WO2018043855A1

WO2018043855A1 - In-wheel type two-stage transmission

Info

Publication number: WO2018043855A1
Application number: PCT/KR2017/002869
Authority: WO
Inventors: 이규정
Original assignee: 이엠티씨 주식회사
Priority date: 2016-08-29
Filing date: 2017-03-17
Publication date: 2018-03-08
Also published as: CN109073049A; CN109073049B

Abstract

The present invention relates to an in-wheel type two-stage transmission, and the objective of the present invention is to provide an in-wheel type two-stage transmission having a simple structure in which the transmission is integrally coupled to the inside of a tire wheel, quickly transmitting the driving power of a sun gear part to the wheel through a planetary gear part, and enabling a gear shift to be easily performed in two stages by means of a clutch part. The present invention comprises: a power part; the sun gear part to which the driving power of the power part is transmitted; the planetary gear part connectedly provided to the wheel and to which the driving power of the sun gear part is transmitted; a ring gear part connectedly provided to the planetary gear part, and provided such that reverse rotation thereof is restricted by a one-way bearing; and the clutch part having one side connected to the power part or to the sun gear part connectedly provided to the power part, and having another side connectedly provided to the wheel or to the planetary gear part integrally connected to the wheel, such that the clutch part is operated so as to allow the sun gear part, the planetary gear part, and the ring gear part to integrally rotate, wherein the driving power of the power part is transmitted to the wheel through the sun gear part and the planetary gear part in a state in which the reverse rotation of the ring gear part is restricted by the one-way bearing, such that low-speed traveling is performed, and the sun gear part, the planetary gear part, the ring gear part and the wheel are integrally rotated by the driving power of the power part through the operation of the clutch part such that speed-increased traveling is performed.

Description

In-wheel type two-speed

The present invention relates to an in-wheel type two-speed gearbox, which is integrally installed in a wheel, and the driving force of the power unit is input to the planetary gear unit through the sun gear unit and transmitted to the output shaft, and the input driving force is operated by the clutch unit. It relates to an in-wheel type two-speed transmission that can be shifted and transmitted to the output shaft.

Recently, energy conservation policies are being promoted due to the depletion of energy resources and the protection of the global environment due to air pollution and global warming due to the exhaust of automobiles. To solve these problems, electric vehicles, hybrid electric vehicles, fuel cell electricity There is a growing interest in environmentally friendly cars such as cars.

In general, an electric vehicle uses electricity as a fuel, unlike a gasoline engine, and uses an electric motor as a power unit. Thus, an electric vehicle is a pollution-free vehicle that emits no exhaust gas. Although the power transmission structure mainly used to drive the driving wheels by decelerating the drive speed has been used, in recent years, it is possible to transmit the power from the electric motor to the driving wheels more efficiently, thereby extending the driving distance of the vehicle and improving the driving performance. Research is active.

Conventional electric vehicles are excellent in the characteristics of the motor has been widely used reducer having a single gear ratio, but when using only the reducer, there is a problem that the capacity of the motor must be relatively large, in recent years to operate the motor as efficiently as possible Two-speed gearboxes are widely used.

However, the conventional two-speed gearbox requires two friction clutches or fluid clutches to implement the two-speed gearbox, which increases the volume of the transmission, increases manufacturing costs, and increases power transmission efficiency. There was a problem of deterioration.

In addition, in the conventional two-speed gearbox, a plurality of external gears, a locking device, a shift mechanism, and the like are applied, and the structure thereof is very complicated, assembly is deteriorated, the number of components is increased, and the connection relationship is complicated. As a result, a power loss phenomenon in which power of the power unit is not quickly transmitted to the output shaft is generated, and the shift performance is deteriorated.

In particular, the conventional two-speed transmission has a problem in that the shift shock and friction loss occurs when shifting from the first gear to the second gear, reducing the ride comfort of the occupant and hindering safe driving.

In addition, the conventional two-speed gearbox is installed separately on the outside of the wheel, and the output shaft is configured to be connected to the wheel, to secure a space for installing the two-speed gearbox on the frame, thereby reducing the size of the device There were various problems such as limitations.

(Prior art document)

(Patent Document 1) Publication No. 10-2016-0005209 (2016.01.14)

(Patent Document 2) Registered Patent Publication No. 10-1532834 (2015.06.24)

(Patent Document 3) Registration Patent Publication No. 10-1350772 (2014.01.07)

(Patent Document 4) Published Patent Publication No. 1997-0046346 (1997.07.26)

An object of the present invention has a simple structure that is integrally coupled within the wheel of the wheel, the driving force of the sun gear portion is quickly transmitted to the wheel through the planetary gear portion, the in-wheel that can be easily shifted in two stages by the clutch portion In-wheel type two-speed gearbox is provided.

The present invention power unit; A sun gear unit to which driving force of the power unit is transmitted; A planetary gear unit for transmitting driving force to the sun gear unit and being connected to the wheel; A ring gear unit connected to the planetary gear unit and installed to restrain the reverse rotation by the unidirectional bearing; One side is connected to the power unit or the sun gear connected to the power unit, the other side is connected to the wheel or planetary gear unit integrally connected to the wheel, the clutch unit is operated to rotate the sun gear unit, the planetary gear unit and the ring gear unit integrally Including, the driving force of the power unit is transmitted to the wheel through the sun gear portion, the planetary gear portion in a state in which the reverse rotation of the ring gear portion is constrained by the unidirectional bearing, and the low speed driving is performed, and the sun gear portion, the planetary gear portion, and the ring machine are operated by the clutch portion. The fisherman and the wheel are integrally rotated by the driving force of the power unit, and are configured to increase speed driving.

According to the present invention, the driving force of the power unit is transmitted to the wheel by the sun gear input and the planetary gear carrier output method, and thus the configuration is simpler than the existing device, and thus the power transmission efficiency is excellent, and the power loss is low, thereby improving the energy efficiency. have.

The present invention has a compact structure in which the sun gear unit, the planetary gear unit, the ring gear unit, and the clutch unit are integrally connected, and are integrated to connect the power unit to the sun gear unit, which can be installed integrally in the wheel of the vehicle (In wheel type). Do.

When the present invention is applied to an electric vehicle, the fastest speed performance of the vehicle is improved compared to the motor speed reducer, the acceleration performance and the climbing performance are improved, as well as the cost can be reduced and the weight can be minimized by minimizing the number of components. .

