CN111089145A - Variable-speed driving device with bidirectional input and unidirectional output and vehicle - Google Patents

Variable-speed driving device with bidirectional input and unidirectional output and vehicle Download PDF

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Publication number
CN111089145A
CN111089145A CN202010036053.4A CN202010036053A CN111089145A CN 111089145 A CN111089145 A CN 111089145A CN 202010036053 A CN202010036053 A CN 202010036053A CN 111089145 A CN111089145 A CN 111089145A
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China
Prior art keywords
gear
clutch
shaft
overrunning clutch
input shaft
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Pending
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CN202010036053.4A
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Chinese (zh)
Inventor
黄键
徐世跃
陈学文
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Fujian Wanrun New Energy Technology Co ltd
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Fujian Wanrun New Energy Technology Co ltd
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Priority to CN202010036053.4A priority Critical patent/CN111089145A/en
Publication of CN111089145A publication Critical patent/CN111089145A/en
Pending legal-status Critical Current

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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
    • F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with 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
    • F16H2200/2002—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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means

Abstract

The invention relates to a vehicle driving system, and provides a variable speed driving device with bidirectional input and unidirectional output and a vehicle, comprising: the system comprises a power input shaft, a power output shaft, an epicyclic gear train, a clutch, a first one-way overrunning clutch and a second one-way overrunning clutch; the power input shaft is connected with the power output shaft through a clutch; a planet carrier of the epicyclic gear train is connected with the power input shaft through a first transmission assembly, a sun gear is connected with the power input shaft through a second transmission assembly, and a gear ring is connected with the power output shaft through a third transmission assembly; a first one-way overrunning clutch and a second one-way overrunning clutch are respectively connected between the planet carrier and the first transmission assembly and between the shells, and the constraint steering of the first one-way overrunning clutch and the constraint steering of the second one-way overrunning clutch are opposite. The variable speed driving device with bidirectional input and unidirectional output has simple structure and convenient control, and can realize bidirectional input and unidirectional variable speed output by only controlling one clutch.

