CN111255864B - Planetary wheel type two-gear gearbox based on pawl overrunning clutch and control method - Google Patents

Planetary wheel type two-gear gearbox based on pawl overrunning clutch and control method Download PDF

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Publication number
CN111255864B
CN111255864B CN202010137928.XA CN202010137928A CN111255864B CN 111255864 B CN111255864 B CN 111255864B CN 202010137928 A CN202010137928 A CN 202010137928A CN 111255864 B CN111255864 B CN 111255864B
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China
Prior art keywords
gear
pawl
ring
control
clutch
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CN202010137928.XA
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Chinese (zh)
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CN111255864A (en
Inventor
韩毓东
岳汉奇
蔡文奇
高炳钊
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Jilin Bocheng Transmission System Technology Co ltd
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Jilin Bocheng Transmission System Technology Co ltd
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like
    • F16D41/14—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like the effective stroke of the pawl being adjustable
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/028—Gearboxes; Mounting gearing therein characterised by means for reducing vibration or noise
    • 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
    • F16H61/04—Smoothing ratio shift
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • 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
    • F16H61/04—Smoothing ratio shift
    • F16H2061/0425—Bridging torque interruption
    • 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
    • F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears
    • 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
    • F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
    • F16H2200/2082—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches one freewheel mechanisms

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses a planetary wheel type two-gear gearbox based on a pawl type overrunning clutch and a control method, wherein the gearbox consists of an input shaft, a diaphragm spring clutch, a planetary wheel type transmission mechanism, a pawl type overrunning clutch assembly and an output shaft, the pawl type overrunning clutch assembly realizes locking or overrunning through pawls arranged between an outer ring and an inner ring in pairs, the pawls are connected with a control ring at the outer side in the axial direction through pawl control pins, and the control ring controls the pawl control pins to drive the pawls to swing up and down through control windows arranged on the control ring, so that the bidirectional locking, unidirectional locking or bidirectional overrunning of the clutch is realized; the control method comprises a first gear forward control method, a second gear forward control method, a first gear reverse control method and a power interruption-free gear shifting control method. The invention realizes the forward and backward of one gear, can carry out the powerless interrupt gear shifting, can bear larger load and further improves the gear shifting effect.

Description

Planetary wheel type two-gear gearbox based on pawl overrunning clutch and control method
Technical Field
The invention belongs to the technical field of electric vehicle transmission systems, and particularly relates to a planetary wheel type two-gear gearbox based on a pawl overrunning clutch and a control method.
Background
The technical scheme provided in the patent application number 2019103261167, named as a planetary unpowered interruption two-gear gearbox and a gear shifting control method thereof, solves the problem of power interruption of traditional AMT gear shifting, can realize unpowered interruption gear shifting, the gear box always has power output in the gear shifting process of upshifting or downshifting, smoothness in the gear shifting process is improved, smooth speed ratio switching process can be realized, and the planetary unpowered interruption two-gear gearbox can realize one-gear forward and one-gear reverse, so that the safety problem of the phenomenon that the reverse speed of a two-gear reversing device is too high and the overrunning clutch is blocked in the prior art is effectively solved.
However, the controllable overrun clutch adopted in the technical scheme is a roller overrun clutch, the power transmitted by the roller overrun clutch is limited, and the overload is easy to be severely worn, so that the phenomenon of slip failure occurs; in addition, the controllability of the roller in the roller overrunning clutch is low, and the control effect of the clutch is poor. Therefore, the transmission performance of the gearbox in the technical scheme of the patent is affected.
Disclosure of Invention
Aiming at the defects in the prior art, the invention discloses a planetary wheel type two-gear gearbox based on a pawl overrunning clutch and a control method thereof, which can bear larger load and further improve the gear shifting effect on the basis of realizing the forward and backward of a first gear and being capable of carrying out power-interruption-free gear shifting. The technical scheme of the invention is as follows:
Planetary wheel type two keeps off gearbox based on pawl formula overrunning clutch includes: the device comprises an input shaft 2, a diaphragm spring clutch 3, a planetary wheel type transmission mechanism, an overrunning clutch assembly and an output shaft 10, wherein the planetary wheel type transmission mechanism consists of a planet carrier 5, a gear ring 7, a planet wheel 8 and a sun wheel 9, the diaphragm spring clutch 3 is arranged on the input shaft 2 which is coaxially and fixedly connected with the sun wheel 9, a flywheel disc 38 of the diaphragm spring clutch 3 is coaxially connected with the gear ring 7, and the output shaft 10 is coaxially connected with the planet carrier 5;
the overrunning clutch assembly is a pawl overrunning clutch assembly 6 and consists of a pawl overrunning clutch and a clutch control mechanism;
the pawl type overrunning clutch consists of an outer ring 61, a control ring 62, a forward pawl 63, a reverse pawl 64 and an inner ring, wherein the outer ring 61 is fixed on a gearbox shell 4, the inner ring is positioned on the outer side of a gear ring 7 and is integrally arranged with the gear ring 7, the forward pawl 63 and the reverse pawl 64 are uniformly arranged in an annular space between the outer ring 61 and the inner ring in pairs, pawl roots of the forward pawl 63 and the reverse pawl 64 are rotatably arranged on the outer ring 61, pawl heads of the forward pawl 63 and the reverse pawl 64 are oppositely arranged and are clamped with pawl clamping grooves on the outer circumferential surface of the inner ring, a folding leaf spring is arranged between the forward pawl 63 and the reverse pawl 64 and the outer ring 61, the forward pawl 63 and the reverse pawl 64 are respectively connected with a forward control window 622 and a reverse control window 623 on the control ring 62 in a sliding mode through pawl control pins arranged on axial side surfaces of the forward pawl 63, and the reverse pawl 64 swing up and down under rotation control of the control ring 62, and bidirectional locking, unidirectional locking or bidirectional overrunning between the gear ring 7 and the outer ring 61 is further achieved.
The clutch control mechanism is composed of a control motor 65, a transmission shaft 66, a worm 57, a sensor 68 and a worm gear 69, wherein the control motor 65 is fixedly connected with one end of the transmission shaft 66 coaxially, the sensor 68 is arranged at the other end of the transmission shaft 66, the worm 57 is coaxially arranged on the transmission shaft 66 and is meshed with the worm gear 69 coaxially fixed on the outer circumference of the control ring 62, and the control ring 62 is further controlled to rotate.
Further, on the control ring 62, the control surface at the bottom of the forward control window 622 is a forward control window inclined plane 624 and a forward control window plane 625 which are sequentially and continuously arranged along the rotation direction of the control ring 62, the control surface at the bottom of the reverse control window 623 is a reverse control window plane 626 and a reverse control window inclined plane 627 which are sequentially and continuously arranged along the rotation direction of the control ring 62, wherein the forward control window inclined plane 624 and the reverse control inclined plane 627 are curved surfaces gradually approaching the center of the control ring 62 along the rotation direction of the control ring 2, and the forward control window plane 625 and the reverse control window plane 626 are curved surfaces concentrically arranged with the control ring 62.
Further, a plurality of pawl clamping groove pairs are uniformly formed in the outer circular surface of the inner ring along the circumferential direction, each group of clamping groove pairs consists of two pawl clamping grooves, the two pawl clamping grooves are respectively matched with the pawl heads of the forward pawl 63 and the reverse pawl 64, and when the clamping grooves of the inner ring rotate to any one group of pawl pairs, the forward pawl 63 and the reverse pawl 64 can find pawl clamping grooves matched and clamped with the pawl clamping grooves in the corresponding pawl clamping groove pairs in the outer circular surface of the inner ring.
