CN211259510U - Planet row type three-gear gearbox - Google Patents

Planet row type three-gear gearbox Download PDF

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Publication number
CN211259510U
CN211259510U CN201921839636.XU CN201921839636U CN211259510U CN 211259510 U CN211259510 U CN 211259510U CN 201921839636 U CN201921839636 U CN 201921839636U CN 211259510 U CN211259510 U CN 211259510U
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China
Prior art keywords
gear
spring
brake
piston
shell
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CN201921839636.XU
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Chinese (zh)
Inventor
辜建军
曾为华
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Hunan Yipu Automobile Technology Co ltd
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Hunan Yipu Automobile Technology Co ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by 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
    • 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
    • F16H3/78—Special adaptation of synchronisation mechanisms to these gearings
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
    • F16H63/3026—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes
    • 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
    • F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means
    • 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
    • F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches
    • 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
    • F16H2716/00—Control devices for speed-change mechanisms of planetary gearings, with toothed wheels remaining engaged, e.g. also for devices to simplify the control or for synchronising devices combined with control devices
    • F16H2716/04—Control devices for speed-change mechanisms of planetary gearings, with toothed wheels remaining engaged, e.g. also for devices to simplify the control or for synchronising devices combined with control devices the control being hydraulic or pneumatic

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The utility model relates to the technical field of motor vehicle gear shifting, in particular to a planetary gear-shifting type three-gear transmission, which comprises a first brake gear shifting mechanism, a second brake gear shifting mechanism, a clutch gear shifting mechanism and a gear transmission mechanism; the first brake gear shifting mechanism and the second brake gear shifting mechanism share the same brake sliding sleeve; the clutch gear shifting mechanism comprises a clutch and a clutch sliding sleeve; the gear transmission mechanism comprises a gear ring and a sun wheel seat; in the first stopper gearshift, braking sliding sleeve outer tooth and shell internal tooth sliding connection, braking sliding sleeve inner tooth can be connected with the sun gear seat, and in the second stopper gearshift, braking sliding sleeve outer tooth and casing internal tooth sliding connection, braking sliding sleeve inner tooth can be connected with the ring gear, and separation and reunion sliding sleeve inner tooth and hydro-cylinder outer tooth sliding connection can be connected with the sun gear seat. The planetary gear type three-gear transmission has a wider transmission range, and the performance of the whole vehicle is improved by utilizing the automatic switching of three speed ratios of the transmission.

Description

Planet row type three-gear gearbox
Technical Field
The utility model relates to a motor vehicle technical field that shifts especially relates to a planet row formula three-gear gearbox.
Background
The torque and the rotating speed of the engine of the driving device used by the automobile can be changed in a limited range, so that various driving conditions of the automobile can not be met, and the torque and the rotating speed under various working conditions required by the automobile can be provided, so that the automobile needs to be provided with a gearbox for shifting, and the torque and the rotating speed of the engine of the gearbox are changed along with the driving conditions of the automobile, so that various driving condition requirements of the automobile can be met.
Because the motor speed regulation range is wider than the engine speed regulation range, the requirement of most driving working conditions of the automobile can be met, the gearbox of the electric vehicle does not need to have multiple gears like the traditional gearbox, and the more gears of the gearbox are, the more complex the structure of the gearbox is, the weight of the whole automobile is increased, and the cost is also increased. Because the automatic gearbox structure and control are more complicated than the manual gear gearbox, the electric vehicle mainly uses the reduction gearbox with fixed speed ratio at present, can not change the speed, influences the whole vehicle performance, and under the condition that the battery capacity is the same, the reduction gearbox with fixed speed ratio needs to output more powerful current than the multi-gear gearbox, has reduced the continuation of the journey mileage of whole vehicle. If the same endurance mileage is provided with a motor with higher power or a battery with higher capacity, the weight and the cost of the whole vehicle are increased, and the power loss and the energy consumption of the whole vehicle are increased.
SUMMERY OF THE UTILITY MODEL
Technical problem to be solved
In order to solve the above-mentioned problem of prior art, the utility model provides a planet row formula three keeps off gearbox.