According to the present invention, when the power unit is started and the sun gear unit rotates, the output is made to the wheel through the planetary gear unit without loss, thereby increasing power transmission efficiency of the entire rpm section.

According to the present invention, a two-stage shifting can be performed dynamically according to a driving state, thereby improving output and performance of the vehicle.

In the centrifugal clutch according to the present invention, the first and second rotors of the clutch are rotated integrally by the roller which is rotationally driven, so that a loss due to friction is not generated, and thus driving force of the power unit is directly transmitted to the wheel without power loss. .

The present invention improves the driving performance of the electric vehicle by providing a gear ratio of two stages, and it is possible to improve the fuel efficiency of the electric vehicle and increase the driving distance by minimizing the power consumption.

The present invention can be installed in a device driven by an electric drive, an electric drive vehicle, an electric drive, and the like, and can be easily applied to a pre-produced device.

1 is an exemplary view showing the overall configuration according to the present invention

2 is an exemplary view showing an internal configuration according to the present invention

Figure 3 is an exemplary view briefly showing the configuration according to the present invention

Figure 4 is an exemplary view showing the configuration of the power unit and the clutch unit (electronically controlled) of the present invention

5 is another exemplary view briefly showing a configuration according to the present invention.

Figure 6 is an exemplary view showing the configuration of the centrifugal clutch according to the invention

Figure 7 is an exemplary view showing an operating state of the present invention centrifugal clutch

Figure 8 is an exemplary view showing a link portion connected state of the present invention centrifugal clutch

9 is an exemplary view showing a link portion operating state of the present invention centrifugal clutch.

Figure 10 is a simplified illustration showing the configuration according to the invention (including one-way clutch)

11 is an exemplary view showing a modified configuration of the present invention

12 is a simplified example showing the configuration of FIG.

(Explanation of the sign)

10: power unit 20: sun gear unit

(21): Input shaft (22): Sun gear

30: clutch portion 35: unidirectional clutch

(40): Planetary gear unit (41): Planetary gear

(42): Planetary gear carrier 50: Central axis

(60): ring gear portion 61: ring gear

(62): gear housing (70): electronically controlled clutch

71: clutch first rotor 72: clutch second rotor

(73): clutch stator 80: centrifugal clutch

(81): clutch first rotor (81a): outer peripheral surface

(82): clutch second rotor (82a): receiving groove

(82b): Inner circumference (83): Interspace

(84): clutch operating portion (84a): roller

(84b): support (84c): mobile

(84d): support spring (85): tight contact

85a: support surface 85b: inclined surface

(841c): hanging jaw

(851a): top (851b): bottom

852a: Outer End 852b: Inner End

(86): mounting hole (86a): one side

(86b): other side (90,91,95): unidirectional bearing

92: bearing 96: link portion

(97): connection link (98): center rotation link

(100): two-speed transmission (110): first frame

120: second frame 130: wheel

(131): tire (140): wheel dust cover

150: wheel cover 151: projection

160: brake unit

1 is an exemplary view showing an overall configuration according to the present invention, Figure 2 is an exemplary view showing an internal configuration according to the present invention, Figure 3 is an exemplary view briefly showing the configuration of Figure 2, Figure 4 the present invention Exemplary view showing the configuration of the power unit and the clutch unit (electronically controlled), Figure 5 is a simplified view showing the configuration according to the present invention (centrifugal clutch), Figure 6 is a configuration of the centrifugal clutch according to the present invention 7 is an exemplary view showing an operating state of the present invention centrifugal clutch, Figure 8 is an illustration showing a link portion of the present invention centrifugal clutch, Figure 9 is a present invention centrifugal clutch Figure 10 is an exemplary view showing the operation state of the link, Figure 10 is a simplified illustration showing the configuration according to the present invention (including one-way clutch), Figure 11 is an illustration showing a modified configuration of the present invention, Figure 12 is a view 11 is a schematic view showing the configuration of 11,

The present invention provides an in-wheel type two-speed transmission; The power unit 10, the sun gear unit 20 to which the driving force of the power unit 10 is transmitted, the planetary gear unit 40 to which the driving force of the sun gear unit 20 is transmitted and connected to the wheel 130, and the planetary unit The ring gear part 60, which is installed to be connected to the fisherman and is installed to restrain the reverse rotation by the unidirectional bearing, the sun gear part 20, the planetary gear part 40 and the ring gear part 60 by the driving force of the power unit 10. Including a clutch unit 30 to rotate integrally,

The driving force of the power unit 10 is transmitted to the wheel 130 through the sun gear unit 20 and the planetary gear unit 40 in a state in which the reverse rotation of the ring gear unit 60 is constrained by the unidirectional bearing 90, thereby driving at low speed. This is done,

By the operation of the clutch unit 30, the sun gear unit 20, the planetary gear unit 40, the ring gear unit 60, and the wheel 130 are integrally rotated by the driving force of the power unit 10 to increase speed driving. have.

The present invention, for example, the power unit 10, the sun gear unit which is connected to one end of the input shaft 21 to the power unit 10 and the sun gear 22 integrally formed on the other side of the input shaft penetrating the wheel 130 (20), a planetary gear portion (40) having a plurality of planetary gears (42) receiving a driving force from the sun gear 22, the planetary gear carrier 41 is fixedly installed on the wheel 130, and a plurality of One side is connected to the ring gear unit 60 installed to receive the driving force from the planetary gear 42 and the sun gear unit 20 connected to the power unit 10 or the power unit 10, the wheel 130 or wheel One side is connected to the planetary gear unit 40 integrally connected to the 130, the clutch unit 30 is installed to penetrate through the power unit 10, the sun gear unit 20 and the ring gear unit 60, The ring gear part 60 is supported by the unidirectional bearing 90, and includes a central axis 50 fixed at both ends thereof to the first and

second frames

110 and 120.

In operation of the clutch unit 30, the wheel 130 on which the planetary gear unit 40 is installed is coupled to the power unit 10, such that the sun gear unit 20, the planetary gear unit 40, the ring gear unit 60, and the wheel ( 130 is integrally rotated by the driving force of the power unit 10 to increase speed.