Further, the inner side wall of the outer ring 61 is provided with a plurality of pawl mounting groove pairs corresponding to the forward pawl 63 and the reverse pawl 64 one by one, and each pawl mounting groove in the pawl mounting groove pairs is provided with a folding leaf spring mounting groove.
Further, the diaphragm spring clutch 3 release bearing 31, the diaphragm spring 32, the spring support ring 33, the clutch cover 34, the pressure plate 35, the friction plate 36 and the flywheel disc 38 are sequentially arranged from front to back;
the flywheel disc 38 is coaxially connected with the connecting end of the gear ring 7 through a spline 39, the friction plate 36 is coaxially and fixedly connected to the input shaft 2, the pressure plate 35 is coaxially arranged at the front end of the friction plate 36, the clutch cover 34 is covered on the outer sides of the pressure plate 35 and the friction plate 36, the clutch cover 34 is coaxially and fixedly arranged on the front end face of the flywheel disc 38 through a bolt 37, the spring support ring 33 is fixed on the clutch cover 34, the diaphragm spring 32 is supported and arranged on the clutch cover 34 through the spring support ring 33, the front end of the diaphragm spring 32 is in contact connection with the release bearing 31, and the rear end of the diaphragm spring 32 is in contact connection with the pressure plate 35.
Further, one end of the planet carrier 5 is coaxially sleeved on the input shaft 2, and the other end of the planet carrier 5 is coaxially and fixedly connected with the output shaft 10; the planetary gears 8 are arranged on the planetary gear frame 5 in an empty sleeve mode, one side of each planetary gear 8 is meshed with the outer side of the sun gear 9, and the other side of each planetary gear 8 is meshed with the inner side of the gear ring 7.
The control method of the planetary wheel type two-gear gearbox based on the pawl type overrunning clutch comprises the following steps: a first gear forward control method, a second gear forward control method, a first gear reverse control method and a power interruption-free gear shifting control method;
the specific control process of the first gear forward control method is as follows:
when the vehicle advances at first gear, the clutch actuating mechanism controls the diaphragm spring clutch 3 to be in a separation state, meanwhile, the worm gear transmission mechanism in the clutch control mechanism drives the control ring 62 in the pawl overrunning clutch to rotate, so that the forward pawl 63 moves along the forward control window 622 and is clamped with the clamping groove of the outer circular surface of the gear ring 7, the reverse pawl 64 moves along the reverse control window 623 and is separated from the clamping groove of the outer circular surface of the gear ring 7, at the moment, the gear ring 7 is locked against rotation relative to the outer circular surface 61, the input shaft 2 rotates positively under the driving of the motor 1, the sun gear 9 coaxially fixedly connected to the input shaft 2 synchronously rotates positively, the sun gear 9 drives the planetary gear 8 to rotate reversely, the gear ring 7 generates a trend of reverse rotation along the axis, and the gear ring 7 is locked against the outer circular surface 61 and is fixed on the transmission housing 4, so that the planetary gear 8 rotates positively along the sun gear 9, the planetary gear 5 further drives the planetary carrier 5 to rotate positively, and finally, the power is output to realize forward output through the output shaft 10;
The specific control process of the second gear forward control method is as follows:
when the vehicle advances in second gear, the clutch actuating mechanism controls the diaphragm spring clutch 3 to be in a combined state, meanwhile, the worm gear transmission mechanism in the clutch control mechanism drives the control ring 62 in the pawl overrunning clutch to rotate, so that the forward pawl 63 moves along the forward control window 622 and is separated from the clamping groove of the outer circular surface of the gear ring 7, the reverse pawl 64 moves along the reverse control window 623 and is separated from the clamping groove of the outer circular surface of the gear ring 7, at the moment, the gear ring 7 rotates freely in two directions relative to the outer ring 61, the input shaft 2 rotates positively under the driving of the motor 1, on one hand, the sun gear 9 coaxially fixedly connected to the input shaft 2 rotates positively synchronously, on the other hand, the gear ring 7 also rotates positively synchronously with the input shaft 2 under the combined driving of the diaphragm spring clutch 3, at the moment, the planetary gear transmission mechanism rotates positively, the planetary carrier 5 drives the output shaft 10 to rotate positively synchronously, and finally power is output outwards through the output shaft 10 to realize second gear forward;
the specific control process of the first-gear reversing control method is as follows:
when the vehicle backs up in a first gear, the clutch actuating mechanism controls the diaphragm spring clutch 3 to be in a separation state, meanwhile, the worm gear transmission mechanism in the clutch control mechanism drives the control ring 62 in the pawl overrunning clutch to rotate, so that the forward pawl 63 moves along the forward control window 622 and is clamped with the clamping groove of the outer circular surface of the gear ring 7, the reverse pawl 64 moves along the reverse control window 623 and is clamped with the clamping groove of the outer circular surface of the gear ring 7, at the moment, the gear ring 7 is locked in a bidirectional rotation way relative to the outer ring 61, the input shaft 2 rotates reversely under the driving of the motor 1, the sun gear 9 coaxially fixedly connected to the input shaft 2 rotates reversely synchronously, the sun gear 9 drives the planet gears 8 to rotate positively, the gear ring 7 generates a tendency of rotating positively along the axis, and the gear ring 7 is relatively locked with the outer ring 61 at the moment, the outer ring 61 is fixed on the transmission housing 4, at the moment, the gear ring 7 is fixed, according to the transmission characteristics of the planetary gear transmission mechanism, the planet gears 8 reversely revolve along the sun gear 9, the planet carrier 5 is driven to rotate reversely, the output shaft 10 is driven to rotate synchronously, and finally, and the output shaft 10 rotates reversely, and the reverse power is output outwards through the reverse gear 10 is realized;
The power interruption-free gear shifting control method comprises a first gear up-shift and second gear down-shift control process and a second gear down-shift control process;
the first gear up-shift and second gear up-shift control process specifically comprises the following steps:
during first gear and second gear, the clutch actuating mechanism controls the diaphragm spring clutch 3 to be combined gradually, and meanwhile, the worm gear transmission mechanism in the clutch control mechanism drives the control ring 62 in the pawl overrunning clutch to rotate, so that the forward pawl 63 moves along the forward control window 622, the forward pawl 63 gradually moves from being clamped with the clamping groove on the outer circumferential surface of the gear ring 7 to being separated from the clamping groove on the outer circumferential surface of the gear ring 7, and the reverse pawl 64 moves along the reverse control window 623 and keeps being separated from the clamping groove on the outer circumferential surface of the gear ring 7; in the process, the power transmitted to the gear ring 7 by the input shaft 2 through the diaphragm spring clutch 3 is gradually increased, along with the combination, the power input by the input shaft 2 is transmitted from the sun gear 9 when the gear advances, the power is gradually transferred to the gear ring 7 and the sun gear 9 when the gear advances, along with the gradual increase of the rotating speed of the planet carrier 5, the revolution speed of the planet wheel 8 is gradually the same as the rotating speed of the sun gear 9 under the driving of the planet carrier 5, so that the meshing force between the planet wheel 8 and the sun gear 9 is reduced, the power transmitted to the planet wheel 8 by the sun gear 9 is reduced, the rotating speed of the planet wheel 8 along the axis of the planet wheel is gradually reduced to zero, at the moment, the positive pawl 63 and the reverse pawl 64 in the pawl overrunning clutch are separated from the clamping groove on the outer circumferential surface of the gear ring 7, the gear ring 7 can rotate freely relative to the outer ring 61, at the moment, the whole planetary transmission mechanism rotates in the positive direction, so that the gear ring 7 rotates in the positive direction, after the power is input through the input shaft 2, the power is transmitted to the carrier 5 through the diaphragm spring clutch 7, and finally the power is transmitted to the planet carrier 5, the output shaft 10, and finally the rotating power is output to the output shaft 10, and the gear output is up to the gear 10 is realized.