Description

Variable-speed driving device with bidirectional input and unidirectional output and vehicle
Technical Field
The present invention relates to a vehicle drive system, and more particularly to a variable speed drive device with bidirectional input and unidirectional output and a vehicle.
Background
The national policy strives to improve the requirements of the engineering machinery and promote the development of the engineering machinery industry, which inevitably drives the engineering machinery industry to a certain extent. In the engineering fields of machinery, automobiles and the like, there is a typical power drive requirement: when the rotational direction of the power input is changed, the rotational direction of the required power output remains unchanged. At present, the existing power driving device needs to judge the direction and control more than two brakes according to the judged direction to obtain the single-direction rotation output, so the existing driving device is complex in structure and control, and the control difficulty of the cost of the driving device is greatly increased.
Disclosure of Invention
Therefore, a variable speed driving device with bidirectional input and unidirectional output is needed to be provided for solving the technical problems of complicated structure and control of the existing bidirectional input and unidirectional output setting.
To achieve the above object, the present inventors provide a bidirectional-input unidirectional-output variable speed drive device including: the system comprises a power input shaft, a power output shaft, an epicyclic gear train, a clutch, a first one-way overrunning clutch and a second one-way overrunning clutch;
the power input shaft and the power output shaft are coaxially arranged and are connected through a clutch;
the planetary gear train comprises a sun gear, a planetary gear, a planet carrier and a gear ring, the planetary gear is rotatably arranged on the planet carrier, the sun gear is meshed with the planetary gear, and the planetary gear is meshed with the gear ring;
the planet carrier is in transmission connection with the power input shaft through a first transmission assembly, the sun gear is in transmission connection with the power input shaft through a second transmission assembly, and the gear ring is in transmission connection with the power output shaft through a third transmission assembly;
a first one-way overrunning clutch is connected between the planet carrier and the first transmission assembly, a second one-way overrunning clutch is connected between the planet carrier and the shell, and the constraint directions of the first one-way overrunning clutch and the second one-way overrunning clutch are opposite;
when the power input shaft rotates forwards or reversely, the clutch is controlled to be combined or separated, and the power output shaft rotates in a single direction and has two different rotating speeds.
Further, the first transmission assembly, the second transmission assembly and the third transmission assembly are gear set reverse transmission assemblies.
Further, the output/input speed ratio of the first transmission assembly < the output/input speed ratio of the third transmission assembly < the output/input speed ratio of the second transmission assembly.
Furthermore, the first transmission assembly comprises a first gear and a third gear, the first gear is meshed with the third gear, the first gear is fixedly connected with the power input shaft, the third gear is fixedly connected with an inner ring of the first one-way overrunning clutch, and an outer ring of the first one-way overrunning clutch is fixedly connected with the planet carrier;
the second transmission assembly comprises a second gear and a fourth gear, the second gear is meshed with the fourth gear, the second gear is fixedly connected with the power input shaft, and the fourth gear is fixedly connected with the sun gear;
the third transmission assembly comprises a fifth gear and a sixth gear, the fifth gear is meshed with the sixth gear, the sixth gear is fixedly connected with the power output shaft, and the fifth gear is fixedly connected with the gear ring.
Further, the power input shaft rotates in the forward direction, when the clutch is separated, the first one-way overrunning clutch drives the planet carrier to rotate in the reverse direction, the sun gear rotates in the reverse direction, the gear ring rotates in the reverse direction, and the gear ring drives the power output shaft to rotate in the forward direction at a low speed;
the power input shaft rotates in the positive direction, and when the clutch is combined, the power input shaft drives the power output shaft to synchronously rotate in the positive direction;
the power input shaft rotates reversely, when the clutch is separated, the sun gear rotates forwardly, the first one-way overrunning clutch enables the planet carrier to be separated from the power input shaft, the second one-way overrunning clutch restricts the planet carrier not to rotate forwardly, the gear ring rotates reversely by the forward rotation of the sun gear, and the gear ring drives the power output shaft to rotate forwardly at a low speed.
Further, the rotating shaft of the driving motor is connected with the power input shaft, or the rotating shaft of the driving motor is the power input shaft.
In order to solve the above technical problem, the present invention further provides another technical solution:
a vehicle comprises a driving device, wherein the driving device is used for driving the vehicle to run, and the driving device is a bidirectional-input one-way-output variable-speed driving device in any one of the technical schemes.
Different from the prior art, the driving device in the technical scheme comprises an epicyclic gear train, a power input shaft, a power output shaft, a clutch, a first one-way overrunning clutch and a second one-way overrunning clutch, wherein the clutch is arranged between the power input shaft and the power output shaft, the power input shaft is connected with a planet carrier through a first transmission component, a sun gear is connected with the power input shaft through a second transmission component, and a gear ring is connected with the power output shaft through a third transmission component, so that the power connection between the power input shaft and the power output shaft is realized through the clutch, or the power connection between the power input shaft and the power output shaft is realized through the first transmission component, the second transmission component, the third transmission component and the epicyclic gear train, and the driving device is also provided with the first one-way clutch between the planet carrier and the first transmission component and provided with the second one-way clutch between the planet carrier and the shell, the first one-way overrunning clutch and the second one-way overrunning clutch are opposite in constraint steering, and power is input in two directions and output in one direction through the combination of the constraint of the first one-way overrunning clutch and the second one-way overrunning clutch and the clutch, and high-speed and low-speed output is achieved. The variable speed driving device with bidirectional input and unidirectional output has simple structure and convenient control, and can realize bidirectional input and unidirectional variable speed output by only controlling one clutch.
Drawings
Fig. 1 is a schematic diagram of a bidirectional-input unidirectional-output variable speed drive device according to an embodiment.
