shell, wherein the planetary gear speed change mechanism and the gear shifting executing mechanism are arranged in the transmission shell; the planetary gear speed change mechanism comprises a sun gear, a planet carrier and a gear ring; the planet gear is meshed with the sun gear and the gear ring respectively, and the planet carrier is movably connected with the sun gear and the planet gear respectively; the gear shifting executing mechanism comprises a first executing element, a second executing element, an elastic mechanism and an actuator; the first executing element and the second executing element both comprise friction plates and steel plates which are arranged opposite to the friction plates; the friction plate of the first executing element is connected with the gear ring, and the steel sheet is connected with the shell in a key way and can axially slide relative to the friction plate; the steel sheet of the second executing element is connected with the planet carrier, and the friction plate is connected with the gear ring key and can axially slide relative to the friction plate; the elastic mechanism is connected with the actuator and is used for interlocking and controlling the second executing element to be in a combining process in the process of separating the first executing element under the pushing of the actuator or in a separating process in the process of combining the first executing element. The arrangement realizes that one driving device controls to realize the switching of two gears, reduces the cost and the control difficulty, ensures that the interlocking states of the first execution element and the second execution element are overlapped to a certain extent in the gear shifting process of a user, realizes the power-free interruption gear shifting, and namely realizes the foolproof function of the transmission.
Drawings
FIG. 1 is a cross-sectional view of an automatic transmission with powerless interrupt shifting in accordance with an embodiment of the present invention;
FIG. 2 is a schematic diagram illustrating operation of an automatic transmission with power-free interruption shift according to an embodiment of the present invention;
fig. 3 is a second schematic operation diagram of the automatic transmission for power-interruption-free gear shifting according to an embodiment of the present invention.
Reference numerals illustrate:
1. a left shell;
2. a left end cover;
3. a support bearing for the power input shaft;
4. sealing rings of the power input shaft;
5. a power input shaft;
6. a planet wheel;
7. planetary gear pin shaft;
8. a planet carrier;
9. a gear ring;
10. a stop for the first actuator;
11. a first actuator;
12. a movable platen;
13. a screw motor;
14. an oil reservoir;
15. a piston;
16. an accumulator spring;
17. a screw nut;
18. a pressure sensor;
19. a clasp;
20. an accumulator seal ring;
21. a right shell;
22. a spline push block;
23. a piston push rod;
24. a support platen;
25. a return spring;
26. a return spring support pin;
27. a second actuator;
28. a limiting member of the second actuator;
29. a second spline hub;
30. a power output shaft;
31. sealing rings of the power output shaft;
32. a support bearing of the power output shaft;
33. a right end cover;
34. and a sun gear.
Detailed Description
In order to describe the technical content, constructional features, achieved objects and effects of the technical solution in detail, the following description is made in connection with the specific embodiments in conjunction with the accompanying drawings.
Referring to fig. 1 to 3, the present invention provides an automatic transmission without power interruption for shifting gears without power interruption during shifting gears.
Referring to fig. 1, in a specific embodiment, the automatic transmission without power interruption includes a planetary gear transmission mechanism, a gear shifting executing mechanism and a transmission housing, wherein the planetary gear transmission mechanism and the gear shifting executing mechanism are disposed in the transmission housing. Wherein the transmission housing comprises a left housing 1 and a right housing 21; the planetary gear speed change mechanism comprises a sun gear 34, a planet wheel 6, a planet carrier 8 and a gear ring 9; the gear ring 9 and the sun gear 34 are coaxially arranged, the planet gears 6 are respectively meshed with the sun gear 34 and the gear ring 9, the planet carrier 8 is respectively movably connected with the sun gear 34 and the planet gears 6, and when the sun gear 34 rotates, the planet gears 6 and the planet carrier 8 can revolve around the sun gear 34. The planet wheel 6 is movably connected with the planet carrier 8 through a planet wheel pin shaft 7, so that the planet carrier 8 can revolve around the sun wheel 34 together with the planet wheel 6.