The two-gear and one-gear control process specifically comprises the following steps:
during the second gear down-shifting, the clutch executing mechanism controls the diaphragm spring clutch 3 to gradually separate, and at the same time, the worm gear transmission mechanism in the clutch controlling mechanism drives the control ring 62 in the pawl overrunning clutch to reversely rotate, so that the forward pawl 63 moves along the forward control window 622, the forward pawl 63 gradually moves from being separated from the clamping groove on the outer circumferential surface of the gear ring 7 to be clamped with the clamping groove on the outer circumferential surface of the gear ring 7, and the reverse pawl 64 moves along the reverse control window 623 and keeps being separated from the clamping groove on the outer circumferential surface of the gear ring 7 until the gear ring 7 freely rotates in the forward direction relative to the outer ring 61 and is reversely locked; in the process, the power transmitted by the input shaft 2 to the gear ring 7 through the diaphragm spring clutch 3 is gradually reduced, the power of the planet carrier 5 is gradually smaller than the resistance applied by the power, the rotating speed of the planet carrier 5 is gradually reduced, the power input by the input shaft 2 is transmitted downwards from the planet carrier 5 when advancing from the second gear, the power is transmitted downwards from the sun gear 9 when gradually transferring to the first gear, the planet gear 8 starts to resume reverse rotation along the axis of the planet carrier 5 along with the gradual reduction of the rotating speed of the planet carrier 5, the meshing force between the sun gear 9 and the planet gear 8 is gradually increased, the power starts to be transmitted downwards from the planet gear 8, meanwhile, the rotating speed of the gear ring 7 is gradually reduced until reverse rotation is locked, the power is sequentially transmitted to the output shaft 10 through the sun gear 9, the planet gear 8 and the planet carrier 5 after being input through the input shaft 2, and the final power is output outwards through the output shaft 10 to realize the second gear down-first gear.
Compared with the prior art, the invention has the beneficial effects that:
1. in the planetary wheel type two-gear gearbox based on the pawl type overrunning clutch, the pawl type overrunning clutch is adopted, so that a larger load can be borne, and larger power transmission is realized;
2. in the planetary wheel type two-gear gearbox based on the pawl type overrunning clutch, a planetary wheel type transmission structure is adopted, the pawl type overrunning clutch is matched, the transmission process is smoother without power interruption, and the gear shifting effect is further improved;
3. in the planetary wheel type two-gear gearbox based on the pawl type overrunning clutch, the adopted pawl type overrunning clutch can effectively reduce abrasion, and the working process is more accurate and reliable;
4. in the planetary wheel type two-gear gearbox based on the pawl type overrunning clutch, the pawl type overrunning clutch is adopted to drive the pawl to lift through the control window on the control ring, so that the pawl lifting process is more stable, the position is more accurate, and the clutch is placed to generate noise.
4. In the planetary wheel type two-gear gearbox based on the pawl type overrunning clutch, the worm and gear type control mechanism is adopted to control the rotation of the control ring of the clutch, so that the transmission ratio is increased, the control is more accurate, the self-locking effect is realized, and the position of the control ring is prevented from moving.
Drawings
FIG. 1 is a schematic illustration of a planetary two-speed transmission of the present invention in a first-speed condition;
FIG. 2 is a schematic diagram of a planetary two-speed gearbox according to the present invention in a second-speed condition;
FIG. 3 is a schematic diagram of a diaphragm spring clutch in a planetary two-speed transmission according to the present invention;
FIG. 4 is a front view of a pawl type overrunning clutch assembly in a planetary gear type two-speed gearbox according to the present invention;
FIG. 5 is a top view of a pawl type overrunning clutch assembly in a planetary gear type two speed transmission according to the present invention;
FIG. 6 is an exploded view of a pawl type overrunning clutch in a planetary two-speed transmission according to the present invention;
FIG. 7 is a schematic diagram of the control ring structure of the pawl type overrunning clutch in the planetary gear type two-gear transmission of the present invention;
FIG. 8 is a schematic diagram of a two-way lockup state of a pawl overrunning clutch in a planetary gear type two-speed transmission according to the present invention;
FIG. 9 is a schematic diagram of a one-way overrunning condition of a pawl overrunning clutch in a planetary gear type two-speed gearbox according to the present invention;
FIG. 10 is a schematic diagram of a two-way overrunning condition of a pawl overrunning clutch in a planetary gear type two-speed gearbox according to the present invention;
In the figure:
1 a driving motor, 2 an input shaft, 3 a diaphragm spring clutch, 4 a gearbox housing,
5 planetary frame, 6 pawl overrunning clutch assembly, 7 gear ring, 8 planetary wheel,
9 sun gear, 10 output shaft;
31 release bearing, 32 diaphragm spring, 33 spring support ring, 34 clutch housing
35 pressure plate, 36 friction plate, 37 bolt, 38 flywheel disc,
39 splines;
61 outer race, 62 control ring, 63 forward pawl, 64 reverse pawl,
65 control motor, 66 drive shaft, 67 worm, 68 sensor,
69 worm gear;
621 control ring body, 622 forward control window, 623 reverse control window, 624 forward control window ramp,
625 forward control window plane, 626 reverse control window plane, 627 reverse control window ramp, 628 worm gear connection plate.
Detailed Description
For a clear and complete description of the technical scheme and the specific working process thereof, the following specific embodiments of the invention are provided with reference to the accompanying drawings in the specification:
as shown in figure 1, the invention discloses a planetary two-gear gearbox based on a pawl type overrunning clutch, which comprises an input shaft 2, a diaphragm spring clutch 3, a gearbox housing 4, a planet carrier 5, a pawl type overrunning clutch assembly 6,
The gear ring 7, the planet wheel 8, the sun wheel 9 and the output wheel 10. One end of the input shaft 2 is coaxially and fixedly connected with the output end of the driving motor 1, and the other end of the input shaft 2 penetrates through the gearbox housing 4 and is coaxially and fixedly connected with the sun gear 9 in the gearbox housing 4; the diaphragm spring clutch 3 is coaxially arranged on the input shaft 2, wherein a friction plate 36 in the diaphragm spring clutch 3 is coaxially fixedly connected with the input shaft 2, and a connecting end of a flywheel disc 37 in the diaphragm spring clutch 3 is sleeved on the input shaft 2 and coaxially fixedly connected with a gear ring 7 in the gearbox housing 4; one end of the planet carrier 5 is coaxially sleeved on the input shaft 2, and the other end of the planet carrier 5 is coaxially and fixedly connected with the output shaft 10; the planetary gear 8 is arranged on the planetary gear frame 5 in an empty sleeve manner, one side of the planetary gear 8 is meshed with the outer side of the sun gear 9, and the other side of the planetary gear 8 is meshed with the inner side of the gear ring 7; the planet carrier 5, the gear ring 7, the planet gears 8 and the sun gear 9 form a planet wheel type transmission mechanism; in the pawl type overrunning clutch assembly 6, the outer ring of the pawl type overrunning clutch is fixed on the inner side wall of the gearbox housing 4, the inner ring of the pawl type overrunning clutch is coaxially arranged on the outer side wall of the gear ring 7 and is fixedly connected with the gear ring to form an integral structure, and therefore the inner ring of the pawl type overrunning clutch is the gear ring 7.