Description of reference numerals:
2. a sun gear;
6. a planet wheel;
7. a ring gear;
12. a planet carrier;
15. a clutch;
8. a first one-way overrunning clutch;
11. a second one-way overrunning clutch;
1. a power input shaft;
13. a power take-off shaft;
3. a first transmission shaft;
10. a second transmission shaft;
17. a first gear;
16. a second gear;
4. a third gear;
5. a fourth gear;
9. a fifth gear;
14. a sixth gear;
Detailed Description
To explain technical contents, structural features, and objects and effects of the technical solutions in detail, the following detailed description is given with reference to the accompanying drawings in conjunction with the embodiments.
Referring to fig. 1, the present embodiment provides a bidirectional-input unidirectional-output variable speed driving apparatus. The variable-speed driving device with bidirectional input and one-way output can realize that the power input is realized in only one rotating direction no matter in the forward direction or the reverse direction (namely clockwise or anticlockwise, for convenience of description, clockwise rotation is set as the forward direction, and anticlockwise rotation is set as the reverse direction), and the power output can also realize two different rotating speeds of high speed and low speed. Specifically, the bidirectional-input unidirectional-output variable speed driving device includes: the power input device comprises a power input shaft 1, a power output shaft 13, an epicyclic gear train, a clutch 15, a first one-way overrunning clutch 8 and a second one-way overrunning clutch 11.
Wherein, the epicyclic gear train includes sun gear 2, planet wheel 6, ring gear 7, planet carrier 12, planet wheel 6 has more than two, and planet wheel 6 passes through the rotatable setting on planet carrier 12 of planet wheel axle, sun gear 2 with planet wheel 6 meshes, planet wheel 6 with ring gear 7 meshes.
The power input shaft 1 and the power output shaft 13 are coaxially arranged, the power input shaft 1 and the power output shaft 13 are rotatably arranged on the shell through bearings respectively, wherein the power input shaft 1 can be a rotating shaft of a driving motor or a transmission shaft synchronously rotating with the rotating shaft of the driving motor. The power input shaft 1 is connected with the power output shaft 13 through the clutch 15, the power input shaft 1 and the power output shaft 13 can be combined together to coaxially rotate through the combination of the clutch 15, and when the clutch 15 is separated, the power input shaft 1 and the power output shaft 13 are in power separation. The clutch 15 is a conventional clutch, and includes a driving portion and a driven portion, and the clutch 15 can be combined with and separated from the driving portion and the driven portion no matter the input is positive or negative.
As shown in FIG. 1, the planet carrier 12 is connected with the first transmission shaft 3 through a first one-way overrunning clutch 8, the planet carrier 12 is further connected with the shell of the driving device through a second one-way overrunning clutch 11, and the constraint directions of the first one-way overrunning clutch and the second one-way overrunning clutch are opposite. The transmission shaft I3 is in transmission connection with the power input shaft 1 through a gear III 4 and a gear I17, wherein the transmission shaft I3, the gear III 4 and the gear I17 form a first transmission assembly.
It should be noted that the one-way overrunning clutch includes an outer ring and an inner ring, and the one-way overrunning clutch is implemented between the outer ring and the inner ring, that is, only when the rotation speed of the inner ring exceeds the speed of the outer ring in a certain direction (forward rotation or reverse rotation), the inner ring and the outer ring are combined, and the inner ring and the outer ring are separated under other conditions.
Specifically, the outer ring of the first one-way overrunning clutch 8 is connected with the planet carrier 12, the inner ring of the first one-way overrunning clutch 8 is connected with the first transmission shaft 3, the outer ring of the second one-way overrunning clutch 11 is fixed with the shell of the driving device, and the inner ring of the second one-way overrunning clutch 11 is connected with the planet carrier 12 through the second transmission shaft 10. Therefore, the rotation of the carrier 12 is simultaneously restricted by the first one-way overrunning clutch 8 and the second one-way overrunning clutch 11, and the restriction of the first one-way overrunning clutch 8 and the restriction of the second one-way overrunning clutch 11 are reversed.
The gear 3 is arranged on the first transmission shaft 3 and rotates synchronously with the first transmission shaft 3, the first gear is arranged on the power input shaft 1 and rotates synchronously with the power input shaft 1, and the first gear 17 is meshed with the third gear 4, so that the power input shaft 1 can drive the first transmission shaft 3 and the power input shaft 1 to rotate reversely through the first gear 17 and the third gear 4. The number of teeth of the first gear 17 can be smaller than that of the third gear 4, so that the rotating speed of the first transmission shaft 3 is smaller than that of the power input shaft 1, namely, the first transmission assembly is a speed reduction transmission assembly.
The sun gear 2 is in power connection with the power input shaft 1 through the gear four 5 and the gear two 16, the gear four 5 and the gear two 16 form a second transmission assembly, and the power input shaft 1 can drive the transmission shaft sun gear 2 and the power input shaft 1 to rotate reversely through the gear two 16 and the gear four 5. The number of teeth of the second gear 16 is greater than that of the fourth gear 5, that is, the second transmission assembly is a speed-increasing transmission assembly.
The gear ring 7 is in transmission connection with the power output shaft 13 through a gear five 9 and a gear 6, wherein the gear five 9 is connected with the gear ring 7 and rotates synchronously with the gear ring 7, a gear six 14 is connected with the power output shaft 13 and rotates synchronously with the power output shaft 13, the gear six 14 is meshed with the gear five 9, and the gear six 14 and the gear five 9 form a third transmission assembly, so that the gear ring 7 can drive the power output shaft 13 to rotate reversely with the gear ring 7 through the gear six 14 and the gear five 9. The number of teeth of the gear five 9 may be equal to the number of teeth of the gear six 14, that is, the third transmission assembly may be a traveling assembly.
When the power input shaft 1 rotates forwards or backwards, the clutch 15 is controlled to be combined or separated, and the power output shaft 13 rotates in a single direction and has two different rotating speeds.
In fig. 1, the first one-way overrunning clutch 8 restricts the inner ring from rotating in a reverse direction (i.e., counterclockwise) relative to the outer ring (i.e., only the inner ring of the first one-way overrunning clutch 8 is allowed to drive the outer ring counterclockwise), and the second one-way overrunning clutch 11 restricts the inner ring from rotating in a forward direction (i.e., clockwise) relative to the outer ring (in fig. 1, the outer ring of the second one-way overrunning clutch 11 is fixed, i.e., only the inner ring is allowed to rotate counterclockwise, but the inner ring is not allowed to rotate clockwise).