1 and 10, the unidirectional clutch 35 is further installed to be positioned between the planetary gear portion 40 and the sun gear portion 20, and the unidirectional clutch 35 is a sun gear. It operates to restrain forward rotation of the planetary gear carrier 41 with respect to the negative input shaft 21.

The power unit 10 refers to a driving means for generating power such as a motor, an electric motor, and is installed to be located in the wheel 130.

Since the power unit 10 is sufficient to generate power, the configuration thereof is not limited, but as shown in FIG. 4, for example, the motor stator 12 is connected to the central shaft 50 to be installed. The rotor 11 may be installed to be connected to the sun gear unit 20. In addition, the motor rotor 11 may be configured to replace the motor case to realize the function.

The sun gear unit 20 includes an input shaft 21 having one end connected to the power unit 10 to receive a driving force, and a sun gear 22 integrally formed at the other side of the input shaft 21.

The input shaft 21 has a central shaft 50 penetrated and supported by a bearing, and one end thereof is integrally connected to one side of the power unit, for example, the motor rotor 11, so that the driving shaft rotates when the power unit is driven. In addition, one side of the clutch unit may be connected to the input shaft 21.

The clutch unit 30 is installed between the wheel 130 and the power unit 10, and is operated to transmit the driving force of the power unit 10 to the wheel 130, the electronically controlled clutch 70 or centrifugal force type It may be made of a clutch (80).

The electronically controlled clutch 70 is configured such that the two clutch rotors are closely coupled to each other so that power is transmitted, or if the clutch clutch is more than a predetermined speed, the two clutch rotors are automatically adhered to each other so as to transmit power. It may include all.

Such an electronically controlled clutch 70 is not limited in configuration, but as an example, as illustrated in FIGS. 2 to 4, the motor rotor 11 of the power unit 10 or the input shaft 21 of the sun gear unit is illustrated. A clutch first rotor 71 coupled integrally, a clutch second rotor 72 integrally fixed to the wheel 130 or the planetary gear portion 40 so as to correspond to the clutch first rotor 71, and a center; To include a clutch stator 73 connected to the shaft 50 or the motor stator 12,

The clutch first rotor 71 and the clutch second rotor 72 are closely coupled by the operation of the clutch stator 73, so that the driving force of the power unit 10 may be transmitted to the wheel 130.

In this case, the clutch first rotor 71 may be replaced by utilizing one side of the motor rotor 11. That is, one side of the motor rotor 11 corresponding to the clutch first rotor 71 may be deformed so as to have a function of the clutch first rotor 71.

Since the configuration and operation of such an electronically controlled clutch is a known technique, a detailed description thereof will be omitted.

The centrifugal clutch 80 is automatically operated by the centrifugal force to transmit the driving force of the power unit 10 to the wheel 130, as shown in Figures 5 to 9, the motor rotor 11 of the power unit Or the wheel 130 or the planetary gear part 40 to have a clutch first rotor 81 integrally coupled to the input shaft 21 of the sun gear part, and the space between the clutch first rotor 81 and the space 83. Rotational force of the clutch first rotor 81 which is connected to the clutch first rotor 81 so as to be located between the clutch second rotor 82 fixedly installed on the clutch and the clutch first and

second rotors

81 and 82. It is automatically operated by the clutch includes a clutch operating portion 84 for connecting the first and

second rotors

81 and 82 to be integrated.

The clutch first rotor 81 is integrally connected to the motor rotor 11 of the power unit or the input shaft 21 of the sun gear unit so as to rotate concentrically with the motor rotor 11 or the sun gear 22 of the power unit, and the outer peripheral surface 81a. ) Is provided with a close contact portion 85 having a support surface 85a and an inclined surface 85b, and an installation hole 86 to which the clutch operating portion 84 is connected is provided with a predetermined length and formed therein. .

The support surface 85a is formed such that an upper side thereof is connected to the outer circumferential surface 81a of the clutch first rotor, and a lower end thereof is connected to the inclined surface 85b, and has a vertical surface facing the center of the clutch first rotor 81. Or a curved surface having a predetermined concave curvature.

The support surface 85a is preferably made of a curved surface of concave curvature for the stable mounting of the clutch operating portion 84, the height (h) of the support surface is formed to be larger than the roller diameter (D) of the clutch operating portion. .

The inclined surface 85b may be formed in a curved or straight shape so that the roller 84a of the clutch operating portion 84 can be moved outward by the rotational force of the clutch first rotor 81. For example, the inclined surface 85b is formed in an involute curve or a taper shape, and is preferably formed in an involute curve.

That is, the inclined surface (85b) is formed so that one end is connected to the support surface (85a) and the other end is connected to the outer peripheral surface (81a) of the clutch first rotor, clutch operation by the rotational force of the clutch first rotor (81) The negative roller 84a can be moved in the direction of the outer circumferential surface 81a of the clutch first rotor.

At least one contact portion 85 configured as described above is formed on the outer circumferential surface 81a of the clutch first rotor, and a plurality of the close contact portions 85 are continuously formed to face one direction on the entire circumferential surface of the clutch first rotor 81. In this case, the first rotor 81 of the clutch is formed in a sawtooth shape by the outer peripheral surface itself by a plurality of contact portion (85).

The installation hole 86 is the clutch operating portion 84 is connected to the installation, one side (86a) toward the inner side of the first clutch of the clutch 81, the other side (86b) the outer side of the clutch first rotor (82) It is formed with a predetermined length so as to face.

The installation hole 86 may have a straight long hole shape or may have a curved long hole shape, and is preferably formed in a straight long hole shape.

The clutch second rotor 82 is integrally connected to the wheel 130 to have a clutch first rotor 81 and an interspace 83.

The clutch second rotor 82 includes a receiving groove 82a so that the clutch first rotor 81 is positioned therein, and the roller 84a of the clutch operating portion contacts the circumference of the receiving groove 82a. An inner circumferential surface 82b is formed.

When the interspace 83 is assembled such that the clutch first rotor 81 is located in the accommodation groove 82a of the clutch second rotor, an interval between the inner circumferential surface 82b of the accommodation groove to the contact portion inclined surface 85b is provided. Means a space formed by the, the interspace 83 is made of a shape that the interval between the inner circumferential surface 82b and the inclined surface 85b of the receiving groove is gradually narrowed.