The gear shifting executing mechanism comprises a first executing element 11, a second executing element 27, an elastic mechanism and an actuator; the first actuator 11 and the second actuator 27 each include a friction plate and a steel plate disposed opposite to the friction plate. One of the first actuator 11 and the second actuator 27 is a component of a brake, and the other is a component of a clutch, and both have two operating states of engagement and disengagement. The brake is used to stop movement of a structure, the clutch is used to separate or combine two components, and for ease of explanation, the first actuator 11 is a component of the brake, and the second actuator 27 is a component of the clutch.
In a specific embodiment, the friction plate of the first actuating element is connected with the gear ring 9, and the steel sheet is connected with the shell in a key way and can axially slide relative to the friction plate; the steel sheet of the second actuating element 27 is connected with the planet carrier 8, the friction plate is connected with the gear ring 9 in a key way and can axially slide relative to the friction plate, and the arrangement is such that the friction plates of the first actuating element 11 and the second actuating element 27 can be combined under the action of pushing force and separated under the action of no pushing force.
The elastic mechanism is connected with the actuator, and is used for interlocking and controlling the second actuator 27 to be in a combining process in the process of separating the first actuator 11 or the second actuator 27 to be in a separating process in the process of combining the first actuator 11 under the pushing of the actuator. If the brake applies pressure to the elastic mechanism, the elastic mechanism gradually extrudes the first actuating element 11 to enable the steel sheet and the friction plate of the first actuating element 11 to gradually approach, at the moment, the extrusion force of the elastic mechanism acting on the second actuating element 27 gradually disappears, the steel sheet and the friction plate of the second actuating element 27 gradually separate, and when the steel sheet and the friction plate of the first actuating element 11 are completely combined, the steel sheet and the friction plate of the second actuating element 27 are not completely separated yet; the pressure applied by the brake to the elastic mechanism gradually disappears, the extrusion force of the elastic mechanism to the first actuating element 11 gradually disappears, so that the steel sheet and the friction plate of the first actuating element 11 are gradually separated, at this time, the elastic mechanism gradually extrudes the second actuating element 27, so that the steel sheet and the friction plate of the second actuating element 27 are gradually close, and when the steel sheet and the friction plate of the first actuating element 11 are not completely separated, the steel sheet and the friction plate of the second actuating element 27 are completely combined. By the arrangement, when a user shifts gears, the transmission in the scheme cannot have power interruption, cannot have impact phenomenon after the shifting gears are completed, and can stably finish gear switching.
In a further embodiment, the first actuator 11 and the second actuator 27 are respectively disposed at two end surfaces of the elastic mechanism in the extending direction, and one end surface of the elastic mechanism is connected to the first actuator 11 or the second actuator 27. In case of an elongation or a shortening of the elastic means, the first or second actuator unit may be pushed to be axially coupled or decoupled.
In a further embodiment, the elastic mechanism comprises a return spring 25, a supporting pressure plate 24 and a movable pressure plate 12, wherein the supporting pressure plate 24 is arranged opposite to the movable pressure plate 12, and the return spring 25 is arranged between the supporting pressure plate 24 and the movable pressure plate 12 through a return spring supporting pin 26. This arrangement allows the return spring 25 to be more stable and not buckle when compressed or extended.
In a further embodiment, the gear ring 9 is provided with a first spline hub and a second spline hub 29, respectively, in the axial direction; the friction plate of the first actuating element 11 is connected with the gear ring 9 through a first spline hub key and can axially slide; the friction plates of the second actuator 27 are keyed to the ring gear 9 by means of a second splined hub 29 and are axially slidable. The arrangement enables the friction plate of the first actuator 11 to gradually approach the steel plate of the first actuator 11 under the external force applied by the elastic mechanism, thereby realizing the combination of the first actuator 11. The friction plate of the second actuator 27 may gradually approach the steel plate of the second actuator 27 when receiving the external force of the elastic mechanism, thereby realizing the combination of the second actuator 27.
In a further embodiment, the first actuator 11 and the second actuator 27 each comprise more than two friction plates and more than two steel plates, and the friction plates are arranged at intervals with the steel plates. This arrangement makes the coupling or decoupling of the first actuator 11 and the second actuator 27 more stable.