Specifically, (1) when the power input shaft 1 (i.e., the motor) rotates in the forward direction, the control clutch 15 is disengaged, the first gear 17 and the second gear 16 on the power input shaft 1 respectively drive the third gear 4 and the fourth gear 5 to rotate in the reverse direction, as can be seen from the gear diameter (the diameter corresponds to the number of teeth, the larger the diameter is, the more the number of teeth) in fig. 1, the first transmission shaft 3 driven by the third gear 4 rotates in the reverse direction, and the sun gear 2 driven by the fourth gear 5 rotates in the reverse direction, and the speed of the reverse rotation of the sun gear 2 is higher than that of the first transmission shaft 3. Due to the fact that the first transmission shaft 3 rotates reversely, the planet carrier 12 is driven to rotate reversely through the first one-way overrunning clutch 8 and is matched with the reverse rotation of the sun gear 2 to drive the reverse rotation of the gear ring 7 together, the gear ring drives the gear six 14 to rotate forward through the gear five 9, and the power output shaft 13 is driven to rotate at a low speed in a forward direction.
Suppose n3For the input speed of drive shaft one 3, n4For the rotation speed of the sun wheel, n5Is the output rotational speed of the ring gear 7;
order:
Figure BDA0002366043950000071
wherein Z4' is the number of teeth of sun gear 2; z5' is the tooth number of the gear ring; according to an epicyclic gear formula:
Figure BDA0002366043950000072
then it is possible to obtain: -kn5+kn3＝n4-n3；
The formula is deformed to obtain (k +1) n3-n4＝kn5；
If k is 3, this can yield4n3-n4＝3n5；
Then
Figure BDA0002366043950000073
Therefore, as long as
Figure BDA0002366043950000074
Then n is5> 0, so n5And n3、n4In the same direction; since n is4＞n3；
So n is5＜n3；
Figure BDA0002366043950000075
Wherein n is1The rotating speed of the first gear 17;
if Z is6＝Z5n5＞ncWherein n iscThe output rotating speed of the power output shaft 13; n can be obtainedc＜n1I.e. the output rotational speed of the power take-off shaft 13 is smaller than the input rotational speed of the power take-in shaft 1.
(2) When the power input shaft 1 keeps rotating in the forward direction and the clutch 15 is combined, the power input shaft 1 directly drives the power output shaft 13 to rotate in the forward direction, and the power output shaft 13 obtains a forward high-speed rotation output because the speed is not reduced.
According to the formula:
Figure BDA0002366043950000081
wherein n isHThe rotational speed of the planet carrier;
Figure BDA0002366043950000082
if n isH＞n3I.e. no interference occurs;
since n is3＜n1，n5＝n1，n4＞n1；
So that it can be demonstrated that: n isH＞n1(ii) a At this time, the planet carrier 12 is reversely dragged by the ring gear 7 to rotate reversely at a speed higher than the first transmission shaft 3, and the constraint characteristic of the first one-way overrunning clutch 8 prevents the epicyclic gear train from interfering with the power input shaft 1 and the power output shaft 13.
(3) When the power input shaft 1 rotates in the reverse direction, i.e., counterclockwise, the control clutch 15 should be disengaged, in the figure 1, a gear three 4 drives a transmission shaft one 3 to rotate in the positive direction, a gear four 5 drives a sun gear 2 to rotate in the positive direction, due to the constraint characteristic of the first one-way overrunning clutch 8, the transmission shaft I3 rotates in the positive direction and cannot drive the planet carrier 12, the planet carrier 12 has positive rotation torque under the influence of the sun gear 2, but can not rotate in the forward direction due to the constraint characteristic of the second one-way overrunning clutch 11, namely, the fixed planet carrier 12 forms the fixed shaft transmission of the planet wheel, so that the forward rotation of the sun wheel 2 drives the gear ring 7 to rotate in the reverse direction, and the reverse rotation of the gear ring 7 drives the gear six 14 to generate the forward low-speed rotation of the power output shaft 13 through the gear five 9, so that the forward low-speed rotation of the power output shaft 13 is realized.
When the fixed planet carrier 12 forms a dead axle transmission of the planet wheel, as shown in fig. 1, according to a dead axle input-output transmission ratio formula:
Figure BDA0002366043950000091
therefore only need to
Figure BDA0002366043950000092
That is n can be realized1＞n6When the rotating speed of the power input shaft 1 is greater than that of the power output shaft 13, the power output shaft 13 rotates at a low speed in the forward direction.
Wherein Z1 is the number of teeth of gear one 17;
z2 is the number of teeth of gear two 16;
z3 is the number of teeth of gear three 4;
z4 is the number of teeth in gear four 5;
z5 is the number of teeth on gear five 9;
z6 is the number of teeth in gear six 14;
therefore, the variable-speed driving device with bidirectional input and unidirectional output has the advantages that the bidirectional input and unidirectional output of power can be realized only by controlling the combination or the separation of the clutch 15 through the constraint of the epicyclic gear train, the first unidirectional overrunning clutch 8 and the second unidirectional overrunning clutch 11 and the combination of the clutch 15, and the variable-speed driving device with the bidirectional input and the unidirectional output has high-speed and low-speed two-gear output, so that the variable-speed driving device with the bidirectional input and the unidirectional output has a simple structure, is convenient to control, and greatly improves the stability and the reliability of the driving device.
In the above embodiment, the first transmission assembly, the second transmission assembly and the third transmission assembly are all gear set reverse transmission assemblies, that is, transmission assemblies which are driven by gears and have reverse input and output directions are realized. And the output/input speed ratio of the first transmission assembly < the output/input speed ratio of the third transmission assembly < the output/input speed ratio of the second transmission assembly. The gear train transmission assembly has the characteristics of simple structure, stability and reliability, but the first transmission assembly, the second transmission assembly and the third transmission assembly are not limited to the gear train transmission assembly, and in other embodiments, other transmission assemblies such as a chain type transmission assembly, a belt type transmission assembly and the like which satisfy the input-output transmission direction and the transmission ratio can be adopted as the first transmission assembly, the second transmission assembly and the third transmission assembly.
In another embodiment, a vehicle is provided, which includes a driving device for driving the vehicle to run, wherein the driving device is a bidirectional-input one-way-output variable speed driving device described in any one of the above embodiments.
It should be noted that, although the above embodiments have been described herein, the invention is not limited thereto. Therefore, based on the innovative concepts of the present invention, the technical solutions of the present invention can be directly or indirectly applied to other related technical fields by making changes and modifications to the embodiments described herein, or by using equivalent structures or equivalent processes performed in the content of the present specification and the attached drawings, which are included in the scope of the present invention.