That is, when the clutch first rotor 81 is assembled into the receiving groove 82a of the clutch second rotor, the clutch first rotor is formed on the inner circumferential surface 82b of the clutch second rotor by the shape of the inclined surface 85b of the close contact portion. The distance between the other end of the inclined surface (or the inclined surface outer end) of the rotor is smaller than the roller diameter D of the clutch operating portion, and from the inner circumferential surface of the second clutch rotor to the one end of the inclined surface of the clutch first rotor (or the inclined surface inner end). The interspace 83 is formed such that the space between the larger than the roller diameter (D) of the clutch operating portion.

The clutch operation unit 84 is operated by the rotational force of the clutch first rotor 81 to perform an operation of making the clutch first rotor 81 and the clutch second rotor 82 come into close contact so as to be integrally rotated. In this way, the clutch operating portion 84 configured as described above has a feature that there is no loss caused by friction.

The clutch operating portion 84 includes a roller 84a installed to be located in the close contact portion 85 of the clutch first rotor, a support 84b connected to one side so that the roller 84a is rotatable, and a clutch agent. Mounting hole 84c installed so as to be located in the installation hole 86 of one rotor and hingedly installed on the other side of the support stand 84b, and an installation hole so as to be located between the movable stand 84c and the other side 86b of the installation hole. It is provided in the 86, and the support spring 84d which elastically supports the movable stand 84c is included.

That is, the clutch operating portion 84 is rotatably connected to the roller (84a) on one side of the support (84b), the other side of the support (84b) on both ends of the mobile (84c) through the installation hole 86 It is rotatably connected, and the movable stand 84c is supported by the support spring 84d in the installation hole 86.

When the clutch actuating unit 84 configured as described above has the rotational force of the clutch first rotor 81 less than a predetermined value, the roller 84a does not move and is inoperative, and the rotational force of the clutch first rotor 81 is a constant value. In this case, the roller 84a is moved by the centrifugal force and is pinched between the clutch first and second rotors, thereby performing the function of causing the clutch first and

second rotors

81 and 82 to be integrally rotated.

That is, the clutch operating portion 84, when the rotational force of the clutch first rotor 81 is less than a predetermined value by the elastic support force of the support spring 84d so that the movable table 84c is located on one side 86a of the installation hole. The roller 84a to which the movable stand 84c is connected by the support stand 84b maintains a state in which the moving table 84c is in contact with the support surface 85a and the inclined surface 85b of the close contact portion 85 simultaneously. At this time, the clutch first rotor 81 is rotated integrally with the motor rotor 11 and the input shaft 21 of the sun gear without interference caused by the roller 84a.

In addition, when the rotational force of the clutch first rotor 81 rises above a certain value, the roller 84a is moved along the inclined surface 85b of the close contact portion by the centrifugal force, and the movable table 84c is supported by the support spring 84d. ) And moves from one side 86a of the installation hole to the other side 86b. At this time, the roller 84a moved along the inclined surface of the close contact portion, as shown in FIG. 7, the interval between the inclined surface and the inner circumferential surface of the clutch housing is gradually narrowed, the inclined surface 85b of the close contact portion at a portion smaller than the diameter of the roller Since it is sandwiched between and the inner circumferential surface (82b) of the clutch second rotor, the clutch first rotor 81 and the clutch second rotor 82 is integrally coupled to rotate. That is, the rotational force of the clutch first rotor 81 is transmitted to the clutch second rotor 82.

The predetermined value of the rotational force of the clutch first rotor 81 for operating the clutch operating portion 84 is determined by the elastic force of the support spring 84d, the movable table 84c, and the roller 84a in consideration of the capacity of the power portion and the required output amount. Since it is calculated by the calculation or the program according to the weight of the), it is not particularly limited.

For example, the clutch operating unit 84 may be set to a predetermined value to be operated when reaching more than about 50% of the maximum output speed of the power unit, more specifically, the rotational force of the clutch first rotor is 500 ~ 1,000rpm It may be designed to operate when a certain value set in the section is reached.

In addition, the clutch actuating unit 84 is provided by the link unit 96 as shown in FIGS. It may be configured to be connected to each other.

The link portion 96 is a central rotary link 98 is installed so as to support the bearing on the input shaft 21, and one end of each of the central rotary link 98 is hinged and rotated on the moving table 84c of the clutch operating portion It is to include a connection link 97 is connected to the other end as possible.

The link portion 96 configured as described above has a rotational force of the clutch first rotor 81 when a plurality of clutch operating portions 84 are provided between the clutch first rotor 81 and the clutch second rotor 82. When one side of the clutch operating part is operated, the rotation operation of the central rotary link 98 by the connecting link 97 connected thereto, and a plurality of other connecting links 97 connected thereto by the rotation of the central rotary link 98 It is operated at the same time, so that the operation of the plurality of clutch operating portion is synchronized.

In addition, the centrifugal clutch 80 is configured to further include a ball stopper portion 87, as shown in Figs. 6 to 9, so that the clutch only operates when the first rotor 81 rotates at a high speed. The operation unit 84 may be operated to achieve a high stage (two stage) shift, and may be configured to return to a low stage (one stage) even at a low speed.

The ball stopper part 87 is provided with a stopper hole 87a formed to communicate with the installation hole 86 of the clutch first rotor, and inserted into the stopper hole 87a to protrude into the installation hole 86. The ball 87b, the ball spring 87c installed in the stopper hole 87a to elastically support the ball 87b, and the stopper hole 87a are fastened to prevent the ball spring 87c from being separated and Control bolt 87d for adjusting.

The ball stopper portion 87 configured as described above is installed at one side of the installation hole 86 so that the ball is supported by the moving table 84c of the clutch operating portion, so that the clutch first rotor 81 is rotated below a set value. At the time, it has a function to prevent the movable stand 84c from moving along the installation hole 86.

When the ball stopper portion 87 is further installed on the centrifugal clutch 80 as described above, when the clutch first rotor 81 is rotated at a low speed (for example, less than 700 rpm), the movable stand 84c is disposed on the ball stopper portion 87. Is in contact with the clutch operating unit 84, and the clutch first rotor 81 rotates at a high speed (for example, 700 rpm or more). When the clutch first rotor 81 is rotated by a centrifugal force caused by the rotation of the clutch first rotor 81 ( 84c may be configured to move along the installation hole 86 while pressing the ball 87b to compress the ball spring 87c to operate the clutch operating unit 84.