(II) technical scheme
In order to achieve the above object, the utility model discloses a main technical scheme include:
the utility model provides a planetary gear type three-gear transmission, which comprises a shell, a first brake gear shifting mechanism, a second brake gear shifting mechanism, a clutch gear shifting mechanism and a gear transmission mechanism;
the shell is fixedly connected with the shell;
the first brake gear shifting mechanism and the second brake gear shifting mechanism share the same brake sliding sleeve;
the clutch gear shifting mechanism comprises a clutch and a clutch sliding sleeve;
the gear transmission mechanism comprises a gear ring and a sun wheel seat;
in the first brake gear shifting mechanism, the outer teeth of a brake sliding sleeve are in sliding connection with the inner teeth of the shell, and the brake sliding sleeve axially moves along the inner teeth of the shell and can be connected with the outer teeth of the sun gear seat;
in the second brake gear shifting mechanism, the outer teeth of the brake sliding sleeve are in sliding connection with the inner teeth of the shell, and the brake sliding sleeve axially moves along the inner teeth of the shell and can be connected with the outer teeth of the gear ring;
the clutch comprises an oil cylinder, clutch sliding sleeve inner teeth and oil cylinder large-diameter outer teeth are in sliding connection, and the clutch sliding sleeve moves axially along the oil cylinder large-diameter outer teeth and can be connected with sun gear seat end teeth.
According to the utility model discloses, the first stopper gearshift still includes the first stopper, and the first stopper includes first piston, first spring holder;
the shell is provided with a positioning boss which axially limits the first piston;
the shell is also provided with two ring grooves, namely a first ring groove and a second ring groove, wherein a first snap spring is arranged in the first ring groove for axial limiting, and a second snap spring is arranged in the second ring groove for axial limiting;
the first spring seat is axially limited by the first clamp spring;
the first spring is arranged between the first piston and the first spring seat, one end of the first spring is in contact with the first spring seat, and the other end of the first spring is in contact with the first piston.
According to the utility model, the first brake further comprises a first dual plate and a first friction plate;
the first pair of even pieces and the first friction plate are arranged at intervals, the first pair of even pieces is in splined connection with the shell, and the first friction plate is in splined connection with the sun wheel seat.
According to the utility model discloses, the second stopper gearshift still includes the second stopper, and the second stopper includes second piston, second spring holder;
the shell is provided with a positioning boss which axially limits the second piston;
the shell is also provided with two ring grooves, namely a third ring groove and a fourth ring groove, wherein a third snap spring is installed in the third ring groove for axial limiting, and a fourth snap spring is installed in the fourth ring groove for axial limiting;
the second spring seat is axially limited by the second clamp spring;
the second spring is arranged between the second piston and the second spring seat, one end of the second spring is in contact with the second spring seat, and the other end of the second spring is in contact with the second piston.
According to the utility model, the second brake further comprises a second dual plate and a second friction plate;
the second counter piece and the second friction plate are arranged at intervals, the second counter piece is connected with the shell through a spline, and the second friction plate is connected with the gear ring through a spline.
According to the utility model, the gear transmission mechanism comprises an input shaft, a large sun gear, a long planet gear, a short planet gear and a planet gear shaft;
a small sun gear is fixedly arranged on the input shaft, the large sun gear is sleeved on the input shaft through a sixth bearing, and a gap is formed between the large sun gear and the small sun gear;
the sun wheel seat is connected with a large sun wheel spline;
the big sun gear is provided with a fifth annular groove, and a fifth clamp spring is installed in the fifth annular groove for axial limiting.
According to the utility model, the long planet gears and the short planet gears are sleeved on the planet gear shaft, the planet carriers are fixed at two ends of the planet gear shaft, and the planet carriers are rotationally connected with the sun gear seat;
the short planet wheel is meshed with the small sun wheel, and the long planet wheel is meshed with the large sun wheel;
the short planet wheel is respectively meshed with the long planet wheel and the gear ring.
According to the utility model, the clutch comprises a third piston, a balance piston, a third spring and a positioning boss arranged on the oil cylinder, and the positioning boss axially limits the third piston;
a sixth ring groove and a seventh ring groove are respectively arranged on the large-diameter inner teeth and the small-diameter outer circles of the oil cylinders, wherein a sixth snap spring is installed in the sixth ring groove for axial limiting, and a seventh snap spring is installed in the seventh ring groove for axial limiting;
the balance piston is axially limited by a sixth clamp spring; and one end of the third spring is in contact with the third piston, and the other end of the third spring is in contact with the balance piston.