Claims (7)

1. A bidirectional-input unidirectional-output variable speed drive device, comprising: the power input shaft, the power output shaft, the turnover system, the clutch, the first one-way overrunning clutch and the second one-way overrunning clutch;
the power input shaft and the power output shaft are coaxially arranged and are connected through a clutch;
the epicyclic gear train comprises a sun wheel, a planet carrier and a gear ring, the planet wheel is rotatably arranged on the planet carrier, the sun wheel is meshed with the planet wheel, and the planet wheel is meshed with the gear ring;
the planet carrier is in transmission connection with the power input shaft through a first transmission assembly, the sun gear is in transmission connection with the power input shaft through a second transmission assembly, and the gear ring is in transmission connection with the power output shaft through a third transmission assembly;
a first one-way overrunning clutch is connected between the planet carrier and the first transmission assembly, a second one-way overrunning clutch is connected between the planet carrier and the shell, and the constraint directions of the first one-way overrunning clutch and the second one-way overrunning clutch are opposite;
when the power input shaft rotates forwards or reversely, the clutch is controlled to be combined or separated, and the power output shaft rotates in a single direction and has two different rotating speeds.
2. A bi-directional input and uni-directional output variable speed drive as claimed in claim 1 wherein the first, second and third drive assemblies are gearset reverse drive assemblies.
3. A bi-directional input and single output variable speed drive as claimed in claim 1 or 2 wherein the output/input speed ratio of the first transmission assembly < the output/input speed ratio of the third transmission assembly < the output/input speed ratio of the second transmission assembly.
4. The variable-speed drive device with bidirectional input and one-way output according to claim 2, wherein the first transmission assembly comprises a first gear and a third gear, the first gear is meshed with the third gear, the first gear is fixedly connected with the power input shaft, the third gear is fixedly connected with an inner ring of a first one-way overrunning clutch, and an outer ring of the first one-way overrunning clutch is fixedly connected with the planet carrier;
the second transmission assembly comprises a second gear and a fourth gear, the second gear is meshed with the fourth gear, the second gear is fixedly connected with the power input shaft, and the fourth gear is fixedly connected with the sun gear;
the third transmission assembly comprises a fifth gear and a sixth gear, the fifth gear is meshed with the sixth gear, the sixth gear is fixedly connected with the power output shaft, and the fifth gear is fixedly connected with the gear ring.
5. A bi-directional input and uni-directional output variable speed drive as claimed in claim 1 wherein the power input shaft rotates in a forward direction, and when the clutch is disengaged, the first uni-directional overrunning clutch drives the planet carrier to rotate in a reverse direction, the sun gear rotates in a reverse direction, the ring gear rotates in a reverse direction, and the ring gear drives the power output shaft to rotate in a forward low speed;
the power input shaft rotates in the positive direction, and when the clutch is combined, the power input shaft drives the power output shaft to synchronously rotate in the positive direction;
the power input shaft rotates reversely, when the clutch is separated, the sun gear rotates forwardly, the first one-way overrunning clutch enables the planet carrier to be separated from the power input shaft, the second one-way overrunning clutch restricts the planet carrier not to rotate forwardly, the gear ring rotates reversely by the forward rotation of the sun gear, and the gear ring drives the power output shaft to rotate forwardly at a low speed.
6. A bi-directional input and uni-directional output variable speed drive as claimed in claim 1 further comprising a drive motor, the rotating shaft of the drive motor being connected to the power input shaft, or the rotating shaft of the drive motor being the power input shaft.
7. A vehicle comprising a driving device for driving the vehicle to run, wherein the driving device is a bidirectional-input unidirectional-output variable-speed driving device according to any one of claims 1 to 6.
CN202010036053.4A 2020-01-14 2020-01-14 Variable-speed driving device with bidirectional input and unidirectional output and vehicle Pending CN111089145A (en)

