KR20130109871A - Transmission for electric vehicle with two planetary gear - Google Patents

Transmission for electric vehicle with two planetary gear Download PDF

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Publication number
KR20130109871A
KR20130109871A KR1020120031982A KR20120031982A KR20130109871A KR 20130109871 A KR20130109871 A KR 20130109871A KR 1020120031982 A KR1020120031982 A KR 1020120031982A KR 20120031982 A KR20120031982 A KR 20120031982A KR 20130109871 A KR20130109871 A KR 20130109871A
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KR
South Korea
Prior art keywords
gear
planetary gear
shaft
planetary
motor
Prior art date
Application number
KR1020120031982A
Other languages
Korean (ko)
Inventor
이기채
Original Assignee
지앤씨 유한회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 지앤씨 유한회사 filed Critical 지앤씨 유한회사
Priority to KR1020120031982A priority Critical patent/KR20130109871A/en
Publication of KR20130109871A publication Critical patent/KR20130109871A/en

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/32—Electric motors actuators or related electrical control means therefor
    • F16H2061/323—Electric motors actuators or related electrical control means therefor for power assistance, i.e. servos with follow up action

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

The present invention relates to a vehicle transmission system equipped with two planetary gears, and more particularly, including a main motor, a submotor, and a connection gear connecting the main motor and the submotor to operate the submotor. The present invention relates to a vehicle transmission system equipped with two planetary gears, which are shifted depending on whether the vehicle is shifted while reducing power consumption.

Description

Transmission for Electric Vehicle with two planetary gear}

The present invention relates to a vehicle transmission system equipped with two planetary gears, and more particularly, including a main motor, a submotor, and a connection gear connecting the main motor and the submotor to operate the submotor. The present invention relates to a vehicle shifting system equipped with two planetary gears, which are shifted depending on whether the vehicle shifts or not.

1 is a schematic configuration diagram of a conventional automatic transmission system, in which a differential gear device 30 is connected between wheels 10 and 20 on both sides, and a secondary gear 40 is fitted to an output side of the differential gear device 30. And a synchro mechanism 60 on the secondary shaft 50 including the secondary gear 40.

In addition, the actuator motor 70 is connected to the synchro mechanism 60 so as to drive the synchro mechanism 60, and the second gear 80 and the first gear 90 are fitted to the respective gears of the secondary shaft 50. , The second gear 80 and the first gear 90 is configured to be coupled to the primary shaft (100).

In addition, the primary shaft 100 is configured by connecting to the traction motor 110.

This synchronizer shifting method has a small number of shift steps, making it difficult to determine the synchronizer capacity and difficulty in arranging components related to control.

There is a problem that is vulnerable to shifting shocks occurring during shifting.

The present invention has been made to solve the above problems, and an object thereof is to provide a vehicle shifting system equipped with two planetary gears that can facilitate shifting while reducing power consumption.

A vehicle shifting system equipped with two planetary gears of the present invention for achieving the above object includes a main motor, a submotor, and a connecting gear connecting the main motor and the submotor to the submotor. The shift is characterized in that the operation.

According to the vehicle shifting system equipped with two planetary gears of the present invention as described above, the following effects are obtained.

It includes a main motor, a submotor, and a connecting gear connecting the main motor and the submotor, and are shifted according to whether the submotor is operated, thereby reducing power consumption.

1 is a configuration diagram of a conventional conventional automatic transmission system
Figure 2 is a perspective view of a vehicle shift system provided with two planetary gears according to a preferred embodiment of the present invention.
Figure 3 is an exploded perspective view of a vehicle shift system with two planetary gears of Figure 2;
4 is a perspective view of the combined state in a state in which the second side housing is removed from the vehicle shift system provided with the two planetary gears of FIG.
5 is a cross-sectional view taken along line AA of FIG.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

For reference, the same components as those of the conventional art will be described with reference to the above-described prior art, and a detailed description thereof will be omitted.