According to the utility model, the clutch also comprises a third dual plate and a third friction plate;
the third dual plate and the third friction plate are arranged at intervals, the third dual plate is connected with an oil cylinder spline, and the third friction plate is connected with a sun wheel seat spline.
According to the utility model discloses, the hydro-cylinder cover is established on the input shaft, the path internal spline of hydro-cylinder with input shaft splined connection.
(III) advantageous effects
The utility model has the advantages that: the utility model discloses a planet formula three-gear gearbox possess wideer variable speed range, utilize the automatic switch-over of three kinds of velocity ratios of gearbox, and the economic nature of satisfying whole car that can be better and the requirement of acceleration nature promote whole car performance. Under the condition of the same endurance mileage, the planetary gear-type three-gear transmission can reduce the battery capacity, reduce the weight and the cost of the whole vehicle, and reduce the power loss and the energy consumption of the whole vehicle. Under the condition that the battery capacity is the same, the planetary gear type three-gear transmission can output lower-power current compared with a transmission, and the endurance mileage of the whole vehicle is increased.
Drawings
Fig. 1 is a structural diagram of the automatic transmission of the present invention.
[ description of reference ]
1: a housing; 2: a first piston; 3: a first spring; 4: a first clamp spring; 5: a first spring seat; 6: a sun gear seat; 7: a first pair of doublets; 8: a first friction plate; 9: a second clamp spring; 10: a first bearing; 11: a planetary wheel shaft; 12: braking the sliding sleeve; 13: a long planetary gear; 14: a third clamp spring; 15: a second pair of doublets; 16: a second friction plate; 17: a ring gear; 18: a second spring seat; 19: a fourth clamp spring; 20: a second spring; 21: a second piston; 22: a housing;
23: an input shaft; 24: a second bearing; 25: a third bearing; 26: a fourth bearing; 27: a short planet wheel; 28: a planet carrier; 29: a fifth bearing; 30: a sixth bearing; 31: a large sun gear; 32: a seventh bearing; 33: a clutch sliding sleeve; 34: a third dual patch; 35: a third friction plate; 36: an oil cylinder; 37: a third piston; 38: a balance piston; 39: a third spring; 40: a fifth clamp spring; 41; a sixth clamp spring; 42: an eighth bearing; 43: a ninth bearing; 44: a tenth bearing; 45: and a seventh snap spring.
Detailed Description
For a better understanding of the present invention, reference will now be made in detail to the present invention, examples of which are illustrated in the accompanying drawings.
The utility model provides a planet row formula three-gear gearbox, as shown in FIG. 1, this gearbox includes two stopper gearshift, a clutch gearshift and a gear drive.
The brake gear shifting mechanism comprises a first brake gear shifting mechanism and a second brake gear shifting mechanism, the first brake gear shifting mechanism comprises a first brake and a brake sliding sleeve, the second brake gear shifting mechanism comprises a second brake and a brake sliding sleeve, and the first brake gear shifting mechanism and the second brake gear shifting mechanism share the same brake sliding sleeve, namely the brake sliding sleeve 12.
The first brake gear shifting mechanism comprises a first brake and a brake sliding sleeve 12, wherein the first brake comprises a first piston 2, a first spring 3, a first clamp spring 4, a first spring seat 5, a first dual plate 7, a first friction plate 8 and a second clamp spring 9.
The second brake gear shifting mechanism comprises a second brake and a brake sliding sleeve 12, wherein the second brake comprises a third snap spring 14, a second dual plate 15, a second friction plate 16, a second spring seat 18, a fourth snap spring 19, a second spring 20 and a second piston 21.
The clutch gear shifting mechanism comprises a clutch and a clutch sliding sleeve 33, the clutch comprises an oil cylinder 36, a third piston 37, a balance piston 38, a third spring 39, a third dual plate 34, a third friction plate 35, a fifth snap spring 41 and a sixth snap spring 45,
the gear transmission comprises a ring gear 17, an input shaft 23, a large sun gear 31, a planet carrier 28, a long planet gear 13, a short planet gear 27, a planet gear shaft 11 and a sun gear seat 6.
The planetary gear row type three-gear transmission comprises a shell 1 and a shell 22, wherein the shell 1 is fixedly connected with the shell 22.