In a further embodiment, the actuator may be disposed outside or inside a housing of the transmission, and the actuator is an accumulator, including an accumulator housing, a driving motor, an oil reservoir 14, and a piston rod 23. The accumulator is used for generating and storing pressure which can act on the elastic mechanism, the oil storage 14 is used for storing oil, the piston push rod 23 pushes the elastic mechanism under the action of the driving motor, and in order to prevent oil pressure from being influenced by gaps between the piston push rod 23 and an oil duct, a piston push rod sealing ring is sleeved on the periphery of the piston push rod 23.
The energy accumulator is characterized in that an oil cavity is formed in the energy accumulator shell, a first oil port and a second oil port are formed in the energy accumulator shell, and an oil duct is connected to the first oil port. The output shaft of the driving motor is arranged in the oil cavity, the output shaft of the driving motor is provided with a piston 15 matched with the oil cavity, and the piston 15 is used for extruding oil in the oil cavity to an oil duct under the pushing of the driving motor. The oil duct is provided with a movable piston push rod 23, the piston push rod 23 is opposite to the elastic mechanism, the spline push block 22 acts on the elastic mechanism, and the piston push rod 23 is used for moving to push the elastic mechanism to interlock the first executing element 11 and the second executing element 27 when receiving oil pressure. The oil reservoir 14 communicates with the oil chamber through a second oil port that is opened or closed when the piston 15 reciprocates.
When the driving motor rotates positively, the output shaft of the driving motor acts on the piston 15, so that the piston 15 moves away from the driving motor to extrude oil in the oil cavity, the piston 15 continues to move after reaching the second oil port, the second oil port is sealed, the pressure in the oil cavity is gradually increased, the oil in the oil cavity is pressurized and extruded into the oil duct to push the piston push rod 23 to move away from the first oil port, and the piston push rod 23 extrudes the elastic mechanism. When the driving motor rotates reversely, the output shaft of the driving motor moves along the direction away from the first oil port along with the piston 15 until the piston 15 does not seal the second oil port, the second oil port is communicated, the pressure in the oil cavity is reduced, the oil in the oil cavity returns to the oil cavity, the piston push rod 23 approaches the first oil port, and the piston push rod 23 does not gradually squeeze the elastic mechanism.
The working principle of the first actuator 11 is as follows:
(1) Brake disengaged state (shown in fig. 2): when the right side of the piston push rod 23 is low-pressure oil, the supporting pressure plate 24 and the movable pressure plate 12 relatively move away from each other axially under the action of the spring force of the return spring 25. However, the pre-tensioned spring force, under the limitation of the second stop on the second splined hub 29, operates the steel and friction plates of the second actuator 27 in a "combined" state. At this time, the spring force received by the second actuator 27 belongs to an internal force, the whole second actuator 27 can move along the axial direction, and the friction plate and the steel plate of the first actuator 11 can be pushed to work in a 'separated' state by utilizing the inertia of oil throwing of the friction plate and the steel plate of the first actuator 11 at a high speed. That is, an oil film is gradually formed between the friction plate and the steel plate of the first actuator 11 due to the release of the pressing force, and the entire clutch moves rightward in the axial direction by the oil film.
(2) Brake-combined braking ring gear 9 state (shown in fig. 3): when the right side of the piston push rod 23 is high-pressure oil, the piston push rod 23 moves left along the axial direction under the action of oil pressure, and the movable pressure plate 12 is driven by the spline push block 22 to compress the return spring 25. The steel and friction plates of the first actuator 11 are operated in the "coupled" state by the spring force of the return spring 25.
The second actuator 27 operates on the principle that:
(1) Normally closed engaged state (shown in fig. 2): when the right side of the piston push rod 23 is low-pressure oil, the supporting pressure plate 24 and the movable pressure plate 12 are relatively axially far away under the action of the spring force of the return spring 25. The pre-tensioned spring force, under the restraint of the stop of the second actuator 27, causes the steel and friction plates of the second actuator 27 to operate in a "combined" state. Meanwhile, since the limiting member of the second actuator 27 acts the friction plate of the second actuator 27 and the spring force on the supporting pressure plate 24 on the second spline hub 29 respectively, a self-closing state of the second actuator 27 is achieved (i.e., the pressing spring force does not exert an acting force on a part outside the second actuator 27). In addition, under the inertia oil slinging, the friction plate and the steel plate of the first actuating element 11 are separated, and the second actuating element 27 is pushed to move to the right integrally (the second spline hub 29 is connected with the gear ring 9 through a key and can move axially).