As shown in Figures 2 to 5, the vehicle transmission system equipped with two planetary gears of the present embodiment, the main motor 200, the sub-motor 700, the main motor 200 and the sub Including a connecting gear connecting the motor 700, the sub-motor 700 is shifted according to whether or not the operation.

As shown in FIG. 2, the main motor 200 rotates the output shaft 600 to drive the vehicle.

As shown in FIG. 3, the sub-motor 700 is provided with a motor having a small power consumption, and may be provided with, for example, a motor consuming about 10W of power.

The vehicle transmission of the present invention is shifted according to whether or not the sub-motor 700 is operated, and can shift while reducing power consumption.

The connection gear connects the main motor 200 and the submotor 700.

The connecting gear includes a planetary gear, a worm wheel 340 connected to the planetary gear, and a worm gear 350 meshed with the worm wheel 340.

The planetary gear is connected to the shaft of the main motor 200, and the worm gear 350 is connected to the shaft of the submotor 700.

The planetary gear may include a first sun gear 310, a first planetary gear 331 meshed with the first sun gear 310, and a second planetary gear 332 connected to the first planetary gear 331. , A carrier 333 connected to the first planetary gear 331 and the second planetary gear 332, and a second sun gear 320 meshed with the second planetary gear 332.

The first sun gear 310 is axially coupled to the first transmission gear 410 which transmits power toward the output.

Power is transmitted to the output shaft 600 through a second transmission gear 420 that transfers power between the first transmission gear 410 and the differential gear 500.

The carrier 333 is formed in a plate shape, and is coupled to the shaft of the main motor 200 through the connecting shaft 334.

The carrier 333 has through-holes through which shafts connecting the first planetary gear 331 and the second planetary gear 331 pass through the upper and lower portions thereof.

The first planetary gear 331 and the second planetary gear 331 are disposed on both sides of the carrier 333, respectively, and are coupled to each other.

The first planetary gear 331 and the second planetary gear 331 are shaft-jointed through the shaft joint member 360.

As shown in FIGS. 3 and 5, the shaft fitting member 360 includes a ring member 361 and a taper member 362 and a ring member 361 and a taper member 362 fitted to the ring member 361. And a bolt 363 that is fastened to it. At least one of the ring member 361 and the tapered member 362 is cut off at one side thereof, and is in close contact with the gear and the shaft when the bolt 363 is fastened.

The ring member 361 is formed in a ring shape, an insertion hole into which the taper member 362 is inserted is formed therein, and a bolt fastening hole to which the bolt 363 is fastened along a circumference thereof is formed. The insertion hole is formed to be narrower toward the opposite direction of the inlet in which the taper member 362 is inserted.

As shown in FIG. 6, the taper member 362 has a taper portion 364 formed at one end thereof to be tapered to correspond to the insertion hole, and a flange 365 is formed at the other end thereof.

The flange 365 has a bolt fastening hole for fastening the bolt 363 is formed.

In addition, the taper member 362 is formed with a shaft through hole through which the shaft of the first planetary gear 331 passes.

The second planetary gear 331 is formed with a shaft through hole through which the shaft of the first planetary gear 331 penetrates, and a seating groove in which the shaft joint member 360 is seated is formed to communicate with the shaft through hole. .

The first planetary gear 331 and the second planetary gear 331 are assembled through the following assembling process.

After the shaft of the first planetary gear 331 passes through the carrier 333, the shaft is inserted into the shaft through hole of the second planetary gear 331. Subsequently, the ring member 361 of the shaft fitting member 360 is seated in the seating groove, the taper member 362 is inserted into the insertion hole of the ring member 361, and then the bolt 363 is attached to the ring member 361. And a taper member 362. The assembly position of the first planetary gear 331 and the second planetary gear 331 can be precisely adjusted by the fastening degree of the bolt 363.

When the shaft joint member 360 is used as described above, the assembly position of the planetary gears, which are provided in plural, can be easily adjusted, thereby preventing mismatching of the planetary gears.

Therefore, one of the planetary gears forms a key groove and inserts the key into the key groove to make the shaft joint, and the other uses the shaft joint member 360 to easily adjust the position to the planetary gear which is shaft-joined using the key. Can be.