The clutch or brake actuating mechanism comprises a hydraulic type and an electric control type, the hydraulic type clutch is selected in the embodiment and consists of an oil cylinder, a piston and a spring, and the clutch actuating mechanism can also be selected in the electric control type and consists of a motor, a speed reducing mechanism, an axial propelling mechanism and the like.
Gear transmission mechanism
The input shaft 23 is fixedly provided with a small sun gear, the small sun gear is provided with external teeth, the large sun gear 31 is supported and sleeved on the input shaft 23 through a sixth bearing 30, and a gap is formed between the large sun gear 31 and the small sun gear.
The long planet wheel 13 and the short planet wheel 27 are both provided with external teeth, the short planet wheel 27 is meshed with the small sun wheel, and the long planet wheel 13 is meshed with the large sun wheel 31.
The short planet wheel 27 is externally sleeved with a gear ring 17, the inner ring and the outer ring of the gear ring 17 are both provided with teeth, the short planet wheel 27 is respectively engaged with the inner teeth of the long planet wheel 13 and the gear ring 17, and the gear ring 17 is axially positioned by the third bearing 25.
The long planet gears 13 and the short planet gears 27 are supported and sleeved on the planet gear shaft 11 through the first bearing 10, the planet carrier 28 is fixed at two ends of the planet gear shaft 11, and the planet carrier 28 at one side close to the shell 22 is axially limited by the fourth bearing 26 and the third bearing 25.
The big sun gear 31 is provided with a fifth ring groove, and a fifth clamp spring 40 is arranged in the fifth ring groove for axial limiting. The outer circle of the sun wheel seat 6 with the large diameter is provided with small outer teeth and large outer teeth respectively, the inner circle with the small diameter is provided with an internal spline and connected with the external spline of the large sun wheel 31, the planet carrier 28 close to one side of the oil cylinder 36 is axially limited by the seventh bearing 32, and the two ends of the sun wheel seat 6 close to one side of the oil cylinder 36 are both provided with teeth.
One end of the clutch sliding sleeve 33 close to the sun wheel seat 6 is provided with teeth which can be connected with the teeth at one end of the sun wheel seat 6 close to the oil cylinder 36.
The brake sliding sleeve 12 is provided with internal teeth which can be connected with the large external teeth of the sun gear seat 6.
First brake gear shift mechanism
The shell 1 is provided with two ring grooves, namely a first ring groove and a second ring groove, wherein a first snap spring 4 is installed in the first ring groove for axial limiting, and a second snap spring 9 is installed in the second ring groove for axial limiting.
The shell 1 is provided with a positioning boss, and the first piston 2 is in contact with the positioning boss to perform axial limiting. The major diameter and the minor diameter of the first piston 2 are provided with sealing structures which are respectively in contact with the outer diameter and the inner diameter of the shell 1, the first spring seat 5 is axially limited by the first clamp spring 4, the first spring seat 5 is not in contact with the first piston 3, the inner diameter of the first spring seat 5 is in clearance fit with the shell 1, and the other end of the first spring seat is in contact with the first clamp spring 4 and is axially limited on the shell 1.
The first spring 3 is disposed between the first piston 2 and the first spring seat 5, and one end of the first spring 3 is in contact with the first spring seat 14 and the other end is in contact with the first piston 2.
Be equipped with the internal tooth on the shell 1, first dual piece 7 is equipped with the external tooth, and first friction disc 8 is equipped with the internal tooth, and first dual piece 7 and first friction disc 8 interval are placed, and 7 external teeth of first dual piece and 1 internal tooth of shell are connected, and 8 internal teeth of first friction disc are connected with the big external tooth of sun gear seat 6.
The outer ring of the braking sliding sleeve 12 is provided with outer teeth, the outer teeth of the outer ring of the braking sliding sleeve 12 are in sliding connection with the inner teeth of the shell 1, and the braking sliding sleeve 12 can axially move along the inner teeth of the shell 1. The inner ring of the brake sliding sleeve 12 is provided with internal teeth which can be connected with the large external teeth of the sun wheel seat 6.
Second brake shift mechanism
The shell 22 is provided with two ring grooves, namely a third ring groove and a fourth ring groove, wherein a third snap spring 14 is installed in the third ring groove for axial limiting, and a fourth snap spring 19 is installed in the fourth ring groove for axial limiting.