(2) Separation state (shown in fig. 3): when the right side of the piston push rod 23 is high-pressure oil, the piston push rod 23 moves left along the axial direction under the action of oil pressure, and the movable pressure plate 12 is driven by the spline push block 22 to compress the return spring 25. Since the support platen 24 is constrained to the first actuator 11 and fixed, the left movement of the movable platen 12 causes the steel and friction plates of the second actuator 27 to operate in a "split" state.
The first actuator 11 and the second actuator 27 adopt a linkage-interlock design, that is, when the second actuator 27 operates in a combined state, the first actuator 11 correspondingly operates in a separated state; when the second actuator 27 operates in the disengaged state, the first actuator 11 correspondingly operates in the engaged state. Therefore, the transmission can be ensured not to be simultaneously hung into the wrong design of two gears, namely, the foolproof function of the transmission is realized.
For ease of explanation, the first actuator 11 is a component of the brake, and the second actuator 27 is a component of the clutch. In this case, if the transition from the high gear to the low gear is made, i.e. when the right side of the piston rod 23 is filled with high pressure oil, the entire clutch is first moved to the left. After the support platen 24 is moved to the left to be fixed by the brake, the left movement of the movable platen 12 gradually transitions the steel plates and friction plates of the clutch from the "engaged" state to the "disengaged" state. In this process, it is known from conservation of power that the internal torques of the sun gear 34, the carrier 8, and the ring gear 9 of the single-row planetary gear train are in a fixed proportional relationship in the low gear, that is, (1+k) ts=tc= (1+k) TR/K, and the internal torques of the sun gear 34, the carrier 8, and the ring gear 9 are equal in the high and low gears. Thus, as long as the torque Ts input by the sun gear 34 remains constant, the brake torque on the ring gear 9 does not reach K Ts, and the brake is in a half slip mode state; correspondingly, the clutch release force between the carrier 8 and the ring gear 9 gradually increases from 0 to Ts, and the clutch transitions from the engaged state to the disengaged state. When the clutch is thoroughly released, the brake gradually transitions from the semi-slip state to the engaged state as the brake braking force increases further. Therefore, the scheme can realize that the 'combined' states of the clutch and the brake are overlapped to a certain extent in the process of switching the high gear of the transmission to the low gear, and power cannot be interrupted.
Similarly, when the transmission is shifted from the low gear to the high gear, the right side of the piston rod 23 becomes low-pressure oil. The entire clutch gradually enters the engaged state by the elastic force of the return spring 25. At the moment, the moment of the brake gradually decreases from K Ts to 0, and the brake is in a half slip mode state in the process; correspondingly, the clutch release force between the carrier 8 and the ring gear 9 gradually decreases from K Ts to 0, and the clutch transitions from the released state to the engaged state. Therefore, the scheme can realize that the 'combined' states of the clutch and the brake are overlapped to a certain extent in the process of switching the low gear of the transmission to the high gear, and power cannot be interrupted.
In a further embodiment, the driving motor may be a linear motor or a screw motor 13, and when the driving motor is the screw motor 13, the piston 15 is sleeved at the screw of the screw motor 13; the screw sleeve of the screw motor 13 is provided with a screw nut 17, and the screw nut 17 abuts against the piston 15 and is used for pushing the piston 15 when the screw rotates. Specifically, the screw nut 17 is limited on the screw of the screw motor 13 through a snap ring 19, so that the screw nut 17 keeps a certain distance from the housing of the screw motor 13, and the screw nut 17 is prevented from being blocked too close to the housing of the screw motor 13. In addition, an accumulator spring is provided between the lead screw nut 17 and the piston 15 to reduce the impact of pressure on the piston 15.
In order to prevent oil in the oil chamber from leaking out of the gap between the piston 15 and the accumulator housing, in a further embodiment an accumulator sealing ring is arranged between the piston 15 and the accumulator housing.