In this case, a step is formed in the movable table 84c to include a locking step 841c. When the clutch first rotor 81 rotates at a low speed, the locking step 841c of the moving table 84c of the ball stopper portion 87 is formed. When the moving table 84c is moved along the mounting hole 86 by the high speed rotation of the clutch first rotor 81, the moving table 84c moves to the ball stopper. The state in which the negative ball 87b is kept pressed is maintained.

That is, the present invention allows the high speed shift (two steps) at a high speed (for example 700 rpm or more) to be made at a high speed (for example, 500 rpm or more) by the ball stopper 87, and a low speed (for example, less than 700 rpm). ), The moving table 84c is in situ even at a lower speed (e.g., less than 500 rpm less than 700 rpm) without being affected by the ball stopper portion 87, The clutch operating unit 84 is operated to adjust the speed section.

1 to 3, the planetary gear unit 40 includes a plurality of planetary gears 42 installed to receive a driving force from the sun gear 22 and the plurality of planetary gears 42 to be rotatable. The planetary gear carrier 41 is connected to and supported integrally with the wheel 130.

The planetary gear 42 is installed around the sun gear 22, receives the driving force from the sun gear 22, and rotates (rotates) the sun gear 22 in the direction opposite to the sun gear 22, while the sun gear 22 is centered. By rotating (idling), the planetary gear carrier 41 is rotated in the same direction as the sun gear 22. Since the arrangement of the planetary gear 41 is a known technique, a detailed description thereof will be omitted.

The planetary gear carrier 42 corresponds to an output unit that receives the driving force of the power unit 10 and outputs it to the wheel 130, and the plurality of planetary gears 41 are rotatably connected (rotating). , One side is fixedly installed so as to be connected to the wheel 130 by a bolt or the like. In addition, the first gear clutch of the clutch unit may be connected to the planetary gear carrier 42.

1 and 10, when the rotational force of the input shaft 21 is greater than the rotational force of the planetary gear carrier 41, the unidirectional clutch 35 idles in the forward direction in the free state. When the rotational force of the planetary gear carrier 41 is greater than the rotational force of the input shaft 21, the planetary gear carrier 41 and the input shaft are restrained by restraining the forward rotation of the planetary gear carrier 41 with respect to the input shaft 21. The 21 is connected to the planetary gear carrier 41 and the input shaft 21 of the sun gear unit so as to rotate integrally.

As shown in FIGS. 1 to 3, the ring gear unit 60 includes a ring gear 61 meshed with the planetary gears 41 and a unidirectional bearing such that the ring gear is integrally formed and the reverse rotation is restricted. And a gear housing 62 supported by the central shaft 50 by 90. At this time, the ring gear 61 is formed inside the gear housing 62 so that a plurality of planetary gears 42 are engaged at the same time.

The ring gear unit 60 configured as described above is constrained to rotate (rotate) in the reverse direction (the opposite direction to the rotational direction of the sun gear) by the unidirectional bearing 90, and the sun gear 22 when the clutch unit 30 is inoperative. Drive force is output to the wheel 130 through the planetary gear unit 40, and when the clutch unit 30 is operated, the wheel 130 is rotated in the forward direction together with the sun gear unit 20 and the planetary gear unit 40. ) Will increase the output.

In addition, as shown in FIG. 1, the wheel dust cover 140 is installed at one side of the wheel 130 on which the power unit 10 is installed, and the planetary gear unit 40 and the ring gear unit 60 are provided. The wheel cover 150 is installed at another side of the wheel 130 to be installed, such that the power unit 10, the ring gear unit 60, and the planetary gear unit 40 are not exposed to the outside.

The wheel dust cover 140 is installed such that one side is integrally connected to the wheel 130 and the other side is bearing supported on the power unit 10 or the central shaft 50.

The wheel cover 150 is installed such that one side is integrally connected to the wheel 130 and the other side is bearing supported on the central shaft 50.

Since the installation of the wheel dust cover 140 and the wheel cover 150 is made in a known fixing means such as a bolt, a detailed description thereof will be omitted.

In addition, the present invention is connected to each other between the oil seal, ball bearing, etc., and this additional configuration is a known technique in the transmission, so the description thereof will be omitted.

In addition, as shown in FIGS. 1, 3, and 10, the wheel cover 150 may further include a brake unit 160, and the brake unit 160 may have a cylindrical shape on an outer side of the wheel cover 150. It may be installed to be located in the protruding protrusion 151. Since the brake unit 160 uses a known configuration in which the rotation of the wheel 130 is stopped by contact between the brake drum pad and the brake disc, a detailed description thereof will be omitted.

The central shaft 50 is installed to penetrate the power unit 10, the sun gear unit 20, and the ring gear unit 60, and both ends thereof are fixed to the first and

second frames

110 and 120. That is, the central shaft 50 is penetrated so that the motor rotor 11 of the power unit and the input shaft 21 of the sun gear unit are respectively supported by the bearing, and the ring gear 60 is penetrated so as to be supported by the unidirectional bearing 90. Both ends are fixed to the first and

second frames

110 and 120 so that the wheel cover 150 is supported by the bearing.

According to the present invention configured as described above, the driving force of the power unit is transmitted to the wheel 130 through the sun gear unit 20 and the planetary gear unit 40 so that low speed driving (deceleration) is made, and the power is driven by the operation of the clutch unit 30. The wheel 130 is integrally connected to the unit 10 so that the sun gear unit 20, the planetary gear unit 40, and the ring gear unit 60 are integrally rotated to achieve high speed driving (speedup).

In addition, the present invention may be designed with a sun gear portion as an input source, gear ratio low speed 2.25: 1, high speed 1: 1, by changing the ring gear portion 60 to the input source, that is, the ring gear portion 60 is a power unit ( 10), the sun gear 20 may be configured to be supported by the unidirectional bearing 90 to be connected to the central axis. As such, when the ring gear 60 is designed as an input source, the gear ratio is low at 1.75. : 1, high speed 1: 1 can be changed.

11 and 12, the input shaft 21 of the sun gear part without the central axis 50 may be connected to the first and

second frames

110 and 120. When the central shaft is not installed in this way, the clutch unit 30 and the power unit 10 are merely changed in position, the function is made the same.