As shown in fig. 1 and 3, the diaphragm spring clutch 3 is composed of a release bearing 31, a diaphragm spring 32, a spring support ring 33, a clutch cover 34, a pressure plate 35, a friction plate 36 and a flywheel disk 38 which are arranged in this order from front to back. The flywheel disc 38 is coaxially connected with the connecting end of the gear ring 7 through a spline 39, the friction plate 36 is coaxially and fixedly connected to the input shaft 2, the pressure plate 35 is coaxially arranged at the front end of the friction plate 36, the clutch cover 34 is covered on the outer sides of the pressure plate 35 and the friction plate 36, the clutch cover 34 is coaxially and fixedly arranged on the front end face of the flywheel disc 38 through a bolt 37, the spring support ring 33 is fixed on the clutch cover 34, the diaphragm spring 32 is supported and arranged on the clutch cover 34 through the spring support ring 33, the front end of the diaphragm spring 32 is in contact connection with the release bearing 31, and the rear end of the diaphragm spring 32 is in contact connection with the pressure plate 35.
The diaphragm spring clutch 3 has two operating states:
1. when the release bearing 31 moves axially and backwardly along the input shaft 2 under the action of external force, the release finger end of the diaphragm spring 32 moves backwardly along the axial direction of the input shaft 2 under the pushing action of the release bearing 31, so that the diaphragm spring 32 is gradually compressed, the pressure plate end of the diaphragm spring 32 drives the pressure plate 35 to be far away from the surface of the friction plate 36 under the supporting action of the spring supporting ring 33, the pressure plate 35 is separated from the friction plate 36, the flywheel disc 38 is also separated from the friction plate 36, no torque is transmitted between the friction plate 36 and the clutch flywheel disc 38, and at the moment, the diaphragm spring clutch 3 is in a separated state.
2. When the release bearing 31 moves forward axially along the input shaft 2 under the action of external force, the diaphragm spring 32 moves forward axially along the input shaft 2 under the action of restoring force, so that the diaphragm spring 32 gradually extends, and under the supporting action of the spring supporting ring 33, the pressure plate end of the diaphragm spring 32 drives the pressure plate 35 to press the friction plate 36 on the flywheel disc 38, so that torque is transmitted between the friction plate 36 and the flywheel disc 38, and the diaphragm spring clutch 3 is in a combined state.
The pawl type overrunning clutch assembly 6 consists of a pawl type overrunning clutch and a clutch control mechanism.
As shown in fig. 4 and 6, the pawl overrunning clutch includes: an outer race 61, a control ring 62, a forward pawl 63, a reverse pawl 64, and a ring gear 7 (inner race); wherein, the gear ring 7 is coaxially arranged at the inner side of the outer ring 61, the forward pawl 63 and the reverse pawl 64 are arranged in an annular gap between the outer ring 61 and the gear ring 7, the control ring 62 is arranged at the axial outer side of the gear ring 7 and is connected with the forward pawl 63 and the reverse pawl 64 in a matched manner so as to control the forward pawl 63 and the reverse pawl 64 to swing up and down, and the two axial ends of the outer ring 61 are respectively provided with a clamp spring so as to realize axial limiting of components in the outer ring 61.
As shown in fig. 6 and 8, the forward pawl 63 and the reverse pawl 64 are installed in pairs between the outer ring 61 and the ring gear 7, in this embodiment, six pairs of the forward pawl 63 and the reverse pawl 64 are uniformly distributed in the annular space between the outer ring 61 and the ring gear 7, and the structures of the forward pawl 63 and the reverse pawl 64 are identical.
As shown in fig. 8, the forward pawl 63 and the reverse pawl 64 are mounted symmetrically with respect to the radial direction of the outer race 61 and the ring gear 7 such that the forward pawl 63 and the reverse pawl 64 are disposed reversely; wherein, the pawl root parts of the forward pawl 63 and the reverse pawl 64 are arranged in pawl mounting grooves on the inner side wall of the outer ring 61, and the pawl head parts of the forward pawl 63 and the reverse pawl 64 are matched and clamped with pawl clamping grooves on the outer circumference of the gear ring 7; a folded leaf spring is arranged between the forward pawl 63, the reverse pawl 64 and the inner side wall of the outer ring 61; the axial outer sides of the forward pawl 63 and the reverse pawl 64 are provided with pawl control pins which are slidably connected in a control window of the control ring 62, and swing control of the control ring 62 on the forward pawl 63 and the reverse pawl 64 is realized through cooperation of the control window and the pawl control pins.
As shown in fig. 7 and 8, the control ring main body 621 of the control ring 62 is an annular plate structure, six groups of control window pairs are opened on the control ring main body 621, the six groups of control window pairs are respectively in one-to-one correspondence with six groups of pawl pairs consisting of the forward pawl 63 and the reverse pawl 64, each group of control window pairs consists of a forward control window 622 and a reverse control window 623, the forward control window 622 is in matched connection with the pawl control pin of the forward pawl 63, and the reverse control window 623 is in matched connection with the pawl control pin of the reverse pawl 64; the cooperation connection of the control window and the pawl control pin means: the pawl control pin is inserted into the control window, is connected with the control surface at the bottom of the control window, and controls the pawl control pin to move through the control surface at the bottom of the control window in the process of propping against the control surface at the bottom of the control window, so that the pawl control pin is lifted, and further the corresponding pawl is controlled to swing up and down through the pawl control pin, therefore, the swinging mode of the pawl depends on the design of the control surface at the bottom of the control window, and the shape of the corresponding control surface can be designed according to the actual working condition to realize different working modes; in this embodiment, as shown in fig. 8, 9 and 10, the control ring 2 rotates clockwise relative to the forward pawl 63 and the reverse pawl 64 distributed in a ring shape, and further controls the corresponding pawl to swing through the pawl control pin, and correspondingly, the swinging modes of the forward pawl 63 and the reverse pawl 64 are designed as follows: first,: the forward pawl 5 and the reverse pawl 6 are both positioned at the initial positions of the corresponding control windows, namely the lowest positions; then: the forward pawl 5 is kept at the lowest position and the reverse pawl 6 is gradually lifted to the highest position, and at the moment, the forward pawl 5 and the reverse pawl 6 are positioned at the middle positions of the corresponding control windows; finally: the forward pawl 63 is gradually raised to the highest position and the reverse pawl 64 is maintained at the highest position, at which time both the forward pawl 63 and the reverse pawl 64 are in the end positions of the corresponding control windows. The structure of the control window on the control ring is as follows:
As shown in fig. 7, the control ring main body 621 of the control ring 62 is provided with six groups of control window pairs, the six groups of control window pairs are respectively in one-to-one correspondence with six groups of pawl pairs formed by the forward pawl 63 and the reverse pawl 64, each group of control window pairs is formed by a forward control window 622 and a reverse control window 623, the forward control window 622 is in fit connection with the pawl control pin of the forward pawl 63, and the reverse control window 623 is in fit connection with the pawl control pin of the reverse pawl 64; the bottom control surface of the forward control window 622 includes a forward control window inclined surface 624 and a forward control window plane 625 which are sequentially arranged clockwise (i.e. in the same rotation direction as the control ring 62), the forward control window inclined surface 624 and the reverse control window plane 625 are continuous and unblocked, wherein the forward control window inclined surface 624 is an arc surface which is anticlockwise (i.e. opposite to the rotation direction of the control ring 2) and gradually away from the center position of the control ring 62, and the forward control window plane 625 is an arc surface which is concentrically arranged with the control ring 2; the bottom control surface of the reverse control window 623 comprises a reverse control window plane 626 and a reverse control window inclined surface 627 which are sequentially arranged clockwise (i.e. in the same direction as the rotation direction of the control ring 62), the reverse control window plane 626 and the reverse control window inclined surface 627 are continuous and unblocked, wherein the reverse control window plane 626 is an arc surface which is concentrically arranged with the control ring 62, and the reverse control window inclined surface 627 is an arc surface which is anticlockwise (i.e. opposite to the rotation direction of the control ring 62) and gradually away from the center position of the control ring 62. The forward control window bevel 624 is the same length as the reverse control window bevel 626, and the forward control window bevel 625 is the same length as the reverse control window bevel 627.