When the lead screw motor 13 rotates clockwise, the lead screw nut 17 moves rightward pushing the piston 15 to move rightward by compressing the accumulator spring 16. In this way, high-pressure oil is generated under the sealing of the accumulator sealing ring 20 and the pressure oil is pressurized, so that the piston push rod 23 is pushed to move leftwards, and the gear shifting of the transmission is realized; when the lead screw motor 13 rotates counterclockwise, the lead screw nut 17 moves leftward, so that the compression accumulator spring 16 is gradually released, and finally, is returned to an initial state by the right high pressure oil. And after the second oil port is conducted, the high-pressure oil is converted into low-pressure oil. In this way, the piston rod 23 is moved rightward by the return spring 25, thereby effecting upshifting of the transmission.
In a further embodiment, the device further comprises a driving motor controller and an oil pressure sensor, wherein the driving motor controller is connected with the driving motor and used for controlling the starting or stopping of the driving motor; the oil pressure sensor is arranged at the position of the inner wall of the oil cavity, which is opposite to the piston 15, and is connected with the driving motor controller and used for detecting the oil pressure in the oil cavity of the energy accumulator. In this way, the oil pressure signal of the pressure sensor 18 can be utilized, and the driving motor controller can realize automatic adjustment of the working stroke of the screw motor 13, so that enough pressure is still applied after the friction plates in the first executing element 11 and the second executing element 27 are worn. In this way, a guarantee of shift consistency during powerless interrupt shifts can be achieved.
In order to prevent the steel sheets of the first actuator 11 and the second actuator 27 from being deviated when the first actuator 11 and the second actuator 27 are subjected to the pressing force of the elastic mechanism, in a further embodiment, the first actuator 11 and the second actuator 27 further comprise a stopper; the limiting piece 10 of the first executing element 11 is arranged on the side surface of the steel sheet opposite to the shell; the limiting piece 28 of the second actuating element is arranged on the side surface of the steel sheet opposite to the planet carrier 8. The arrangement is such that the friction plates and the steel plates of the first actuator 11, or the friction plates and the steel plates of the second actuator 27, can be joined when subjected to the pressing force of the elastic mechanism.
The scheme utilizes the structure design that the first executive element 11 and the second executive element 27 are interlocked in a linkage way and the whole second executive element 27 can axially move, and can realize that the working states of the first executive element 11 and the second executive element 27 in the gear shifting process of the automatic transmission are overlapped by a certain short-time 'combination state' so as to realize that the power is thoroughly without interruption. The planetary gear speed change mechanism can also be changed into a fixed-axis gear train. Meanwhile, the scheme realizes that 1 motor is controlled to realize the switching of 2 gears, and reduces the cost and the control difficulty. Meanwhile, with the abrasion of parts, the gear shifting quality such as smoothness of the power-free interrupted gear shifting is not changed.
In a further embodiment, the planetary gear set further comprises a power input shaft 5 and a power output shaft 30, wherein the power input shaft 5 is coaxially connected with the sun gear 34, the power output shaft 30 is connected with the planet carrier 8, and the power output shaft 30 can rotate when the planet carrier 8 rotates. The power input shaft 5 passes through the left end cover 2 of the transmission shell, the power output shaft 30 passes through the right end cover 33 of the transmission shell, or the power input shaft 5 passes through the right end cover 33 of the transmission shell, and the power output shaft 30 passes through the left end cover 2 of the transmission shell; the power input shaft 5 and the power output shaft 30 are respectively connected to the transmission housing through a power input shaft support bearing 3 and a power output shaft support bearing 32, the power input shaft support bearing 3 is sleeved with a power input shaft seal ring 4, and the power output shaft support bearing 32 is sleeved with a power output shaft seal ring 31.
It should be noted that, although the foregoing embodiments have been described herein, the scope of the present invention is not limited thereby. Therefore, based on the innovative concepts of the present invention, alterations and modifications to the embodiments described herein, or equivalent structures or equivalent flow transformations made by the present description and drawings, apply the above technical solution, directly or indirectly, to other relevant technical fields, all of which are included in the scope of the invention.