The second sun gear 320 is connected to the worm wheel 340 by shaft coupling.

An oilless washer 800 is disposed between the worm wheel 340 and the housing in which the connecting shaft 334 serving as the shaft of the worm wheel 340 is installed.

When the worm gear 350 rotates due to the oilless washer 800, the play caused by the thrust generated between the worm gear 350 and the worm wheel 340 may be prevented.

The first transmission gear 410, the first sun gear 310, the carrier 333, the second sun gear 320, and the worm wheel 340 are disposed on the coaxial line through the connecting shaft 334.

The connecting gear is provided in this way, the interaxial distance can be secured so that the main motor 200 of various outputs can be applied, the number of element gears is reduced, the system is simplified, cost reduction and assembly is easy, and the required ground clearance It can be secured, and the two-axis can ensure the safety of the main motor 200.

A housing 100 surrounding the connecting gear, the first and second transmission gears 410 and 420, and the differential gear 500 may be provided.

The housing 100 includes a first side housing 110 connected to the housing of the main motor 200, and a second side housing 120 coupled to the first side housing 110.

The connecting gear and the first transmission gear 410 are disposed in the upper portion of the housing 100, and the second transmission gear 420 and the differential gear 500 are disposed in the lower portion of the housing 100, and have an elliptical shape to correspond to the gear shape. do.

Therefore, the connecting shaft 334 passes through the upper portion of the housing 100 and the output shaft 600 passes through the lower portion of the housing 100.

The first side housing 110 is formed in a cylindrical shape of an ellipse to surround one side of the gear (the main motor 200 side).

The second side housing 120 is formed to surround the other side of the gear. The second side housing 120 is formed to protrude in a cylindrical shape according to the degree of protruding of the gear toward the second side housing 120 is formed stepped. Thus, the housing 100 is formed, there is an advantage that the device is compact.

In addition, the sub-motor 700 is disposed on the outside of the second side housing 120 so that the shaft intersects with the connecting shaft 334. Furthermore, ribs are formed in the protruding portions of the second side housing 120 for installing the sub-motor 700 and the worm gear 350, so that durability may be maintained even when the sub-motor 700 is installed.

Meanwhile, a seating protrusion 122 through which a bearing may be seated is formed around a through hole through which the output shaft 600 of the second side housing 120 passes, and ribs are formed and reinforced on an outer circumferential surface of the seating protrusion 122.

It may include a controller (not shown) for controlling the sub-motor 700.

The control unit controls the sub-motor 700 according to the required torque of the vehicle.

For example, the controller decelerates through the sub-motor 700 when the vehicle requires low-speed driving or travels on a steep road. The controller controls the reduction ratio to 5.5: 1 during normal driving, and drives the sub-motor 700 to achieve a reduction ratio of 8.8: 1 when driving on a climbing road and when high torque is required.

In detail, the control unit controls the sub-motor 700 in a proportional control manner in synchronization with the RPM of the main motor 200. When decelerating, the rotational direction of the sub-motor 700 is rotated in a direction opposite to the main motor 200. The shifting shock may be minimized during shifting using this control method.

In addition, the structure of the housing 100 and the shape and size of the bearing may be selected by estimating the amount of deformation occurring under actual driving conditions through simulation. In addition, the durability of the apparatus may be improved by reinforcing the carrier 333 and selecting a bearing, which is a point at which maximum deformation may occur.

Hereinafter, the operation of the present embodiment having the above-described configuration will be described.

When the main motor 200 is operated, the connecting shaft 334 rotates, and the carrier 333 rotates as the connecting shaft 334 rotates. As the carrier 333 rotates, the first and second planetary gears 331 and 332 simultaneously rotate.

If the submotor 700 does not operate, the worm gear 350 is in a stopped state. Since the worm gear 350 and the worm wheel 340 cannot be reversed, the worm wheel 340 and the second sun gear 320 are also stopped.

The second planetary gear 332 is meshed with the second sun gear 320 so that the first and second planetary gears 331 and 332 also rotate. Since the first planetary gear 331 is meshed with the first sun gear 310, the first transmission gear 410 is rotated so that power is transmitted to the output.