The housing 22 is provided with a positioning boss, and the second piston 21 is in contact with the positioning boss to perform axial limiting. The large diameter and the small diameter of the second piston 21 are both provided with sealing structures which are respectively contacted with the outer diameter and the inner diameter of the shell 22, the second spring seat 18 is axially limited by a fourth snap spring 19, the inner diameter of the second spring seat 18 is in clearance fit with the shell 22, the other end of the second spring seat is contacted with the fourth snap spring 19, and the second spring seat is axially limited on the shell 22.
The second spring 20 is interposed between the second piston 21 and the second spring seat 18, and one end of the second spring 20 is connected to the second spring seat 18 and the other end is connected to the second piston 21.
The shell 22 is provided with internal teeth, the second dual plate 15 is provided with external teeth, the second friction plate 16 is provided with internal teeth, the second dual plate 15 and the second friction plate 16 are arranged at intervals, the second dual plate external teeth 15 are connected with the internal teeth of the shell 22, and the internal teeth of the second friction plate 16 are connected with the external teeth of the gear ring 17.
The outer ring of the braking sliding sleeve 12 is provided with outer teeth, the outer ring outer teeth of the braking sliding sleeve 12 are in sliding connection with the inner teeth of the shell 22, the braking sliding sleeve 12 can move axially along the inner teeth of the shell 22, the inner ring of the braking sliding sleeve 12 is provided with inner teeth, and the inner teeth can be connected with the outer teeth of the gear ring 17.
Clutch gearshift
A sixth ring groove is formed in the large-diameter inner tooth of the oil cylinder 36, and a sixth clamp spring 41 is installed in the sixth ring groove for axial limiting. A seventh ring groove is formed in the outer circle of the small diameter of the oil cylinder 36, and a seventh snap spring 45 is installed in the seventh ring groove for axial limiting.
One side of the oil cylinder 36 close to the shell 1 is provided with a positioning boss, and the third piston 37 is contacted with the positioning boss to perform axial limit. The large diameter and the small diameter of the third piston 37 are provided with sealing structures to be respectively contacted with the outer diameter and the inner diameter of the oil cylinder 36, the balance piston 38 is axially limited by a sixth snap spring 41, and the large diameter of the balance piston 38 is provided with a sealing structure to be contacted with the inner diameter of the third piston 37; the small diameter has a larger clearance with the outer diameter of the oil cylinder 36, and the other end of the small diameter is in contact with the sixth snap spring 41 and axially limited on the oil cylinder 36.
A third spring 39 is interposed between the third piston 37 and the balance piston 38, and one end of the third spring 39 is connected to the third piston 37 and the other end is connected to the balance piston 38.
The shell 1 is rotatably connected with the input shaft 23, a tenth bearing 43 is arranged at the connecting position, a ninth bearing 42 is arranged between the shell 1 and the input shaft 23, the oil cylinder 36 is sleeved on the input shaft 23, and the oil cylinder 36 is provided with an internal spline in a small diameter and is connected with an external spline of the input shaft 23.
The inner circle with the large diameter of the oil cylinder 36 and the outer circle with the large diameter are respectively provided with inner teeth and outer teeth, the third dual plate 34 is provided with outer teeth, the third friction plate 35 is provided with inner teeth, the third dual plate 34 and the third friction plate 35 are arranged at intervals, the inner teeth of the third dual plate 34 are connected with the inner teeth of the oil cylinder 36, and the inner teeth of the third friction plate 35 are connected with the large outer teeth of the sun gear seat 6.
The clutch sliding sleeve 33 is provided with internal teeth, the internal teeth of the clutch sliding sleeve 33 are in sliding connection with the large-diameter external teeth of the oil cylinder 36, the clutch sliding sleeve 33 moves axially along the large-diameter external teeth of the oil cylinder 36, and teeth are arranged at one end, close to the sun gear seat 6, of the clutch sliding sleeve 33 and can be connected with the teeth at one end, close to the oil cylinder 36, of the sun gear seat 6.
The specific working process is as follows:
when the clutch gear shifting mechanism shifts gears, the oil cylinder 36 and the third piston 37 form a closed space, after pressure oil enters the closed space, the third piston 37 is pushed to move axially in the direction away from the oil cylinder 36, and the third piston 37 is in contact with the third dual plate 34.