Claims (10)
1. The automatic transmission without power interruption is characterized by comprising a planetary gear speed change mechanism, a gear shifting executing mechanism and a transmission shell, wherein the planetary gear speed change mechanism and the gear shifting executing mechanism are arranged in the transmission shell;
the planetary gear speed change mechanism comprises a sun gear, a planet carrier and a gear ring; the gear ring and the sun gear are coaxially arranged, the planet gears are respectively meshed with the sun gear and the gear ring, and the planet carrier is respectively and movably connected with the sun gear and the planet gears;
the gear shifting executing mechanism comprises a first executing element, a second executing element, an elastic mechanism and an actuator; the first executing element and the second executing element comprise friction plates and steel plates which are arranged opposite to the friction plates;
the friction plate of the first executing element is connected with the gear ring, and the steel sheet is connected with the shell in a key way and can axially slide relative to the friction plate;
the steel sheet of the second executing element is connected with the planet carrier, and the friction plate is connected with the gear ring key and can axially slide relative to the friction plate;
the elastic mechanism is connected with the actuator and is used for interlocking and controlling the second executing element to be in a combining process in the process of separating the first executing element or in a separating process in the process of combining the first executing element under the pushing of the actuator;
the actuator acts on the elastic mechanism through the spline push block by the piston push rod, the elastic mechanism is directly connected with the first executing element through the movable pressure plate, and the elastic mechanism is directly connected with the second executing element through the supporting pressure plate.
2. The automatic transmission according to claim 1, wherein the first actuator and the second actuator are provided at both end surfaces in the expansion and contraction direction of the elastic mechanism, respectively, and one end surface of the elastic mechanism is connected to the first actuator or the second actuator.
3. The automatic transmission of claim 1, wherein the elastic mechanism comprises a return spring, a support platen, and a movable platen, the support platen being disposed opposite the movable platen, the return spring being disposed between the support platen and the movable platen.
4. The automatic transmission with no power interruption according to claim 1, wherein the ring gear is provided with a first spline hub and a second spline hub, respectively, in an axial direction; the friction plate of the first executing element is connected with the gear ring through a first spline hub key and can axially slide; the friction plate of the second actuating element is connected with the gear ring through a second spline hub key and can axially slide.
5. The automatic transmission of claim 1, wherein the first and second actuators each comprise two or more friction plates and two or more steel plates, the friction plates being spaced from the steel plates.
6. The powerless automatic transmission of claim 1, wherein the actuator comprises an accumulator; the energy accumulator comprises an energy accumulator shell, a driving motor, an oil storage device and a piston push rod;
an oil cavity is formed in the energy accumulator shell and used for containing oil, a first oil port and a second oil port are formed in the energy accumulator shell, and an oil duct is connected to the first oil port;
the output shaft of the driving motor is arranged in the oil cavity, the output shaft of the driving motor is provided with a piston matched with the oil cavity, and the piston is used for extruding oil in the oil cavity to an oil duct under the pushing of the driving motor;
the oil duct is provided with a movable piston push rod, and the piston push rod is arranged opposite to the elastic mechanism and is used for moving to push the elastic mechanism to interlock the first execution unit and the second execution unit when receiving oil pressure;
the oil reservoir is communicated with the oil cavity through a second oil port, and the second oil port can be conducted or closed when the piston moves back and forth.
7. The automatic transmission without power interruption of claim 6, wherein the driving motor is a screw motor, and the piston is sleeved at a screw of the screw motor; the screw rod sleeve of the screw rod motor is provided with a screw rod nut, and the screw rod nut is propped against the piston and is used for pushing the piston when the screw rod rotates.
8. The automatic transmission without power interruption of claim 6, further comprising a drive motor controller and an oil pressure sensor, wherein the drive motor controller is connected with the drive motor for controlling the degree of rotation and torque during start, stop and operation of the drive motor; the oil pressure sensor is arranged at the inner wall of the oil cavity and is connected with the driving motor controller and used for detecting the oil pressure in the oil cavity of the energy accumulator.