That is, FIG. 11 is an exemplary view showing a modified configuration of the present invention, and FIG. 12 is a simplified exemplary view showing the configuration of FIG. 11.

The present invention is a power unit 10; A sun gear unit 20 having one end of the input shaft 21 connected to the power unit 10 and having the sun gear 22 integrally formed at the other side of the input shaft penetrating the wheel 130; A planetary gear unit 40 having a plurality of planetary gears 42 receiving a driving force from the sun gear 22 and having a planetary gear carrier 41 fixedly installed on the wheel 130; A ring gear part 60 installed to receive driving force from the plurality of planetary gears 42 and installed to constrain reverse rotation to the unidirectional bearing 95; Including; clutch portion 30 is connected to the sun gear portion 20 and the ring gear portion 60;

The driving force of the power unit 10 is transmitted to the wheel 130 through the sun gear unit 20, the planetary gear unit 40, the low-speed driving is made,

When the clutch unit 30 is operated, the sun gear unit 20, the planetary gear unit 40, the ring gear unit 60, and the wheel 130 are integrally rotated by the driving force of the power unit 10 so as to increase speed driving. Can be.

The power unit 10 is fixedly installed at one side of the first frame 110 so that one end of the input shaft 21 of the sun gear unit is axially coupled to rotate and drive the input shaft 21 coupled to the shaft.

The input shaft 21 of the sun gear unit penetrates through the first and

second frames

110 and 120, the planetary gear carrier unit 50, and the ring gear unit 60 so that the other end thereof is connected to the clutch unit 30. The bearing 96 is supported on the frame 110.

The planetary gear unit 40 may include a planetary gear 42 and a planetary gear carrier 41, and the planetary gear carrier 42 may be connected to the plurality of planetary gears 42 so as to be rotatable (rotating) and to have wheels. 130 is integrally connected to the installation.

The ring gear part 60 includes a ring gear 61 meshed with a plurality of planetary gears 42, the ring gear 61 is integrally formed, and a bearing 92 is supported by the planetary gear carrier 41. And a gear housing 62 supported by the one-

way bearings

91 and 95 at the second frame 120 and the second frame 120.

The ring gear part 60 configured as described above is constrained by rotation (rotation) in the reverse direction (the opposite direction to the rotational direction of the sun gear) by the unidirectional bearing 95, and is rotated in the forward direction (rotation of the sun gear) by another unidirectional bearing 91. When rotating in the same direction), it is rotated integrally with the input shaft (21).

That is, the ring gear portion 60 is constrained to rotate (rotate) in the reverse direction (the opposite direction to the rotational direction of the sun gear) by the unidirectional bearing 95, so that the sun gear 22 when the clutch portion 30 is inoperative. The driving force of the transmission is transmitted to the planetary gear carrier 41 through the planetary gear 42, the output is made through the wheel 130,

At the time of operation of the clutch part 30, since the ring gear part 60 rotates forward integrally with the input shaft 21 by the unidirectional bearing 91 provided between the input shaft 21, the sun gear 22 and the ring gear part The 60 is rotated to 1: 1 to increase the output of the wheel 131.

The clutch unit 30 may be composed of an electronically controlled clutch 70 or a centrifugal clutch 80. The clutch unit 30 may be connected to the ring gear unit 60 and the input shaft 21 to supply the driving force of the power unit to the ring gear unit ( 60).

That is, when the clutch unit 30 is formed of the electronically controlled clutch 70, the clutch first rotor is connected to the input shaft 21, and the clutch second rotor is installed to be connected to the gear housing 62 of the ring gear unit. The clutch stator is connected to the gear housing 62 or the input shaft 21, and the clutch first rotor and the clutch second rotor are closely coupled by the operation of the clutch stator, and the driving force of the power unit 10 is the ring gear part ( 60).

In addition, when the clutch unit 30 is formed of the centrifugal clutch 80, the clutch first rotor 81 is integrally coupled to the input shaft 21 of the sun gear unit and the space between the clutch first rotor 81 and the space. It is connected to the clutch first rotor 81 so as to be located between the clutch second rotor 82 which is integrally fixed to the ring gear part 60 so as to be provided with (82), and the clutch first and

second rotors

81 and 82. And a clutch operating portion 84 installed to be automatically operated by the rotational force of the clutch first rotor 81 to connect the clutch first and

second rotors

81 and 82 to be integrated. By the clutch operation unit is operated can be configured to be in close contact with the clutch first and second rotor.

Since the configuration and operation of the electronically controlled clutch and the centrifugal clutch as described above are described in the description of FIGS. 1 to 10, the description thereof will be omitted.

The present invention configured as described above can be controlled by setting a shift condition and a deceleration condition as shown in Table 1 below.

Table 1

In addition, the sun gear and the ring gear of the present invention can be determined by the fixed gear ratio at the initial low rpm of the two-speed transmission.

For example, when sun gear: ring gear = 1: 2, the total reduction ratio of the output gearbox of the two-stage planetary gear carrier is reduced by three times (when the ring gear is fixed). Therefore, the gear ratio of the initial low rpm range can be adjusted to the user by arbitrarily changing and combining these gear ratios.

The formula of the rotational speed of the planetary gear components is expressed as S = sun gear rotation, C = planetary gear carrier rotation, R = ring gear rotation, A = ring gear teeth / sun gear teeth This occurs, since [Equation 1] is a known technique, a detailed description thereof will be omitted.

[1] Ring gear rotation speed = ((1 + A) C-S) / A, sun gear rotation speed = (1 + A) C-R x A

Hereinafter, the clutch unit 30 of the present invention is set to the centrifugal clutch 80, and the operation relationship thereof will be described in detail with the accompanying drawings. At this time, the centrifugal force clutch 80 will be described on the assumption that the shift is performed at 30 km / ｈ for the maximum output speed of 100 km / ｈ.

Clutch part inoperative (low speed)

Since the driving force of the power unit is transmitted to the sun gear 22 through the input shaft 21, the planetary gear 42 is rotated, and the gear housing 62 of the ring gear is supported by the unidirectional bearing 90 so that the reverse rotation is constrained. The planetary gear carrier 41 is rotated in the same direction as the rotation direction of the sun gear 22 by the rotation of the planetary gear 42, and the wheel 130 is integrally rotated by the rotation of the planetary gear carrier 41. Drive at low speed of less than 30km / ｈ.