When the pawl control pin of the forward pawl 63 is inserted into the forward control window 622, the pawl control pin of the forward pawl 63 is always pressed against the control surface of the forward control window 622 under the action of the elastic force of the corresponding installed flap spring, and similarly, when the pawl control pin of the reverse pawl 64 is inserted into the reverse control window 623, the pawl control pin of the reverse pawl 64 is always pressed against the control surface of the reverse control window 623 under the action of the elastic force of the corresponding installed flap spring.
Furthermore, a worm gear plate 628 is provided radially outside the control ring 62 for fixedly mounting the worm gear 69 of the clutch control.
The pawl type overrunning clutch has three working states:
1. as shown in fig. 7 and 8, when the forward pawl 63 is located at the initial position of the forward control window 622 and the pawl control pin of the reverse pawl 64 is located at the initial position of the reverse control window 623, the pawl heads of the forward pawl 63 and the reverse pawl 64 are both at the lowest position and are respectively engaged with the pawl engaging grooves on the outer circumferential surface of the ring gear 7; since the forward pawl 63 and the reverse pawl 64 are disposed in opposite directions, the outer race 61 and the ring gear 7 are locked in both clockwise and counterclockwise directions, i.e., in both directions, under the clamping action of the forward pawl 63 and the reverse pawl 64, and the outer race 61 and the ring gear 7 can realize power transmission in both clockwise and counterclockwise directions.
2. As shown in fig. 7 and 9, as the control ring 62 rotates clockwise, the pawl control pin of the forward pawl 63 moves under the action of the forward control window plane 625 of the control ring 62, and since the forward control window plane 625 is disposed coaxially with the control ring 62, the pawl control pin of the forward pawl 63 does not move in the radial direction of the control ring 62, so that the forward pawl 63 is always kept at the lowest position (i.e., the position closest to the center of the control ring 62), and at the same time, the pawl control pin of the reverse pawl 64 moves under the action of the reverse control window inclined plane 627 of the control ring 62, and since the reverse control window inclined plane 627 gradually moves away from the center of the control ring 62 in the counterclockwise direction, the pawl control pin of the reverse pawl 64 gradually moves away from the center of the control ring 62 in the radial direction of the control ring 62, and the pawl control pin of the reverse pawl 64 gradually lifts under the action of the pawl control pin of the reverse pawl 64; when the pawl control pin of the forward pawl 63 is located at the junction of the forward control window plane 206 and the forward control window inclined plane, i.e., at the middle position of the forward control window 622, the forward pawl 63 is still at the lowest position, i.e., the forward pawl 63 still keeps clamping with the pawl clamping groove on the outer circumferential surface of the gear ring 7, and when the pawl control pin of the reverse pawl 64 is located at the junction of the reverse control window inclined plane 627 and the reverse control window plane 626, i.e., at the middle position of the reverse control window 623, the reverse pawl 64 is raised to the highest position (i.e., at the position farthest from the center of the control ring), i.e., the reverse pawl 64 is separated from the pawl clamping groove on the outer circumferential surface of the gear ring 7; at this time, the ring gear 7 is locked in the clockwise direction with respect to the outer ring 61 and is relatively freely rotatable in the counterclockwise direction, and at this time, the clockwise rotation of the ring gear 7 with respect to the outer ring 61 transmits power, while the counterclockwise rotation is unpowered, i.e., overrunning in one direction.
3. As shown in fig. 7 and 10, as the control ring 62 rotates clockwise, the pawl control pin of the forward pawl 63 starts to move under the action of the forward control window inclined plane 624 of the control ring 62, and as the forward control window inclined plane 624 gradually moves away from the center of the control ring 62 in the counterclockwise direction, the pawl control pin of the forward pawl 63 gradually moves away from the center of the control ring 62 in the radial direction of the control ring 62 as the control ring 62 continues to rotate clockwise, and the forward pawl 63 gradually rises under the drive of the pawl control pin of the forward pawl 63 until the pawl control pin moves to the leftmost end of the forward control window inclined plane 624, namely, the end position of the forward control window 622, at this time, the forward pawl 63 rises to the highest position (namely, the position farthest from the center of the control ring), and at this time, the forward pawl 63 is separated from the pawl clamping groove on the outer circumferential surface of the gear ring 7; meanwhile, the pawl control pin of the reverse pawl 64 moves to the end position of the forward control window 622 under the action of the reverse control window plane 626 of the control ring 62, and the pawl control pin of the reverse pawl 64 does not move along the radial direction of the control ring 62 because the reverse control window plane 626 and the control ring 62 are coaxially arranged, and the reverse pawl 64 is kept at the highest position, namely, at the moment, both the forward pawl 63 and the reverse pawl 64 are separated from the pawl clamping groove on the outer circumferential surface of the gear ring 7; at this time, since the forward pawl 63 and the reverse pawl 64 are disengaged from the pawl catch groove on the outer circumferential surface of the ring gear 7, the ring gear 7 can freely rotate in both the clockwise and counterclockwise directions relative to the outer ring 61, and no power is transmitted between the ring gear 7 and the outer ring 61 in both the clockwise and counterclockwise directions, i.e., the two-way overrunning.
As shown in fig. 4 and 5, the clutch control mechanism is composed of a control motor 65, a transmission shaft 66, a worm 67, a sensor 68, and a worm wheel 69; the output end of the control motor 65 is fixedly connected with one end of the transmission shaft 66 coaxially, the worm 67 is fixed on the shaft diameter of the transmission shaft 66 coaxially, the sensor 68 is arranged and installed at the other end of the transmission shaft 66, and the rotation angle of the transmission shaft 66 is detected through the sensor 68, so that the rotation angle of the worm 67 is obtained; the worm wheel 69 is coaxially arranged on the radial outer side of the control ring 62 through the worm wheel connecting plate 28, and the worm wheel 69 is meshed with the worm 67 to form a worm wheel and worm transmission pair.
Under the drive of the control motor 65, the worm 67 synchronously rotates along with the transmission shaft 66 and drives the worm wheel 69 fixedly connected with the control ring 62 to rotate, the control ring 62 rotationally controls the corresponding forward pawl 63 and the corresponding reverse pawl 64 to swing up and down, so that the control of the pawl type overrunning clutch is realized, in the process, the sensor 68 detects the rotation angle of the worm 67, the rotation angle of the worm wheel 69 driving the control ring 62 is judged, the movement positions of pawl control pins of the forward pawl 63 and the reverse pawl 64 on corresponding control surfaces are judged, and finally, the accurate control of the locking or overrunning of the clutch is realized.
According to the specific composition structure of the planetary gear type two-gear gearbox based on the pawl overrunning clutch, the invention also discloses a control method of the planetary gear type two-gear gearbox based on the pawl overrunning clutch, which comprises the following steps: a first gear forward control method, a second gear forward control method, a first gear reverse control method and a power interruption-free gear shifting control method.