9. The powerless interrupt automatic transmission of claim 1, wherein the first and second actuators further comprise a limiter; the limiting piece of the first executing element and the transmission shell are arranged on the side surface of the steel sheet in a way of being opposite to each other; and the limiting piece of the second actuating element and the planet carrier are oppositely arranged on the side surface of the steel sheet.
10. The automatic transmission without power interruption of claim 1, further comprising a power input shaft and a power output shaft, the power input shaft being coaxially connected with the sun gear, the power output shaft being connected with the carrier, the power output shaft being autorotatable upon rotation of the carrier; the power input shaft and the power output shaft are connected to the transmission shell through a supporting bearing of the power input shaft and a supporting bearing of the power output shaft respectively, a sealing ring of the power input shaft is sleeved on the supporting bearing of the power input shaft, and a sealing ring of the power output shaft is sleeved on the supporting bearing of the power output shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810967492.XA CN108757858B (en) | 2018-08-23 | 2018-08-23 | Unpowered interruption automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810967492.XA CN108757858B (en) | 2018-08-23 | 2018-08-23 | Unpowered interruption automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108757858A CN108757858A (en) | 2018-11-06 |
| CN108757858B true CN108757858B (en) | 2023-09-12 |
Family
ID=63966566
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810967492.XA Active CN108757858B (en) | 2018-08-23 | 2018-08-23 | Unpowered interruption automatic transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108757858B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109340326B (en) * | 2018-12-07 | 2023-08-29 | 福州锐智新能源科技有限公司 | Two-control three-gear three-speed transmission |
| CN110578776A (en) * | 2019-07-12 | 2019-12-17 | 福州锐智新能源科技有限公司 | Single gear train linkage gear shifting transmission |
| CN211259607U (en) * | 2019-09-29 | 2020-08-14 | 湖南奕普汽车科技有限公司 | Automatic gearbox gearshift |
Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB829854A (en) * | 1957-02-20 | 1960-03-09 | Allis Chalmers Mfg Co | Improved change speed power transmission mechanism |
| GB831661A (en) * | 1957-05-10 | 1960-03-30 | Axel Charles Wickman | Epicyclic power transmission mechanisms |
| GB1211482A (en) * | 1967-08-16 | 1970-11-04 | Porsche Kg | Hydraulic control for change speed gear transmission |
| US6397994B1 (en) * | 2001-01-10 | 2002-06-04 | New Venture Gear, Inc. | Powershift transmission with engine clutch assembly |
| CN101245848A (en) * | 2007-09-26 | 2008-08-20 | 湖南江麓容大车辆传动有限责任公司 | Shifting mechanism |
| CN202790356U (en) * | 2012-07-12 | 2013-03-13 | 福建省福工动力技术股份公司 | Planetary gear transmission with dual-friction clutches |
| CN103291859A (en) * | 2013-01-16 | 2013-09-11 | 清华大学 | Automatic power-preserving mechanical three-gear transmission of automobile |
| CN106939929A (en) * | 2017-05-19 | 2017-07-11 | 福建万润新能源科技有限公司 | A kind of shift transmission of mono-tooth ring dry friction external control three |
| CN107401603A (en) * | 2016-05-19 | 2017-11-28 | 马自达汽车株式会社 | The control method and control device of automatic transmission |
| CN107542917A (en) * | 2017-08-24 | 2018-01-05 | 江苏大学 | A kind of power failure-free gear shift automatic speed changer for machine hybrid drive train |
| CN108274986A (en) * | 2017-12-29 | 2018-07-13 | 綦江齿轮传动有限公司 | Oil and electricity hybrid vehicle transmission assembly |
| CN108426031A (en) * | 2018-05-21 | 2018-08-21 | 福建中青集团有限公司 | A kind of single control interlocking-type electric automobile gear device shift mechanism and speed changer |
| CN208634295U (en) * | 2018-08-23 | 2019-03-22 | 福州锐智新能源科技有限公司 | A kind of power failure-free automatic transmission |
-
2018
- 2018-08-23 CN CN201810967492.XA patent/CN108757858B/en active Active