Meanwhile, the operating mechanism of the clutch sliding sleeve 33 pushes the clutch sliding sleeve 33 to move axially along the direction of the large-diameter external teeth of the oil cylinder 36 to approach the sun wheel seat 6, and when the third pair of friction plates 34 and the third friction plate 35 gradually contact and form sliding friction, and the difference between the input rotating speed of the oil cylinder 36 and the output rotating speed of the sun wheel seat 6 is very small, namely synchronization is formed, the clutch sliding sleeve 33 and the sun wheel seat 6 are directly and rigidly connected to transmit power, and the clutch is shifted.
The pressure oil of the clutch cylinder 36 and the cooling oil of the third friction plate 35 can be disconnected, the third piston 37 is restored to the original position under the action of the third spring 39, and no pressure force is generated between the third friction plate 35 and the third counter plate 34, so that power cannot be transmitted.
When the clutch gear shifting mechanism works, power is input by the input shaft 23, is rigidly connected with the sun gear seat 6 through the clutch sliding sleeve 33, and is finally directly transmitted to the sun gear seat 1 through the planet carrier 28: 1 output. The input power is directly transmitted by the rigid connection of the clutch sliding sleeve 33 and the sun wheel seat 6, no power loss exists, and the transmission efficiency of the gearbox is improved.
When the first brake gear shifting mechanism shifts gears, the shell 1 and the first piston 2 form a closed space, after pressure oil enters the closed space, the first piston 2 is pushed to move axially in the direction close to the sun wheel seat 6, and the first piston 2 is in contact with the first pair of coupling pieces 7.
Meanwhile, the operating mechanism of the brake sliding sleeve 12 pushes the brake sliding sleeve 12 to move axially along the inner teeth of the shell 1 towards the direction close to the sun wheel seat 6, when the first couple plate and the first friction plate 8 gradually contact and form sliding friction, and the rotating speed of the sun wheel seat 6 is synchronous with the rotating speed of the shell 1, the inner teeth of the inner ring of the brake sliding sleeve 12 are directly and rigidly connected with the large outer teeth of the sun wheel seat 6, the sun wheel seat 6 is locked, and the gear shifting of the brake is completed.
The pressure oil of the brake outer shell 1 and the cooling lubricating oil of the first friction plate 8 can be disconnected, the first piston 2 is restored to the original position under the action of the first spring 4, no pressure force exists between the first friction plate 8 and the first counter plate 7, and the sun wheel seat 6 cannot be locked.
When the first brake gear shifting mechanism works, power is input through the input shaft 23, the small sun gear is meshed with the short planet gear 27, the short planet gear 27 is meshed with the long planet gear 13, the long planet gear 13 is meshed with the large sun gear 31, the large sun gear 31 and the sun gear seat 6 are connected in a spline mode to form a whole body to be locked, speed is changed through the planet gears, and finally the power is output through the planet carrier 28. All the locking torque of the sun wheel seat 6 is directly transmitted by the rigid connection of the braking sliding sleeve 12 and the shell 1, no power loss exists, and the transmission efficiency of the gearbox is improved.
When the second brake gear shifting mechanism shifts gears, the shell 22 and the second piston 23 form a closed space, after pressure oil enters the closed space, the second piston 32 is pushed to move axially in the direction close to the oil cylinder 36, and the second piston 23 is in contact with the second coupling piece 15.
Meanwhile, the operating mechanism of the brake sliding sleeve 12 pushes the brake sliding sleeve 12 to move axially in the direction away from the sun gear seat 6 along the inner teeth of the shell 22, when the second couple plate 15 and the second friction plate 16 gradually contact and form sliding friction, and the rotating speed of the gear ring 17 is synchronous with that of the shell 22, the inner teeth of the brake sliding sleeve 12 are directly and rigidly connected with the outer teeth of the gear ring 17, the gear ring 17 is locked, and the brake finishes gear shifting.
The pressure oil of the brake housing 22 and the cooling lubricant oil of the second friction plate 16 can be disconnected, the second piston 21 is restored to the original position under the action of the second spring 20, no pressure force is generated between the second friction plate 16 and the second counter plate 15, and the ring gear 17 cannot be locked.