1. The specific control process of the first gear forward control method is as follows:
when the vehicle advances at first gear, the clutch actuating mechanism controls the diaphragm spring clutch 3 to be in a separation state, at the same time, a clutch control mechanism in the pawl overrunning clutch assembly is started, a worm gear transmission mechanism in the clutch control mechanism drives a control ring 62 in the pawl overrunning clutch to rotate, forward pawls 63 move along a forward control window 622 and keep clamping connection with clamping grooves on the outer circumferential surface of the gear ring 7, reverse pawls 64 move along a reverse control window 623 and are separated from clamping grooves on the outer circumferential surface of the gear ring 7, at the moment, the clutch control mechanism stops running, at the moment, the gear ring 7 rotates and locks in a reverse direction (namely clockwise direction in fig. 8) relative to the outer ring 61, at the moment, the input shaft 2 rotates positively under the drive of the motor 1, a sun gear 9 coaxially and fixedly connected to the input shaft 2 rotates positively, the sun gear 9 drives a planetary gear 8 to rotate reversely, so that the gear ring 7 generates a trend of rotating reversely along an axis, at the moment, and the gear ring 7 is relatively locked with the outer ring 61, and is fixed on the gear housing 4, at the moment, the gear ring 7 is fixed on the reverse control window 623 and is separated from the clamping grooves on the outer circumferential surface of the gear 7, at the moment, the gear ring 7 is fixed, the gear ring is rotated reversely, the sun gear 7 rotates reversely, namely clockwise direction relative to the sun gear 9, and rotates synchronously, and drives the planetary carrier 5, and further rotates forward rotation, and further rotates along the planetary carrier 5, and rotates forward rotation, and further rotates, forward carrier 10, forward rotation, and further rotates, forward carrier, and finally, the planetary carrier rotates, forward carrier, and rotates, according to the planetary carrier, forward rotation, and rotates;
2. The specific control process of the second gear forward control method is as follows:
when the vehicle advances in second gear, the clutch actuator controls the diaphragm spring clutch 3 to be in a combined state, at the same time, the clutch control mechanism in the pawl overrunning clutch assembly is started, the worm gear transmission mechanism in the clutch control mechanism drives the control ring 62 in the pawl overrunning clutch to rotate, so that the forward pawl 63 moves along the forward control window 622 and is separated from the clamping groove on the outer circumferential surface of the gear ring 7, the reverse pawl 64 moves along the reverse control window 623 and is separated from the clamping groove on the outer circumferential surface of the gear ring 7, at the moment, the clutch control mechanism stops running, as shown in fig. 10, at the moment, the gear ring 7 can freely rotate bidirectionally relative to the outer ring 61, and the input shaft 2 rotates positively under the drive of the motor 1, on the one hand: the sun gear 9 coaxially and fixedly connected to the input shaft 2 synchronously rotates in the forward direction, and on the other hand: under the combined drive of the diaphragm spring clutch 3, the gear ring 7 and the input shaft 2 synchronously rotate in the forward direction, so that at the moment, the whole planetary wheel type transmission mechanism consisting of the planetary frame 5, the gear ring 7, the planetary wheels 8 and the sun wheel 9 rotates in the forward direction, the planetary frame 5 drives the output shaft 10 to synchronously rotate in the forward direction, and finally, power is output outwards through the output shaft 10 to realize secondary forward;
3. The specific control process of the first-gear reversing control method is as follows:
when the vehicle is in a reverse state, the clutch actuating mechanism controls the diaphragm spring clutch 3 to be in a separation state, and at the same time, the clutch control mechanism in the pawl type overrunning clutch assembly is started, the worm gear transmission mechanism in the clutch control mechanism drives the control ring 62 in the pawl type overrunning clutch to rotate, so that the forward pawl 63 moves along the forward control window 622 and keeps clamping with the clamping groove on the outer circumferential surface of the gear ring 7, the reverse pawl 64 moves along the reverse control window 623 and keeps clamping with the clamping groove on the outer circumferential surface of the gear ring 7, at the moment, the clutch control mechanism stops running, as shown in figure 8, and at the moment, the gear ring 7 is locked in bidirectional rotation relative to the outer ring 61, the input shaft 2 reversely rotates under the drive of the motor 1, the sun gear 9 coaxially and fixedly connected to the input shaft 2 synchronously reversely rotates, the sun gear 9 drives the planet gears 8 to reversely rotate, so that the gear ring 7 generates a trend of forward rotation along an axis, the gear ring 7 and the outer ring 61 are relatively locked at the moment, the outer ring 61 is fixed on the gearbox shell 4, the gear ring 7 is fixed at the moment, the planet gears 8 reversely revolve along the sun gear 9 at the moment according to the transmission characteristic of a planetary gear transmission mechanism, the planet gears 5 are driven to reversely rotate, the planet gears 5 further drive the output shafts 10 to synchronously reversely rotate, and finally, the power is output outwards through the output shafts 10 to realize one-gear reversing;
4. The power interruption-free gear shifting control method comprises a first gear up-shift and second gear down-shift control process and a second gear down-shift control process;
1. the first gear up-shift and second gear up-shift control process specifically comprises the following steps:
during first gear and second gear, the clutch actuating mechanism controls the diaphragm spring clutch 3 to be combined gradually, meanwhile, the clutch control mechanism in the pawl type overrunning clutch assembly is started, the worm gear transmission mechanism in the clutch control mechanism drives the control ring 62 in the pawl type overrunning clutch to rotate, so that the forward pawl 63 moves along the forward control window 622, the forward pawl 63 moves gradually from being clamped with the clamping groove on the outer circumferential surface of the gear ring 7 to being separated from the clamping groove on the outer circumferential surface of the gear ring 7, and the reverse pawl 64 moves along the reverse control window 623 and keeps being separated from the clamping groove on the outer circumferential surface of the gear ring 7; in the process, the power transmitted to the gear ring 7 by the input shaft 2 through the diaphragm spring clutch 3 is gradually increased, along with the combination, the power input by the input shaft 2 is transmitted from the sun gear 9 when the gear advances, the power is gradually transferred to the gear ring 7 and the sun gear 9 when the gear advances, along with the gradual increase of the rotating speed of the planet carrier 5, the revolution speed of the planet wheel 8 is gradually the same as the rotating speed of the sun gear 9 under the driving of the planet carrier 5, so that the meshing force between the planet wheel 8 and the sun gear 9 is reduced, the power transmitted to the planet wheel 8 by the sun gear 9 is reduced, the rotating speed of the planet wheel 8 along the axis of the planet wheel is gradually reduced to zero, at the moment, the forward pawl 63 and the reverse pawl 64 in the pawl overrunning clutch are separated from the clamping groove on the outer circumferential surface of the gear ring 7, the gear ring 7 can freely rotate relative to the outer ring 61, at the moment, the whole planetary transmission mechanism rotates in the forward direction, so that the gear ring 7 rotates in the forward direction, after the power is input through the input shaft 2, the power is transmitted to the planet carrier 5 through the diaphragm spring clutch 3, and then transmitted to the output shaft 5 to the output shaft 10, and finally the power is transmitted to the output shaft 10, and the power is output to the gear 10 is in the first gear, and the power is in the second gear has no interruption;
2. The two-gear and one-gear control process specifically comprises the following steps:
during the second gear down-shifting, the clutch actuating mechanism controls the diaphragm spring clutch 3 to be gradually separated, meanwhile, a clutch control mechanism in the pawl type overrunning clutch assembly is started, a worm gear transmission mechanism in the clutch control mechanism drives a control ring 62 in the pawl type overrunning clutch to rotate reversely, so that a forward pawl 63 moves along a forward control window 622, the forward pawl 63 is gradually moved from being separated from a clamping groove on the outer circumferential surface of the gear ring 7 to be clamped with the clamping groove on the outer circumferential surface of the gear ring 7, a reverse pawl 64 moves along a reverse control window 623 and keeps being separated from the clamping groove on the outer circumferential surface of the gear ring 7 until the gear ring 7 rotates freely relative to the outer ring 61 in the forward direction (anticlockwise direction in the figure) and is locked reversely; in the process, the power transmitted by the input shaft 2 to the gear ring 7 through the diaphragm spring clutch 3 is gradually reduced, the power of the planet carrier 5 is gradually smaller than the resistance applied by the planetary carrier 5, the rotating speed of the planet carrier 5 is gradually reduced, the power input by the input shaft 2 is transmitted downwards from the planet carrier 5 when advancing from the second gear, namely, the power is gradually transmitted downwards from the sun gear 9 when gradually transferring to the first gear, namely, the power is gradually transferred to the sun gear 9 from the planet carrier 5, the rotating speed of the planet carrier 5 gradually reduces, the meshing force between the sun gear 9 and the planet gear 8 is gradually increased, the power starts to be transmitted downwards from the planet gear 8 in the planetary transmission mechanism, meanwhile, the rotating speed of the gear ring 7 is gradually reduced until the reverse rotation is locked, the power is sequentially transmitted to the output shaft 10 through the sun gear 9, the planet gear 8 and the planet carrier 5 after being input by the input shaft 2, and finally the power is output outwards through the output shaft 10 to realize the first gear advancing, namely, the process of the second gear and the first gear is realized, and the whole gear upshifting process is not interrupted.