On the other hand, when the sub-motor 700 is operated in the state in which the main motor 200 is operating, the worm gear 350 is rotated in the opposite direction to the main motor 200. As the worm wheel 340 engaged with the worm gear 350 rotates, the second sun gear 320 also rotates opposite to the carrier 333. As a result, the rotation speed of the second planetary gear 331 is decelerated when the submotor 700 is operated, rather than when the submotor 700 is not operated. That is, the rotation speed of the output shaft 600 is reduced and the transmission torque is increased.

The operation of the sub-motor 700 may be controlled by the controller.

The control unit may receive a signal from a sensor for detecting a user's command input or a climbing angle of the vehicle to operate the sub-motor 700 to decelerate according to a required torque of the vehicle.

It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the present invention as defined by the following claims .

DESCRIPTION OF REFERENCE NUMERALS
100: housing 200: main motor
310: first sun gear 320: second sun gear
331: first planetary gear 332: second planetary gear
333: carrier 340: worm wheel
350: worm gear 700: sub motor

Claims (1)

Main motor;
Submotor;
It includes a connection gear for connecting the main motor and the sub-motor,
The connecting gear includes a planetary gear, a worm wheel connected to the planetary gear, and a worm gear meshed with the worm wheel.
The planetary gear may include a first sun gear, a first planetary gear meshed with the first sun gear, a second planetary gear connected to the first planetary gear, the first planetary gear and the second planner. A carrier connected to the battery gear and a second sun gear meshed with the second planetary gear;
The first planetary gear and the second planetary gear are shaft-joined through a shaft joint member,
The shaft joint member includes a ring member, a tapered member fitted to the ring member, and a bolt fastened to the ring member and the tapered member, and at least one of the ring member and the tapered member has one side cut off. Vehicle shifting system equipped with two planetary gears.
KR1020120031982A 2012-03-28 2012-03-28 Transmission for electric vehicle with two planetary gear KR20130109871A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020120031982A KR20130109871A (en) 2012-03-28 2012-03-28 Transmission for electric vehicle with two planetary gear

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020120031982A KR20130109871A (en) 2012-03-28 2012-03-28 Transmission for electric vehicle with two planetary gear

Publications (1)

Publication Number Publication Date
KR20130109871A true KR20130109871A (en) 2013-10-08

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Application Number Title Priority Date Filing Date
KR1020120031982A KR20130109871A (en) 2012-03-28 2012-03-28 Transmission for electric vehicle with two planetary gear

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104279321A (en) * 2014-09-18 2015-01-14 范兆军 Rear axle gear shifting speed change device of electric vehicle
CN104329455A (en) * 2014-11-11 2015-02-04 合肥工业大学 Motor-driven planetary gear train gear shifting mechanism
CN104979950A (en) * 2015-07-24 2015-10-14 徐州南普机电科技有限公司 Automatic gear shifting motor
CN105864367A (en) * 2016-05-25 2016-08-17 湖南江麓容大车辆传动股份有限公司 Automatic transmission for electric vehicle and vehicle
CN106523691A (en) * 2017-01-09 2017-03-22 山东理工大学 Electric vehicle two gear automatic transmission with drive-by-wire centrifugal ball arm jointing device

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104279321A (en) * 2014-09-18 2015-01-14 范兆军 Rear axle gear shifting speed change device of electric vehicle
CN104329455A (en) * 2014-11-11 2015-02-04 合肥工业大学 Motor-driven planetary gear train gear shifting mechanism
CN104979950A (en) * 2015-07-24 2015-10-14 徐州南普机电科技有限公司 Automatic gear shifting motor
CN105864367A (en) * 2016-05-25 2016-08-17 湖南江麓容大车辆传动股份有限公司 Automatic transmission for electric vehicle and vehicle
CN106523691A (en) * 2017-01-09 2017-03-22 山东理工大学 Electric vehicle two gear automatic transmission with drive-by-wire centrifugal ball arm jointing device

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