When the second brake gear shifting mechanism works, power is input through the input shaft 23, the small sun gear is meshed with the short planet gear 27, the short planet gear 27 is meshed with the gear ring 17, the gear ring 17 is locked, and finally the power is output through the planet gear shifting by the planet carrier 28. The entire locking torque of the ring gear 17 is transmitted directly by the rigid connection of the brake slide sleeve 12 with the housing 22 without power losses.
The utility model discloses a planet formula three-gear gearbox possess wideer variable speed range, utilize the automatic switch-over of three kinds of velocity ratios of gearbox, and the economic nature of satisfying whole car that can be better and the requirement of acceleration nature promote whole car performance. Under the condition of the same endurance mileage, the planetary gear-type three-gear transmission can reduce the battery capacity, reduce the weight and the cost of the whole vehicle, and reduce the power loss and the energy consumption of the whole vehicle. Under the condition that the battery capacity is the same, the planetary gear type three-gear transmission can output lower-power current compared with the traditional transmission, and the endurance mileage of the whole vehicle is increased. Clutch and stopper in the structure of shifting gears only work when the gearbox shifts gears, clutch and stopper are opened after shifting gears, replace clutch and stopper transmission power by clutch sliding sleeve and braking sliding sleeve rather than adapting unit rigid connection, clutch sliding sleeve and braking sliding sleeve all are provided with the tooth, and can axial displacement and be connected with the part that matches, carry out the power transmission after being connected with the part that matches, greatly reduced gearbox's loss, transmission efficiency has been improved, and the overload risk of skidding has been avoided, clutch and stopper's life has been increased, the reliability and the quality of gearbox have been promoted.
It should be understood that the above description of the embodiments of the present invention is only for illustrating the technical lines and features of the present invention, and the purpose of the present invention is to enable those skilled in the art to understand the contents of the present invention and to implement the present invention accordingly, but the present invention is not limited to the above specific embodiments. All changes and modifications that come within the scope of the claims are to be embraced within their scope.

Claims (10)

1. The utility model provides a planet row formula three-gear gearbox which characterized in that: the gearbox comprises a shell (1), a shell (22), a first brake gear shifting mechanism, a second brake gear shifting mechanism, a clutch gear shifting mechanism and a gear transmission mechanism;
the shell (1) is fixedly connected with the shell (22);
the first brake gear shifting mechanism and the second brake gear shifting mechanism share the same brake sliding sleeve (12);
the clutch gear shifting mechanism comprises a clutch and a clutch sliding sleeve (33);
the gear transmission mechanism comprises a gear ring (17) and a sun wheel seat (6);
in the first brake gear shifting mechanism, external teeth of a brake sliding sleeve (12) are in sliding connection with internal teeth of a shell (1), and the brake sliding sleeve (12) axially moves along the internal teeth of the shell (1) and can be connected with external teeth of a sun gear seat (6);
in the second brake gear shifting mechanism, external teeth of a brake sliding sleeve (12) are in sliding connection with internal teeth of a shell (22), and the brake sliding sleeve (12) axially moves along the internal teeth of the shell (22) and can be connected with external teeth of a gear ring (17);
the clutch is including hydro-cylinder (36), clutch sliding sleeve (33) internal tooth with hydro-cylinder (36) external tooth sliding connection, axial displacement is made along hydro-cylinder (36) external tooth to clutch sliding sleeve (33), can be connected with sun gear seat (6) end tooth.
2. The epicyclic triple speed transmission of claim 1, wherein:
the first brake gear shifting mechanism further comprises a first brake, and the first brake comprises a first piston (2), a first spring (3) and a first spring seat (5);
a positioning boss is arranged on the shell (1), and the positioning boss axially limits the first piston (2);
the shell (1) is also provided with two ring grooves, namely a first ring groove and a second ring groove, wherein a first snap spring (4) is installed in the first ring groove for axial limiting, and a second snap spring (9) is installed in the second ring groove for axial limiting;
the first spring seat (5) is axially limited by the first clamp spring (4);
the first spring (3) is arranged between the first piston (2) and the first spring seat (5), one end of the first spring (3) is in contact with the first spring seat (5), and the other end of the first spring is in contact with the first piston (2).
3. The epicyclic triple speed transmission of claim 2, wherein:
the first brake further comprises a first pair of friction plates (7) and a first friction plate (8);
the first pair of coupling pieces (7) and the first friction plates (8) are arranged at intervals, the first pair of coupling pieces (7) are in splined connection with the outer shell (1), and the first friction plates (8) are in splined connection with the sun wheel seat (6).