At this time, the clutch first rotor 81 of the centrifugal clutch 80 is rotated with the same rotational force as the power unit or the sun gear unit, and the clutch second rotor 82 is rotated with the same rotational force as the wheel, but the clutch first rotor ( When the rotational force of the 81 is less than a predetermined value, the clutch first and

second rotors

81 and 82 are not coupled by the clutch operating portion 84, so that the clutch first rotor 81 and the clutch second rotor 82 are mutually inclined. It is operated at different torques. That is, the centrifugal clutch 80 is not operated. In addition, in such low-speed driving, the gear ratio may be set to have 2.25: 1.

In addition, in the low-speed driving according to the non-operation of the centrifugal clutch as described above, even when the clutch unit 30 is set as the electronically controlled clutch 70, the power transmission process from the power unit to the wheel is made the same.

Clutch Part Operation (High Speed)

When the rotational force of the input shaft 21 is increased by the power unit 10 and the output speed reaches more than 30 km / ｈ, the rotational force of the clutch first rotor 81 is increased, and the rotational force of the clutch first rotor is increased. The clutch operating portion 84 is operated by the centrifugal force generated by the increase, and the roller 84a is moved along the interspace 83 in the direction of the inner circumferential surface of the second clutch of the clutch along the inclined surface 85b of the close contact portion, and simultaneously moved. The base 84c compresses the support spring 84d and moves along the installation hole 86, so that the distance between the inclined surface 85b of the tight portion and the inner circumferential surface 82b of the receiving groove becomes smaller than the diameter of the roller 84a. The sticking phenomenon of the roller 84a occurs between the inclined surface 85b of the close contact portion and the inner circumferential surface 82b of the receiving groove.

In this way, when the roller 84a of the clutch operating portion is caught between the close contact portion inclined surface 85b of the clutch first rotor and the inner circumferential surface 82b of the clutch second rotor receiving groove, the clutch first rotor 81 and the clutch agent are made. The two rotors 82 are integrally rotated together by the pinch of the roller 84a, so that the driving force of the power unit is transmitted to the wheel. That is, the ring gear unit 60, the planetary gear unit 40, the sun gear unit 20 and the power unit 10 are coupled to each other and all rotated integrally in the same direction, so that the power unit and the wheel are output at a gear ratio of 1: 1. do.

Acceleration pedal not running while driving (generating regenerative braking force)

In addition, when the unidirectional clutch 35 is further installed in the planetary gear unit 40, and when the accelerator pedal is not operated while driving, the planetary gear unit 40 connected to the wheel 130 becomes a power input part, so that the planetary gear unit is operated. The rotational force is input through the fisherman 40.

At this time, the rotational force of the planetary gear unit 40 is greater than the rotational force of the sun gear unit 20, and the unidirectional clutch 35 connected to the planetary gear unit is installed to restrain the forward rotation of the planetary gear carrier with respect to the input shaft of the sun gear unit. When the rotational force higher than the rotational force of the sun gear is input through the planetary gear, the planetary gear and the sun gear are rotated at a rotation ratio of 1: 1. This causes the power unit 10 to be driven to generate power.

That is, in the present invention, when the unidirectional clutch 35 is installed between the planetary gear portion 40 and the sun gear portion 20, when the rotational speed of the planetary gear carrier of the planetary gear portion is greater than the rotational speed of the sun gear, the unidirectional clutch 35 By forcibly driving the power unit, the energy is generated through the power unit by regenerative braking.

Acceleration pedal not in operation while driving (generation of regenerative braking force-configured in Figs.

When the accelerator pedal is not operated while driving, the planetary gear portion 40 becomes a power input portion, so that rotational force is input from the planetary gear portion 40, and the ring gear portion is in the same direction as the planetary gear portion by the rotational force of the planetary gear portion (forward direction). Will rotate.

At this time, the gear housing 62 of the ring gear part is constrained by the unidirectional bearing 91 on the input shaft 21, so that when the ring gear part rotates, the input shaft 21 also rotates in the forward direction, thereby causing the ring gear part ( 60 and the input shaft 21 is generated by forcibly driving the power unit 10 at a rotation ratio of 1: 1.

That is, when the rotational force is input through the planetary gear unit 50, the ring gear unit 60 rotates in the free state in the forward direction. In this case, the sun gear of the input shaft may rotate in the reverse direction, but the power unit for regenerative braking. The reverse force is loaded and the rotation gradually stops. Under these conditions, the idling state is caused by the free rotation amount of the ring gear, so that no regenerative braking force is generated. However, in the present invention, a unidirectional bearing 91 is provided between the ring gear portion 60 and the input shaft 21, so that when the rotational speed of the ring gear portion is greater than the rotational speed of the sun gear, the ring gear portion is formed by the unidirectional bearing 91. And the sun gear are rotated together at a rotation ratio of 1: 1 to forcibly drive the power source, so that energy is generated through the power source by regenerative braking.

The present invention is not limited to the above-described specific preferred embodiments, and various modifications can be made by any person having ordinary skill in the art without departing from the gist of the present invention claimed in the claims. Of course, such changes will fall within the scope of the claims.

Claims

In wheel type two-speed transmission;

Power unit; A sun gear unit to which driving force of the power unit is transmitted; A planetary gear unit for transmitting driving force to the sun gear unit and being connected to the wheel; A ring gear unit connected to the planetary gear unit and installed to restrain the reverse rotation by the unidirectional bearing; One side is connected to the power unit or the sun gear connected to the power unit, the other side is connected to the wheel or planetary gear unit integrally connected to the wheel, the clutch unit is operated to rotate the sun gear unit, the planetary gear unit and the ring gear unit integrally including,

In the state in which the reverse rotation of the ring gear is constrained by the unidirectional bearing, the driving force of the power unit is transmitted to the wheel through the sun gear part and the planetary gear part, thereby driving at low speed.