Claims (7)

1. Planetary wheel type two keeps off gearbox based on pawl formula overrunning clutch includes: input shaft (2), diaphragm spring clutch (3), planetary gear drive mechanism, overrunning clutch assembly and output shaft (10), wherein, planetary gear drive mechanism comprises planet carrier (5), ring gear (7), planet wheel (8) and sun gear (9), its characterized in that:
the diaphragm spring clutch (3) is arranged on an input shaft (2) coaxially and fixedly connected with the sun gear (9), a flywheel disc (38) of the diaphragm spring clutch (3) is coaxially connected with the gear ring (7), and the output shaft (10) is coaxially connected with the planet carrier (5);
the overrunning clutch assembly is a pawl overrunning clutch assembly (6) and consists of a pawl overrunning clutch and a clutch control mechanism;
the pawl type overrunning clutch consists of an outer ring (61), a control ring (62), a forward pawl (63), a reverse pawl (64) and an inner ring, wherein the outer ring (61) is fixed on a gearbox shell (4), the inner ring is positioned on the outer side of a gear ring (7) and is integrally arranged with the gear ring (7), the forward pawl (63) and the reverse pawl (64) are uniformly arranged in an annular space between the outer ring (61) and the inner ring in pairs, pawl roots of the forward pawl (63) and the reverse pawl (64) are rotatably arranged on the outer ring (61), pawl heads of the forward pawl (63) and the reverse pawl (64) are oppositely arranged and are clamped with pawl clamping grooves on the outer ring outer circular surface, a folded sheet spring is arranged between the forward pawl (63) and the reverse pawl (64) and the outer ring (61), the forward pawl (63) and the reverse pawl (64) are respectively connected with a forward control window (622) and a reverse control window (623) on the control ring (62) in a sliding mode through control pin arranged on the axial side surfaces of the control ring, and the forward pawl (63) and the reverse pawl (64) are clamped with the outer ring (64) or the reverse pawl (64) in a bidirectional locking mode, and the forward pawl (63) and the reverse pawl (64) and the outer ring (61) are further clamped with the outer ring (61) or the reverse pawl (61) in a bidirectional locking mode is achieved;
The clutch control mechanism consists of a control motor (65), a transmission shaft (66), a worm (57), a sensor (68) and a worm wheel (69), wherein the control motor (65) is coaxially and fixedly connected with one end of the transmission shaft (66), the sensor (68) is arranged at the other end of the transmission shaft (66), the worm (57) is coaxially arranged on the transmission shaft (66) and is meshed with the worm wheel (69) coaxially fixed on the outer circumference of the control ring (62), and the control ring (62) is further controlled to rotate.
2. The pawl-type overrunning clutch-based planetary two-speed gearbox of claim 1, wherein:
on the control ring (62), the control surface at the bottom of the forward control window (622) is a forward control window inclined surface (624) and a forward control window plane (625) which are sequentially and continuously arranged along the rotation direction of the control ring (62), the control surface at the bottom of the reverse control window (623) is a reverse control window plane (626) and a reverse control window inclined surface (627) which are sequentially and continuously arranged along the rotation direction of the control ring (62), wherein the forward control window inclined surface (624) and the reverse control window inclined surface (627) are curved surfaces which are gradually close to the center position of the control ring (62) along the rotation direction of the control ring (62), and the forward control window plane (625) and the reverse control window plane (626) are curved surfaces which are concentrically arranged with the control ring (62).
3. The pawl-type overrunning clutch-based planetary two-speed gearbox of claim 1, wherein:
a plurality of pawl clamping groove pairs are uniformly formed in the outer circular surface of the inner ring along the circumferential direction, each group of clamping groove pairs consists of two pawl clamping grooves, the two pawl clamping grooves are respectively matched with the pawl heads of the forward pawl (63) and the reverse pawl (64), and when the clamping grooves of the inner ring rotate to any one group of pawl pairs, the forward pawl (63) and the reverse pawl (64) can find pawl clamping grooves matched and clamped with the pawl clamping grooves in the pawl clamping groove pairs corresponding to the outer circular surface of the inner ring.
4. The pawl-type overrunning clutch-based planetary two-speed gearbox of claim 1, wherein:
the inner side wall of the outer ring (61) is provided with a plurality of groups of pawl mounting grooves which are in one-to-one correspondence with the forward pawl (63) and the reverse pawl (64), and each pawl mounting groove in the pawl mounting groove pair is internally provided with a folded sheet spring mounting groove.
5. The pawl-type overrunning clutch-based planetary two-speed gearbox of claim 1, wherein:
the diaphragm spring clutch (3) is characterized in that a release bearing (31), a diaphragm spring (32), a spring support ring (33), a clutch cover (34), a pressure plate (35), a friction plate (36) and a flywheel disc (38) are sequentially arranged from front to back;
Flywheel dish (38) pass through the link coaxial coupling of spline (39) and ring gear (7), friction disc (36) coaxial fixed connection is on input shaft (2), pressure disk (35) coaxial setting is in the front end of friction disc (36), clutch housing (34) cover is put in pressure disk (35) and friction disc (36) outside, and clutch housing (34) pass through the coaxial fixed mounting of bolt (37) on the front end face of flywheel dish (38), spring support circle (33) are fixed on clutch housing (34), diaphragm spring (32) are installed on clutch housing (34) through spring support circle (33) support, diaphragm spring (32) front end and release bearing (31) contact link, diaphragm spring (32) rear end and pressure disk (35) contact link.
6. The pawl-type overrunning clutch-based planetary two-speed gearbox of claim 1, wherein:
one end of the planet carrier (5) is coaxially sleeved on the input shaft (2), and the other end of the planet carrier (5) is coaxially and fixedly connected with the output shaft (10); the planetary gear (8) is arranged on the planetary carrier (5) in an empty mode, one side of the planetary gear (8) is meshed with the outer side of the sun gear (9), and the other side of the planetary gear (8) is meshed with the inner side of the gear ring (7).