4. The epicyclic triple speed transmission of claim 3, wherein:
the second brake gear shifting mechanism further comprises a second brake, and the second brake comprises a second piston (21), a second spring (20) and a second spring seat (18);
a positioning boss is arranged on the shell (22), and the positioning boss axially limits the second piston (21);
the shell (22) is also provided with two ring grooves, namely a third ring groove and a fourth ring groove, wherein a third snap spring (14) is installed in the third ring groove for axial limiting, and a fourth snap spring (19) is installed in the fourth ring groove for axial limiting;
the second spring seat (18) is axially limited by the second clamp spring (9);
the second spring (20) is arranged between the second piston (21) and the second spring seat (18), one end of the second spring (20) is in contact with the second spring seat (18), and the other end of the second spring is in contact with the second piston (21).
5. The epicyclic triple speed transmission of claim 4, wherein:
the second brake further comprises a second dual plate (15) and a second friction plate (16);
the second dual plate (15) and the second friction plate (16) are arranged at intervals, the second dual plate (15) is in splined connection with the shell (22), and the second friction plate (16) is in splined connection with the gear ring (17).
6. The epicyclic triple speed transmission of claim 5, wherein:
the gear transmission mechanism comprises an input shaft (23), a large sun gear (31), a long planet gear (13), a short planet gear (27) and a planet gear shaft (11);
the gear ring (17) is sleeved on the input shaft (23), a small sun gear is fixedly arranged on the input shaft (23), the large sun gear (31) is sleeved on the input shaft (23) through a sixth bearing (30), and a gap is formed between the large sun gear (31) and the small sun gear;
the sun wheel seat (6) is connected with the big sun wheel (31) by a spline;
the big sun gear (31) is provided with a fifth annular groove, and a fifth clamp spring (40) is installed in the fifth annular groove and used for axial limiting.
7. The epicyclic triple speed transmission of claim 6, wherein:
the long planet wheel (13) and the short planet wheel (27) are sleeved on a planet wheel shaft (11), planet carriers (28) are fixed at two ends of the planet wheel shaft (11), and the planet carriers (28) are rotationally connected with a sun wheel seat (6);
the short planet wheel (27) is meshed with the small sun wheel, and the long planet wheel (13) is meshed with the large sun wheel (31);
the short planet wheels (27) are respectively meshed with the long planet wheels (13) and the gear ring (17).
8. The epicyclic triple speed transmission of claim 7, wherein:
the clutch comprises a third piston (37), a balance piston (38), a third spring (39), and a positioning boss is arranged on the oil cylinder (36), and the positioning boss axially limits the third piston (37);
a sixth annular groove and a seventh annular groove are respectively formed in the large-diameter inner teeth and the small-diameter outer circles of the oil cylinders (36), a sixth snap spring (41) is installed in the sixth annular groove to perform axial limiting, and a seventh snap spring (45) is installed in the seventh annular groove to perform axial limiting;
the balance piston (38) is axially limited by a sixth clamp spring (41); the third spring (39) is arranged between the third piston (37) and the balance piston (38), one end of the third spring (39) is in contact with the third piston (37), and the other end of the third spring (39) is in contact with the balance piston (38).
9. The epicyclic triple speed transmission of claim 8, wherein:
the clutch further comprises a third pair of friction plates (34) and a third friction plate (35);
the third dual plate (34) and the third friction plate (35) are arranged at intervals, the third dual plate (34) is in splined connection with the oil cylinder (36), and the third friction plate (35) is in splined connection with the sun wheel seat (6).
10. The epicyclic triple speed transmission of claim 9, wherein:
the oil cylinder (36) is sleeved on the input shaft (23), and a small-diameter internal spline of the oil cylinder (36) is connected with an external spline of the input shaft (23).
CN201921839636.XU 2019-09-29 2019-10-30 Planet row type three-gear gearbox Active CN211259510U (en)

Applications Claiming Priority (2)

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CN201910932652 2019-09-29
CN2019109326521 2019-09-29

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CN201911041648.2A Pending CN110701263A (en) 2019-09-29 2019-10-30 Planet row type three-gear gearbox

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