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CN112125188A (en) * 2020-10-09 2020-12-25 贵州航天林泉电机有限公司 Bidirectional different-speed transmission structure
CN114060479A (en) * 2021-11-16 2022-02-18 贵州凯星液力传动机械有限公司 Transmission mechanism
CN114508571A (en) * 2022-04-18 2022-05-17 溧阳市新力机械铸造有限公司 Special transmission box device of new forms of energy
WO2023284374A1 (en) * 2021-07-10 2023-01-19 广东美的生活电器制造有限公司 Clutch transmission structure, electric motor assembly, cooking utensil and electrical appliance

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112125188A (en) * 2020-10-09 2020-12-25 贵州航天林泉电机有限公司 Bidirectional different-speed transmission structure
WO2023284374A1 (en) * 2021-07-10 2023-01-19 广东美的生活电器制造有限公司 Clutch transmission structure, electric motor assembly, cooking utensil and electrical appliance
CN114060479A (en) * 2021-11-16 2022-02-18 贵州凯星液力传动机械有限公司 Transmission mechanism
CN114508571A (en) * 2022-04-18 2022-05-17 溧阳市新力机械铸造有限公司 Special transmission box device of new forms of energy
CN114508571B (en) * 2022-04-18 2022-07-01 溧阳市新力机械铸造有限公司 Special transmission box device of new forms of energy

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