7. The control method of the planetary two-gear transmission based on the pawl overrunning clutch according to claim 1, wherein the control method comprises the following steps:
Comprising the following steps: a first gear forward control method, a second gear forward control method, a first gear reverse control method and a power interruption-free gear shifting control method;
the specific control process of the first gear forward control method is as follows:
when the vehicle advances at first gear, the clutch actuating mechanism controls the diaphragm spring clutch (3) to be in a separation state, meanwhile, the worm gear transmission mechanism in the clutch control mechanism drives the control ring (62) in the pawl overrunning clutch to rotate, so that the forward pawl (63) moves along the forward control window (622) and is clamped with the clamping groove on the outer circular surface of the gear ring (7), the reverse pawl (64) moves along the reverse control window (623) and is separated from the clamping groove on the outer circular surface of the gear ring (7), at the moment, the gear ring (7) is locked against rotation relative to the outer circular surface (61), the input shaft (2) is driven by the motor (1) to rotate forward, the sun gear (9) coaxially and fixedly connected to the input shaft (2) synchronously rotates forward, the sun gear (9) drives the planet gear (8) to rotate reversely, so that the gear ring (7) generates a trend of rotating reversely along the axis, and the gear ring (7) is relatively locked with the outer circular surface (61) while the gear ring (61) is fixed on the gear housing (4), at the moment, the gear ring (7) is fixed, the planet gear (8) is driven by the motor (1) to rotate forward synchronously, and the planet carrier (10) is driven by the output shaft (5) to rotate forward, and the output shaft (10) rotates forward synchronously;
The specific control process of the second gear forward control method is as follows:
when the vehicle advances in a second gear, the clutch actuating mechanism controls the diaphragm spring clutch (3) to be in a combined state, meanwhile, the worm gear transmission mechanism in the clutch control mechanism drives the control ring (62) in the pawl overrunning clutch to rotate, so that the forward pawl (63) moves along the forward control window (622) and is separated from the clamping groove on the outer circular surface of the gear ring (7), the reverse pawl (64) moves along the reverse control window (623) and is separated from the clamping groove on the outer circular surface of the gear ring (7), at the moment, the gear ring (7) rotates freely in two directions relative to the outer ring (61), the input shaft (2) rotates positively under the driving of the motor (1), on one hand, the sun gear (9) coaxially and fixedly connected to the input shaft (2) rotates positively synchronously, on the other hand, the gear ring (7) also rotates positively synchronously with the input shaft (2) under the combined driving of the diaphragm spring clutch (3), at the moment, the planetary transmission mechanism rotates positively, the planetary carrier (5) drives the output shaft (10) to rotate positively synchronously, and finally, the power is output outwards in a second gear through the output shaft (10);
the specific control process of the first-gear reversing control method is as follows:
when the vehicle is in a reverse state, the clutch actuating mechanism controls the diaphragm spring clutch (3) to be in a separation state, meanwhile, the worm gear transmission mechanism in the clutch control mechanism drives the control ring (62) in the pawl overrunning clutch to rotate, the forward pawl (63) moves along the forward control window (622) and is clamped with the clamping groove on the outer circular surface of the gear ring (7), the reverse pawl (64) moves along the reverse control window (623) and is clamped with the clamping groove on the outer circular surface of the gear ring (7), at the moment, the gear ring (7) is locked in a bidirectional rotation way relative to the outer circular surface (61), the input shaft (2) is driven by the motor (1) to rotate reversely, the sun gear (9) coaxially and fixedly connected to the input shaft (2) synchronously rotates reversely, the sun gear (9) drives the planet gear (8) to rotate positively, so that the gear ring (7) generates a trend of rotating positively along the axis, and the outer circular ring (7) is relatively locked with the outer circular ring (61) at the moment, the planet gear (61) is fixed on the transmission housing (4), at the moment, the planet gear (5) is driven by the non-rotating mechanism to rotate reversely according to the characteristics of the planet carrier (5) synchronously, and the planet carrier (5) is driven reversely rotates synchronously, the final power is output outwards through an output shaft (10) to realize one-gear reversing;
The power interruption-free gear shifting control method comprises a first gear up-shift and second gear down-shift control process and a second gear down-shift control process;
the first gear up-shift and second gear up-shift control process specifically comprises the following steps:
during first gear and second gear, the clutch actuating mechanism controls the diaphragm spring clutch (3) to be combined gradually, meanwhile, the worm gear transmission mechanism in the clutch control mechanism drives the control ring (62) in the pawl overrunning clutch to rotate, so that the forward pawl (63) moves along the forward control window (622), the forward pawl (63) moves gradually from being clamped with the clamping groove on the outer circumferential surface of the gear ring (7) to being separated from the clamping groove on the outer circumferential surface of the gear ring (7), and the reverse pawl (64) moves along the reverse control window (623) and keeps separated from the clamping groove on the outer circumferential surface of the gear ring (7); in the process, the power transmitted by the input shaft (2) to the gear ring (7) through the diaphragm spring clutch (3) is gradually increased, along with the combination, the power input by the input shaft (2) is transmitted by the sun gear (9) when the gear advances, the power is gradually transferred to the gear ring (7) and the sun gear (9) when the gear advances, along with the gradual increase of the rotating speed of the planet carrier (5), the revolution speed of the planet gear (8) is gradually the same as the rotating speed of the sun gear (9) under the driving of the planet carrier (5), so that the meshing force between the planet gear (8) and the sun gear (9) is reduced, the power transmitted by the sun gear (9) to the planet gear (8) is reduced, the rotating speed of the planet gear (8) along the axis of the planet gear is gradually reduced to zero, at the moment, the positive pawl (63) and the reverse pawl (64) in the pawl overrunning clutch are separated from the clamping groove on the outer circumferential surface of the gear ring (7), the gear ring (7) can rotate freely relative to the outer ring (61), the whole wheel type transmission mechanism rotates along the positive rotation direction (7) and the rotating direction, the power is transmitted to the output shaft (2) through the planet carrier (5) to the input shaft (10) through the diaphragm spring (7), the final power is output outwards through an output shaft (10) to realize first gear and second gear;
The two-gear and one-gear control process specifically comprises the following steps:
during the second gear down-shifting, the clutch executing mechanism controls the diaphragm spring clutch (3) to be gradually separated, meanwhile, the worm gear transmission mechanism in the clutch controlling mechanism drives the control ring (62) in the pawl overrunning clutch to rotate reversely, so that the forward pawl (63) moves along the forward control window (622), the forward pawl (63) moves gradually from being separated from the clamping groove on the outer circumferential surface of the gear ring (7) to be clamped with the clamping groove on the outer circumferential surface of the gear ring (7), the reverse pawl (64) moves along the reverse control window (623) and keeps being separated from the clamping groove on the outer circumferential surface of the gear ring (7) until the gear ring (7) rotates freely in the forward direction relative to the outer ring (61), and the reverse pawl is locked; in the process, the power transmitted by the input shaft (2) to the gear ring (7) through the diaphragm spring clutch (3) is gradually reduced, the power of the planet carrier (5) is gradually smaller than the resistance of the power, the rotating speed of the planet carrier (5) is gradually reduced, the power input by the input shaft (2) is transmitted downwards from the planet carrier (5) when the gear is advanced from the second gear, the power is gradually transferred downwards from the sun gear (9) when the gear is advanced to the first gear, the planet gear (8) starts to recover the reverse rotation along the axis along with the gradual reduction of the rotating speed of the planet carrier (5), the meshing force between the sun gear (9) and the planet gear (8) is gradually increased, the power starts to be transmitted downwards from the planet gear (8), meanwhile, the rotating speed of the gear ring (7) is gradually reduced until the reverse rotation is locked, the power is transmitted downwards from the planet carrier (5) to the output shaft (10) when the gear is advanced from the second gear, and finally the power is output outwards through the output shaft (10) to realize the second gear and the first gear.
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