An in-wheel type two-speed gearbox characterized in that the sun gear unit, the planetary gear unit, the ring gear unit, and the wheel are integrally rotated by the driving force of the power unit to increase the speed.
The method according to claim 1;

In-wheel type two-speed gearbox,

Power unit;

A sun gear unit having one end of the input shaft connected to the power unit and having a sun gear integrally formed at the other side of the input shaft penetrating the wheel;

A planetary gear unit having a plurality of planetary gears to receive driving force from the sun gear and having a planetary gear carrier fixedly installed on the wheel;

A ring gear unit installed to receive a driving force from a plurality of planetary gears;

A clutch unit having one side connected to the power unit or the sun gear unit connected to the power unit and the other side connected to the planetary gear unit integrally connected to the wheel or the wheel;

The central shaft is installed to penetrate the power unit, the sun gear unit and the ring gear unit, the ring gear unit is supported by the unidirectional bearing, and both ends are fixed to the first and second frames.

In the state in which the reverse rotation of the ring gear is constrained by the unidirectional bearing, the driving force of the power unit is transmitted to the wheel through the sun gear part and the planetary gear part, thereby driving at low speed.

In operation of the clutch unit, the wheel is coupled to the power unit, the sun gear unit, the planetary gear unit, the ring gear unit and the wheel is integrally rotated by the driving force of the power unit, the in-wheel type two-speed transmission characterized in that configured to increase speed.
The method according to claim 1;

In-wheel type two-speed gearbox,

Power unit;

A sun gear unit having one end of the input shaft connected to the power unit and having a sun gear integrally formed at the other side of the input shaft penetrating the wheel;

A planetary gear unit having a plurality of planetary gears to receive driving force from the sun gear and having a planetary gear carrier fixedly installed on the wheel;

A ring gear part installed to receive driving force from the plurality of planetary gears and installed to constrain the reverse rotation to the unidirectional bearing;

Including; clutch unit is connected to the sun gear unit and the ring gear unit;

The driving force of the power unit is transmitted to the wheel through the sun gear unit and the planetary gear unit to achieve low speed driving,

An in-wheel type two-speed transmission device, characterized in that, when the clutch unit is operated, the sun gear unit, the planetary gear unit, the ring gear unit, and the wheel are integrally rotated by the driving force of the power unit to increase speed driving.
The method according to claim 2;

The clutch consists of an electronically controlled clutch,

The electronically controlled clutch includes a clutch first rotor integrally coupled to a motor rotor of a power unit or an input shaft of a sun gear unit, a clutch second rotor integrally fixed to a wheel or planetary gear unit so as to correspond to the clutch first rotor, and a center thereof. To include a clutch stator connected to the shaft or motor stator,

The clutch first rotor and the clutch second rotor are closely coupled by the operation of the clutch stator, so that the driving force of the power unit is configured to transmit to the wheel.
The method according to claim 2;

Clutch part is made of a centrifugal clutch,

The centrifugal clutch includes a clutch first rotor integrally coupled to a motor rotor of a power unit or an input shaft of a sun gear unit, and a clutch second rotor integrally fixed to a wheel or planetary gear unit to have a space between the clutch first rotor and the clutch. And a clutch operating part connected to the clutch first rotor so as to be positioned between the clutch first and second rotors and automatically operated by the rotational force of the clutch first rotor to connect the clutch first and second rotors to be integrated.

In-wheel type two-speed transmission characterized in that the clutch operating portion is operated by the rotational force of the clutch first rotor is configured to closely couple the clutch first and second rotor.
The method according to claim 3;

Clutch part consists of an electronically controlled clutch, or centrifugal clutch,

The centrifugal clutch includes a clutch first rotor integrally coupled to the input shaft of the sun gear, a clutch second rotor integrally fixed to the ring gear so as to have a space between the clutch first rotor, and the clutch first and second. The clutch is connected to the first clutch of the clutch so as to be positioned between the rotors, and is automatically operated by the rotational force of the first clutch of the clutch, and includes a clutch operating part for connecting the first and second rotors integrally. In-wheel type two-speed transmission characterized in that the operating unit is configured to be in close contact with the clutch first and second rotor.
The method according to claim 5 or 6;

The clutch first rotor has a close contact portion having a support surface and an inclined surface is formed on the outer circumferential surface, and an installation hole to which the clutch operating portion is connected is provided with a predetermined length and formed therein,

The clutch second rotor includes a receiving groove so that the clutch first rotor is positioned therein, and an inner circumferential surface of which the roller of the clutch operating portion is contacted and supported along the circumference of the receiving groove is formed.

The inter-space is in-wheel type two-speed transmission characterized in that it is formed to have a shape that the interval between the inner circumferential surface of the receiving groove and the inclined surface of the rotating body is gradually narrowed.
The method according to claim 5 or 6;

The clutch operating portion includes a roller installed to be located in the close contact portion of the clutch first rotor, a support installed on one side so that the roller is rotatable, and a hinge connected to the other side of the support installed on the other side of the support hole. In-wheel type two-speed gearbox characterized in that it comprises a moving base to be installed, and a support spring is installed in the mounting hole so as to be located between the movable side and the other side of the mounting hole to support the moving table elastically.
The method of claim 8;

The clutch operating portion is configured to be connected to each other by a link portion,

The link unit includes a central rotary link installed to support the bearing on the input shaft, and a connection link of which one end is hinged to the central rotary link and the other end is rotatable to the moving table of the roller clutch. In-wheel type two-speed gearbox.
The method according to claim 5 or 6;

The centrifugal clutch is configured to further include a ball stopper portion,

The ball stopper part includes a stopper hole formed to communicate with an installation hole of the clutch first rotor, a ball inserted into the stopper hole to be partially protruded into the installation hole to be installed in contact with a moving table, and a stopper to elastically support the ball. An in-wheel type two speed transmission apparatus, comprising: a ball spring installed in the hole and an adjustment bolt fastened in the stopper hole to prevent separation of the ball spring and to adjust tension.
The method of claim 10;

In-wheel type two-speed transmission characterized in that the step is formed on the moving table to have a locking step.
The method according to claim 2;

One-way clutch is further installed to connect the planetary gear unit and the sun gear unit.

The unidirectional clutch has a planetary gear with respect to the input shaft when the planetary gear carrier is idled in the forward direction in the free state when the rotational force of the input shaft is greater than the rotational force of the planetary gear carrier. In-wheel type two-speed transmission characterized in that the planetary gear carrier and the input shaft is connected to the planetary gear carrier so as to be positioned between the planetary gear carrier and the input shaft of the sun gear unit by restraining the forward rotation of the carrier.