Patent Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB829854A (en) * | 1957-02-20 | 1960-03-09 | Allis Chalmers Mfg Co | Improved change speed power transmission mechanism |
| GB831661A (en) * | 1957-05-10 | 1960-03-30 | Axel Charles Wickman | Epicyclic power transmission mechanisms |
| GB1211482A (en) * | 1967-08-16 | 1970-11-04 | Porsche Kg | Hydraulic control for change speed gear transmission |
| US6397994B1 (en) * | 2001-01-10 | 2002-06-04 | New Venture Gear, Inc. | Powershift transmission with engine clutch assembly |
| CN101245848A (en) * | 2007-09-26 | 2008-08-20 | 湖南江麓容大车辆传动有限责任公司 | Shifting mechanism |
| CN202790356U (en) * | 2012-07-12 | 2013-03-13 | 福建省福工动力技术股份公司 | Planetary gear transmission with dual-friction clutches |
| CN103291859A (en) * | 2013-01-16 | 2013-09-11 | 清华大学 | Automatic power-preserving mechanical three-gear transmission of automobile |
| CN107401603A (en) * | 2016-05-19 | 2017-11-28 | 马自达汽车株式会社 | The control method and control device of automatic transmission |
| CN106939929A (en) * | 2017-05-19 | 2017-07-11 | 福建万润新能源科技有限公司 | A kind of shift transmission of mono-tooth ring dry friction external control three |
| CN107542917A (en) * | 2017-08-24 | 2018-01-05 | 江苏大学 | A kind of power failure-free gear shift automatic speed changer for machine hybrid drive train |
| CN108274986A (en) * | 2017-12-29 | 2018-07-13 | 綦江齿轮传动有限公司 | Oil and electricity hybrid vehicle transmission assembly |
| CN108426031A (en) * | 2018-05-21 | 2018-08-21 | 福建中青集团有限公司 | A kind of single control interlocking-type electric automobile gear device shift mechanism and speed changer |
| CN208634295U (en) * | 2018-08-23 | 2019-03-22 | 福州锐智新能源科技有限公司 | A kind of power failure-free automatic transmission |
Non-Patent Citations (1)
| Title |
|---|
| 电控机械式自动变速器制动装置研究;李惠军;邱辉鹏;李晓亮;;汽车工程师(第06期);全文 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108757858A (en) | 2018-11-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108757858B (en) | Unpowered interruption automatic transmission | |
| JP5789508B2 (en) | Synchronous lock clutch-combination of friction clutch and mechanical locking clutch | |
| CN108443433B (en) | Single-actuator type two-gear transmission for electric vehicle | |
| US4732253A (en) | Power transmission | |
| JP5874839B2 (en) | Brake device for transmission and control system therefor | |
| RU2561431C2 (en) | Dual clutch with differentiating element | |
| WO2011037023A1 (en) | Drive device for vehicle, using electric motor | |
| CN108426031B (en) | Single-control interlocking type electric automobile transmission gear shifting mechanism and transmission | |
| CN208634295U (en) | A kind of power failure-free automatic transmission | |
| JP2004138131A (en) | Operating device for synchro-mechanism in power train in automobile | |
| CN114412972B (en) | Planetary gear transmission, power assembly and vehicle | |
| CA2772410A1 (en) | Shift cylinder, drive device, work machine as well as method for operating a work machine | |
| JP5922221B2 (en) | Compensation device for changing the operating state of a shift element | |
| JP2009513891A (en) | Automatic transmission with hydraulically operated shift element | |
| CN109372961A (en) | A kind of single controlled three-speed gearbox | |
| CN208169450U (en) | A kind of dynamic device formula two speed gear of electronic automobile-used nonoculture | |
| CN109340326A (en) | One kind two controls three formula three-speed gearboxes | |
| JP2003148515A (en) | Hydraulic engagement device | |
| JP7031476B2 (en) | Friction fastening device | |
| CN209196052U (en) | One kind two controls three formula three-speed gearboxes | |
| CN110578776A (en) | Single gear train linkage gear shifting transmission | |
| US7086976B2 (en) | Electric motor applied clutch with a drag torque actuator | |
| CN102741587A (en) | Combined transmission system | |
| CN211202771U (en) | Single gear train linkage gear shifting transmission | |
| JP2011033071A (en) | Electric motor drive device for vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |