KR20220096439A - Deceleration Device - Google Patents

Abstract

Provided is a deceleration device which is installed between a drive motor and a transmission of an electric vehicle to decelerate while increasing torque of a motor at the time of initial driving and to be directly connected as driving progresses. The deceleration device includes a planetary gear set. Among a sun gear, a ring gear, and a carrier of the planetary gear set, elements which are not connected to input and output are connected to a fixed end via a one-way clutch. The element may include a first clutch provided separately from the one-way clutch. Two selected elements selected among the sun gear, the ring gear, and the carrier of the planetary gear set may be coupled or decoupled by a second clutch. The one-way clutch may freewheel during operation of the second clutch. The first clutch and the second clutch may be operated by a common actuator. The actuator may move to a first position where input torque of forward power is multiplied by not operating both of the first clutch and the second clutch, a second position where the input torque of forward power is directly coupled to the output torque by operating only the second clutch without operating the first clutch, and a third position where the input torque of reverse power is multiplied by operating only the first clutch without operating the second clutch. Therefore, the deceleration device is effective since not requiring additional power to maintain coupling of clutches.

Description

Reducer {Deceleration Device}

The present invention relates to a speed reducer, and more particularly, to a speed reducer installed between a vehicle driving motor and a transmission of an electric vehicle to multiply and decelerate the torque of the motor during initial driving, and to be directly connected as driving progresses.

Vehicles require high torque output during initial driving. Accordingly, a speed reducer is used in the motor of the electric vehicle to obtain high torque during initial operation and to secure the convenience of control.

On the other hand, in order to downsize the motor of the electric vehicle and increase fuel efficiency, a transmission is required. Accordingly, the speed reducer may be installed between the motor and the transmission in the power transmission system.

The initial driving of the vehicle takes place not only in the forward direction but also in the reverse direction. Therefore, for initial driving, the output torque needs to be greater than the input torque not only when the vehicle is moving forward but also when the vehicle is moving backwards.

In the case of an internal combustion engine, the direction of rotation of the engine is the same during forward and reverse driving, and forward/reverse is determined by the transmission. Therefore, even if a hydraulic torque converter that multiplies torque for unidirectional rotation during initial driving is applied to a vehicle to which an internal combustion engine is applied, since the transmission switches forward and reverse directions, the initial output torque can be multiplied during forward and reverse.

However, in the case of an electric vehicle, the direction of rotation of the vehicle driving motor is reversed during forward driving and reverse driving. That is, the driving source itself can rotate in both directions. Therefore, even if the hydraulic torque converter is applied to the output side of the motor, it is difficult to increase the torque when the motor is driven in reverse rotation for reverse due to the characteristics of the hydraulic torque converter that multiplies the torque in one direction.

For this reason, a planetary gear set was also used to multiply the input torque of the motor whose rotation direction changes during forward and reverse driving. A planetary gear set includes a sun gear disposed in the center, a ring gear spaced apart from the sun gear and surrounding the sun gear, a planetary gear disposed between the sun gear and the ring gear, and a planetary gear supporting the planetary gear. including a carrier.

A planetary gear set can be divided into three elements, a sun gear, a ring gear, and a carrier, and when any one of these three elements is fixed, the other two elements become an input and an output, respectively, so that deceleration occurs. In addition, if two elements of the sun gear, ring gear, and carrier are rotated integrally, the planetary gear set as a whole rotates integrally, so that deceleration does not occur and is directly connected 1:1.

Accordingly, as disclosed in CN 107499119A, CN 206765791U, and US 10377221B2, in the prior art, deceleration is implemented through brake control for fixing any one element of the planetary gear set, and the two elements of the planetary gear set are mutually fixed with a clutch. 1:1 direct connection was implemented. According to this structure, any one element of the planetary gear set is fixed when a torque multiplication is required for forward driving or when a reverse drive where a torque multiplication is always required. And when direct connection is required for forward driving, the two elements of the planetary gear set are coupled with a clutch. The brake control and the clutch control were each performed by a predetermined actuator, and in order not to put a strain on the device, the two actuators were not operated at the same time.

On the other hand, as disclosed in GB 518366, JP2019-211083A, in order to solve the trouble of operating two actuators for the brake control and the clutch control, one actuator designed to go back and forth between the first position and the second position is used. also did Since this control method operates so that the actuator is positioned at any one of the two positions of the first position and the second position, the problem of the prior art that the device is burdened when the two actuators are operated at the same time is solved by hardware. In this control method, for example, when the actuator is in the first position, the vehicle driving motor and the transmission are connected to increase torque, and when the actuator is in the second position, the vehicle driving motor and the transmission are directly connected 1:1.

However, in this structure, the driving force of the motor is temporarily reduced due to the driver taking their foot off the accelerator pedal for a while during the torque multiplication process, so that the speed increase occurs when the rotational force of the vehicle load is reversely transmitted to the vehicle driving motor through the reducer. This causes a large reduction in the rotational force on the vehicle load side. That is, this structure may cause the vehicle driving motor to consume the rotational force of the load side during the torque multiplication process.

In addition, since this structure has a structure that continuously consumes energy when the actuator is in either the first position or the second position, it is disadvantageous in terms of efficiency.

The present invention has been devised to solve the above problems, and it is intended to provide a reducer that uses one actuator, but prevents the rotational force of the load from being consumed by the motor even if the driver temporarily stops driving the motor in the torque multiplication process do.

In addition, the present invention is to provide a speed reducer that can be freely applied up to a reduction of a gear ratio of 2.0 or more.

Another object of the present invention is to provide a speed reducer with high efficiency because energy is not consumed to maintain the corresponding position at each operating position of the actuator.

Another object of the present invention is to provide a speed reducer that is particularly optimal for use in an electric vehicle.

In order to solve the above problems, the present invention provides, in a speed reducer having a planetary gear set, an element not connected to the input and output among the sun gear, the ring gear, and the carrier of the planetary gear set is connected to the fixed end by a one-way clutch do.

While the one-way clutch supports the element to not rotate relative to the fixed end, the input torque is multiplied and output by the planetary gear set. This can be applied when inputting forward power.

The element may have a first clutch provided separately from the one-way clutch.

The first clutch may be a dog clutch, a multi-plate clutch, or a single-plate clutch. The first clutch may be applied when reverse power is input. When reverse power is input, the clutch may be actuated to support the element from rotation with respect to the fixed end.

Two elements selected from among the sun gear, the ring gear, and the carrier of the planetary gear set may be coupled or decoupled by the second clutch. The two selected elements may be a carrier and a ring gear. The two selected elements may be a carrier and a sun gear. The two selected elements may be a sun gear and a ring gear.

The second clutch may be a dog clutch, a multi-plate clutch, or a single-plate clutch. The second clutch may be operated when forward power is input. When the second clutch operates, the input and output are directly connected to transmit power. The one-way clutch may be freewheeling while the second clutch is operating.

The first clutch and the second clutch may be operated by a common actuator. The actuator has a first position in which neither the first clutch nor the second clutch are operated, a second position in which the second clutch is operated without operating the first clutch, and the first clutch is operated and the second clutch is operated. You can move the 2 clutch to the 3rd position in which it does not operate.

When the actuator is in the first position, an input torque of the forward power may be multiplied and output. When the actuator is in the second position, the input torque of the forward power may be directly connected to the output torque. When the actuator is in the third position, the input torque of the reverse power may be multiplied and output.

The first position may be disposed between the second position and the third position.

The actuator may include a diaphragm for pressing the second clutch. The diaphragm applies an elastic force to the actuator in a direction in which the actuator moves from the third position to the first position and in a direction in which the actuator moves from the first position to the second position.

The second clutch is pressed by the elastic force of the diaphragm. That is, since the elastic force of the diaphragm operates the second clutch, a separate power is not continuously consumed to maintain the state in which the second clutch is operated.

When the actuator overcomes the elastic force of the diaphragm and starts moving from the second position to the first position, the diaphragm does not press the second clutch.

The actuator may include a slider that moves in an axial direction. The slider may be connected to the diaphragm. The slider may push the diaphragm from the second position to the first position, and may push the diaphragm from the first position to the third position.

The actuator may include a driving unit for moving the slider from the second position through the first position to the third position.

The driving unit may convert the rotational motion into a linear motion to move the slider in the axial direction.

The driving unit may include a rotating motor, a first gear rotating by the motor, a second gear meshing with the first gear, and a sliding member rotating integrally with the second gear. The sliding member and the slider may slide.

The first gear and the second gear may be a worm gear and a worm wheel gear. Accordingly, the rotation axes of the first gear and the second gear may not be parallel.

Alternatively, the first gear and the second gear may be spur gears. Accordingly, the rotation axes of the first gear and the second gear may be parallel to each other.

The sliding member may be a cam. The slider is movable in the axial direction by sliding on the surface of the cam. The slider may be in close contact with the surface of the cam by the elastic force of the diaphragm.

Alternatively, the sliding member may have a screw thread structure. The slider may have a threaded structure engaged with the threaded structure of the sliding member.

Specifically, the present invention provides a speed reducer including an input shaft 10 to which a rotational force is input, an output shaft 90 to which a rotational force is output, and a planetary gear set 20 for transmitting the rotational force of the input shaft 10 to the output shaft 90 . (1) can be applied.

The planetary gear set 20 includes: a sun gear 30; a ring gear 60 surrounding the sun gear 30; a planetary gear 40 disposed between the sun gear 30 and the ring gear 60 to transmit a rotational force between the sun gear 30 and the ring gear 60; and a carrier 50 for rotatably supporting the planetary gear 40 .

The input shaft 10 may be connected to transmit a rotational force to a first element selected from among the sun gear 30 , the ring gear 60 , and the carrier 50 .

A second element (not overlapping with the first element) selected from among the sun gear 30 , the ring gear 60 , and the carrier 50 may be connected to transmit a rotational force to the output shaft 90 .

A third element selected from among the sun gear 30 , the ring gear 60 , and the carrier 50 (does not overlap with the first element and the second element) is disposed with respect to the fixed end 71 of the speed reducer 1 . It is connected to the fixed end 71 through a one-way clutch 73 that allows rotation in one direction and restricts rotation in the other direction.

The third element is rotationally constrained or released with respect to the fixing end 71 by a fixing-releasing part 75 provided separately from the one-way clutch 73 . The fixing-releasing unit 75 may be the first clutch.

Two selected elements among the first element, the second element and the third element are coupled or decoupled by the clutch 77 . The clutch 77 may be the second clutch.

The lock-release portion 75 and the clutch 77 are actuated and disengaged by a common actuator 80 .

The actuator 80 has a first position P1 for disengaging the locking-release portion 75 and disengaging the clutch 77 , and a first position P1 for disengaging the lock-release portion 75 and disengaging the clutch 77 . The second position P2 of operating 77 and the third position P3 of operating the lock-release portion 75 and disengaging the clutch 77 are moved.

The second position P2 may be located farthest from the third element, and the third position P3 may be located closest to the third element.

The first element may be a sun gear 30 , and the second element may be a ring gear 60 .

The planetary gear 40 may include a first planetary gear 41 meshing with the sun gear 30 and a second planetary gear 42 meshing with the ring gear 60 . Here, the first planetary gear 41 and the second planetary gear 42 may mesh with each other. Accordingly, the rotation directions of the sun gear 30 and the ring gear 60 can be matched.

The fixing-releasing unit 75 may include a first dog clutch 751 fixed to the third element and a second dog clutch 752 fixed to the actuator 80 .

The clutch 77 may be a wet multi-plate clutch.

The two elements coupled or uncoupled by the clutch 77 may be the carrier 50 and the ring gear 60 .

The carrier (50) has a carrier cover (51) extending outwardly in a radial direction, the ring gear (60) has a ring gear cover (61) extending outwardly in a radial direction, and the carrier cover (51) and the ring gear cover 61 may be connected to each other by the clutch 77 outside the ring gear 60 in a radial direction.

The actuator 80 may include a slider 81 that is rotationally restricted with respect to the fixed end and is movable in the axial direction along the fixed end.

The actuator 80 may further include a diaphragm 82 for pressing or releasing the pressure of the clutch 77 . The diaphragm 82 is connected to the slider 81 , and may press the clutch 77 or release the pressure on the clutch 77 depending on the axial movement position of the slider 81 .

The actuator 80 may further include a driving unit 83 that provides a force for moving the slider 81 in the axial direction.

The driving unit 83 may include a motor 830 rotatable in both directions.

The driving unit 83 may further include a worm gear 831 connected to the motor 830 .

The driving unit 83 may further include a worm wheel gear 832 meshing with the worm gear 831 .

The worm wheel gear 832 may include a cam 833 . The worm wheel gear 832 and the cam 833 may be installed rotatably relative to the fixed end, and may be restricted from moving in the axial direction with respect to the fixed end. The cam 833 may slide with the slider 81 .

The slider 81 and the diaphragm 82 may be connected by a thrust bearing 84 . Accordingly, relative rotation between the slider 81 that does not rotate with respect to the fixed end and the diaphragm 82 that rotates together with the clutch 77 can be smoothly performed.

The fulcrum 821 of the diaphragm 82 is supported by a clutch cover 771 connected to the clutch 77 , and the force point 822 of the diaphragm 82 has a radius greater than the fulcrum of the diaphragm 82 . It is connected to the slider 81 from the inside in the direction, and the action point 823 of the diaphragm 82 is connected to a pressure plate 772 that presses the clutch 77 radially outside the fulcrum point of the diaphragm 82. can

The slider 81 has a first position P1 for disengaging the lock-disengaging portion 75 and disengaging the clutch 77, and a first position P1 for disengaging the lock-disengaging portion 75 and the clutch ( It can move to a second position P2 of operating 77 , and a third position P3 of operating the lock-release portion 75 and disengaging the clutch 77 . The slider 81 may stay in the first position P1, the second position P2, and the third position P3, respectively.

The elastic force of the diaphragm 82 will press the slider 81 to move from the third position P3 to the first position P1 and from the first position P1 to the second position P2. can

In addition, the present invention further provides a method for controlling the speed reducer described above. In this case, by controlling the position of the slider 81 of the actuator 80, control of whether the clutch 77 and the lock-release unit 75 operate or not can be made.

The control method of the speed reducer may include a forward torque multiplication step, a forward direct connection step, and a reverse torque multiplication step.

The control for multiplying the forward torque is, when a driving force for forward movement starts to be input to the input shaft 10 , the lock-release unit 75 is released and the clutch 77 is released to release the one-way clutch. (73) may be achieved by rotationally constraining the third element with respect to the fixed end (71). Torque multiplication may be achieved through the planetary gear set 20 .

For the forward torque multiplication operation, the control unit 85 may operate the driving unit 83 so that the slider 81 is positioned at the first position P1 .

In the control for direct connection, when the input of the driving force for forward movement to the input shaft 10 is continued and torque multiplication is not required, the lock-release unit 75 is released and the clutch 77 is operated. It can be achieved by operating and rotating the planetary gear set 20 integrally. In the forward direct connection step, the one-way clutch 73 freewheels.

For the direct forward operation, the control unit 85 may operate the driving unit 83 so that the slider 81 is positioned at the second position P2 .

The control for multiplying the reverse torque may be achieved by operating the lock-releasing unit 75 and disengaging the clutch 77 when a driving force for reverse is input to the input shaft 10 . The torque multiplication may be achieved through the planetary gear set 20 .

To increase the reverse torque, the control unit 85 may operate the driving unit 83 so that the slider 81 is positioned at the third position P3 .

According to the present invention, by using the actuator but also using the one-way clutch in the planetary gear set, even if the driver temporarily stops driving the motor during the torque multiplication process, the rotational force of the load is not consumed by the motor.

According to the present invention, the actuator can be operated and controlled to stay in three positions, so that it is possible to implement all of the forward torque multiplication, direct forward connection and reverse torque multiplication of the planetary gear set with one actuator.

According to the present invention, the torque multiplication in the forward movement is achieved by the one-way clutch supporting a selected one element of the planetary gear set so that it does not rotate, and the torque multiplication in the reverse operation is achieved by holding the selected one element by a separate lock-release unit (first It can be achieved by supporting it so that it does not rotate with a clutch).

According to the present invention, since the elastic force of the diaphragm couples the two elements of the planetary gear set to the clutch, there is no need to consume separate power to maintain the coupling of the clutch in the forward direct connection state that occupies most of the operation, which is efficient. .

According to the present invention, the input is connected to the sun gear and the output is applied to the ring gear, and by connecting two planetary gears connecting them in series, the rotation directions of the input and the output can be matched, and the high gear ratio of 2 to 11 A deceleration design is also possible.

The reducer of the present invention is particularly suitable for being interposed between a motor and a transmission, which are power sources of an electric vehicle.

In addition to the above-described effects, the specific effects of the present invention will be described together while describing specific details for carrying out the invention below.

1 is a conceptual diagram of a speed reducer according to an embodiment.
FIG. 2 is a conceptual diagram of a planetary gear set of the speed reducer of FIG. 1 .
3 is a cross-sectional view showing the reduction gear of the embodiment in half with respect to the axis of rotation.
4 is an enlarged view of the rotation center of FIG. 3 .
5 is a view showing a state in which the actuator is in the first position.
6 is a view showing the states of the clutch and the dog clutch when the actuator is in the first position.
7 is a view showing a state in which the actuator is in the second position.
8 is a view showing the states of the clutch and the dog clutch when the actuator is in the second position.
9 is a view showing a state in which the actuator is in the third position.
10 is a view showing the states of the clutch and the dog clutch when the actuator is in the third position.

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

The present invention is not limited to the embodiments disclosed below, and various changes may be made and may be implemented in various different forms. Only this embodiment is provided to complete the disclosure of the present invention and to fully inform those of ordinary skill in the scope of the invention. Therefore, the present invention is not limited to the embodiments disclosed below, and all changes and equivalents included in the technical spirit and scope of the present invention as well as substituting or adding the configuration of any one embodiment and the configuration of other embodiments to each other or substitutes.

The accompanying drawings are only for easy understanding of the embodiments disclosed in the present specification, and the technical spirit disclosed in the present specification is not limited by the accompanying drawings, and all changes and equivalents included in the spirit and scope of the present invention It should be understood to include water or substitutes. In the drawings, in consideration of the convenience of understanding, the size or thickness may be exaggeratedly large or small, but the protection scope of the present invention should not be construed as being limited thereto.

The terms used herein are used only to describe specific embodiments or examples, and are not intended to limit the present invention. And singular expressions include plural expressions unless the context clearly dictates otherwise. In the specification, terms such as includes, consists of, etc. are intended to designate that the features, numbers, steps, operations, components, parts, or combinations thereof described in the specification exist. That is, in the specification, terms such as include and consist of. It should be understood that this does not preclude the possibility of addition or existence of one or more other features or numbers, steps, operations, components, parts, or combinations thereof.

Terms including an ordinal number such as 1st, 2nd, etc. may be used to describe various elements, but the elements are not limited by the terms. The above terms are used only for the purpose of distinguishing one component from another.

When an element is referred to as being “connected” or “connected” to another element, it is understood that it may be directly connected or connected to the other element, but other elements may exist in between. it should be On the other hand, when it is said that a certain element is "directly connected" or "directly connected" to another element, it should be understood that the other element does not exist in the middle.

When an element is referred to as being "on" or "below" another element, it should be understood that other elements may be present in the middle as well as disposed directly on the other element. .

Unless defined otherwise, all terms used herein, including technical and scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. Terms such as those defined in commonly used dictionaries should be interpreted as having a meaning consistent with the meaning in the context of the related art, and should not be interpreted in an ideal or excessively formal meaning unless explicitly defined in the present application. does not

Since the reducer of the embodiment is symmetrical with respect to the axis, only half is shown with respect to the axis for convenience of drawing. In addition, for convenience of explanation, the direction along the longitudinal direction of the shaft forming the center of rotation of the reducer is referred to as the axial direction, that is, the front-rear direction or the axial direction is a direction parallel to the rotation axis, and the front (front) is any one direction, such as a power source, It means a direction toward the vehicle driving motor, and the rear (rear) means another direction, for example, a direction toward the transmission. Therefore, the front (front) means the surface on which the surface faces the front, and the rear (rear) means the surface on which the surface faces the rear.

The radial or radial direction means a direction closer to the center or a direction away from the center along a straight line passing through the center of the rotation axis on a plane perpendicular to the rotation axis. A direction away from the center in a radial direction is referred to as a centrifugal direction, and a direction closer to the center is referred to as a centripetal direction.

The circumferential direction or the circumferential direction means a direction surrounding the rotation shaft. The outer circumference means the outer circumference, and the inner circumference means the inner circumference. Accordingly, the outer circumferential surface is a surface facing away from the rotation shaft, and the inner circumferential surface is a surface facing the rotation shaft.

The circumferential side means a side whose normal line faces the circumferential direction.

[Structure of Reducer]

Hereinafter, the overall structure of the reducer of the embodiment will be described with reference to FIGS. 1 to 4 .

<Fixed end, input shaft and output shaft>

The reducer 1 includes an input shaft 10 and an output shaft 90 having concentric rotation shafts. An inner circumferential surface of the input shaft 10 may include an input shaft spline 105 and may be connected to, for example, a drive shaft of a vehicle driving motor (not shown). The inner peripheral surface of the output shaft 90 may also have output shaft splines 901 , and may be connected to, for example, an input shaft of a transmission of a vehicle (not shown).

A driving shaft of the vehicle driving motor may rotate in both directions. That is, when moving the vehicle forward, the vehicle driving motor may rotate in one direction. And when the vehicle is reversed, the vehicle driving motor may rotate in the other direction.

In an embodiment, the output shaft 90 may rotate in the same rotational direction as the input shaft 10 . Of course, the technical spirit of the present invention is not limited thereto. That is, the technical idea of the present invention also includes a case in which the rotation directions of the input shaft 10 and the output shaft 90 are opposite to each other.

The input shaft 10 and the output shaft 90 are connected to each other through a planetary gear set 20 .

The speed reducer 1 may include a casing 70 . The casing 70 may have a cylindrical shape for accommodating components constituting the speed reducer. The casing 70 may form a fixed end. That is, even if each component inside the casing 70 rotates, the casing 70 may maintain a fixed state without rotation.

A fixed end 71 may be coupled to the vicinity of the center of the casing 70 . The fixed end 71 may be in the form of a hollow shaft extending in the axial direction. The fixed end 71 is coupled to the casing to maintain a fixed state together with the casing.

A small inner diameter portion 711 is provided in front of the inner peripheral surface of the fixed end 71 . A bearing receiving portion 712 in which the first needle bearing 721 can be seated is provided at the rear of the small inner diameter portion 711 . The inner diameter of the bearing accommodating portion 712 is larger than the small inner diameter portion 711 . Accordingly, the rear end of the small inner diameter portion 711 supports the axial front of the first needle bearing 721 to regulate the front position of the first needle bearing 721 .

The diameter of the first needle bearing 721 is slightly larger than the difference between the inner diameter of the small inner diameter portion 711 and the inner diameter of the bearing receiving portion 712 . That is, in a state in which the first needle bearing 721 is seated in the bearing receiving part 712 , the centripetal end of the first needle bearing 721 protrudes more centripetally than the small inner diameter part 711 .

At the rear of the bearing accommodating part 712 , a large inner diameter part 713 having an inner diameter larger than that of the bearing accommodating part 712 is provided.

The input shaft 10 may extend in the axial direction through the hollow portion of the fixed end 71 . The input shaft 10 may be inserted into the hollow portion of the fixed end 71 from the rear to the front of the fixed end 71 .

An alienated neck 101 is provided in front of the outer peripheral surface of the input shaft 10 . The diameter of the outer diameter portion 101 is slightly smaller than the diameter of the small inner diameter portion 711 of the fixed end 71 .

An input shaft bearing jaw 102 having an outer diameter larger than that of the alienated neck 101 is provided at the rear of the alienated neck 101 . The input shaft bearing jaw 102 supports the rear axial direction of the first needle bearing 721 to regulate the rear position of the first needle bearing 721 .

At the rear of the input shaft bearing jaw 102 , an outer diameter portion 103 having an outer diameter larger than that of the input shaft bearing jaw 102 is provided. The diameter of the outer diameter portion 103 is slightly smaller than the diameter of the large inner diameter portion 713 .

The rear end of the input shaft 10 may be connected to a first element selected from among the sun gear 30 , the carrier 50 , and the ring gear 60 of the planetary gear set 20 . In the embodiment, a form in which the input shaft 10 is connected to the sun gear 30 is exemplified.

The diameter of the radially inner end of the sun gear 30 is slightly larger than the inner diameter of the rear end of the input shaft 10 . A second needle bearing 722 is installed at the radially inner end of the sun gear 30 . The axial front end of the second needle bearing 722 is supported by the rear surface of the input shaft 10 .

At the rear of the inner peripheral surface of the input shaft 10 , an inner diameter portion 104 having an enlarged inner diameter of the inner peripheral surface of the input shaft 10 is provided. The inner diameter of the inner diameter portion 104 may correspond to the inner diameter of the small inner diameter portion 711 of the fixed end 71 .

The output shaft 90 may be inserted into the inner diameter portion 104 of the input shaft 10 . The output shaft 90 may be inserted into the inner diameter portion 104 of the input shaft 10 from the rear to the front of the input shaft 10 .

An outer diameter portion 902 having a predetermined outer diameter is provided in front of the output shaft 90 . The diameter of the outer diameter portion 902 is slightly smaller than the diameter of the inner diameter portion 104 of the input shaft 10 . The outer diameter of the outer diameter portion 902 of the output shaft 90 may correspond to the outer diameter of the outer diameter portion 101 of the input shaft 10 .

At the rear of the outer diameter portion 902 of the output shaft 90 , an output shaft bearing jaw 903 having an outer diameter larger than that of the outer diameter portion 902 is provided. The output shaft bearing jaw 903 supports the rear axial direction of the second needle bearing 722 to regulate the rear position of the second needle bearing 722 .

The output shaft bearing jaw 903 is provided with an output shaft flange 904 extending outward in the radial direction. The output shaft flange 904 may be connected to a second element selected from among the sun gear 30 , the carrier 50 , and the ring gear 60 of the planetary gear set 20 . In the embodiment, a form in which the output shaft 90 is connected to the ring gear 60 is exemplified.

According to the structure described above, the input shaft 10 is inserted into the fixed end 71 through the first needle bearing 721 at the rear of the fixed end 71, and the second needle bearing ( The assembly may be made in such a way that the output shaft 90 is inserted into the input shaft 10 with the 722 interposed therebetween. The input shaft 10 is rotationally supported by the fixed end 71 and the first needle bearing 721 , and the output shaft 90 is rotationally supported by the input shaft 10 and the second needle bearing 722 .

Reference numeral B, which is shown in the drawings but not described, denotes a bearing. The bearing (B) may be installed between two parts that rotate relative to each other.

<Planetary Gear Set>

The planetary gear set 20 of the embodiment includes a sun gear 30 , a carrier 50 , and a ring gear 60 having a concentric axis of rotation. The sun gear 30 is disposed on the centripetal side, the ring gear is disposed on the distal side, and the planetary gear 40 is disposed between the sun gear 30 and the ring gear 60 . That is, the planetary gear 40 meshes with the sun gear 30 toward the centripetal side and meshes with the ring gear 60 toward the distal side. The carrier 50 supports the rotation of the planetary gear 40 .

The input shaft 10 is connected to a first element selected from among the sun gear 30 , the carrier 50 , and the ring gear 60 . The output shaft 90 is connected to a second element (not overlapping with the first element) selected from among the sun gear 30 , the carrier 50 and the ring gear 60 . According to the embodiment, the input shaft 10 is connected to the sun gear 30 , and the output shaft 90 is connected to the ring gear 60 . In order for the input shaft 10 and the output shaft 90 to rotate in the same direction, the planetary gear 40 may include a first planetary gear 41 and a second planetary gear 42 connected in series with each other. .

For example, when the carrier 50 is fixed in FIG. 2 , when the sun gear 30 rotates in one direction (eg, clockwise), the first planet gear 41 rotates in the other direction (eg, counterclockwise). and the second planetary gear 42 rotates in one direction again, and accordingly, the ring gear 60 also rotates in one direction. If the rotation of the sun gear is transmitted to the ring gear through one planetary gear, the rotation directions of the sun gear and the ring gear may be opposite to each other. In the embodiment, a structure in which two planetary gears are connected in series between the sun gear and the ring gear to match the rotation directions of the input shaft and the output shaft is exemplified.

The third element (not overlapping with the first element and the second element) selected from among the sun gear 30 , the carrier 50 , and the ring gear 60 is connected to the fixed end 71 through the one-way clutch 73 . It may be connected rotatably in one direction. The one-way clutch 73 prevents the third element from rotating in the other direction with respect to the fixed end 71 . The third element is an element that is not connected to the input shaft and is not connected to the output shaft.

In an embodiment, the third element may be a carrier 50 . For reference, in the embodiment, the input shaft 10 is connected to the sun gear 30 , the output shaft 90 is connected to the ring gear 60 , and the carrier 50 is connected to be rotatably supported with respect to the fixed end 71 . is illustrated, but the connection does not necessarily have to be this way.

For example, the input shaft is connected to the ring gear and the output shaft is connected to the sun gear, the input shaft is connected to the sun gear and the output shaft is connected to the carrier, the input shaft is connected to the carrier and the output shaft is connected to the sun gear, the input shaft is connected to the carrier and the output shaft is connected Of course, the structure connected to the ring gear, the structure in which the input shaft is connected to the ring gear and the output shaft is connected to the carrier may also be included in the technical spirit of the present invention. In addition, elements that are not connected to the input shaft and the output shaft among the sun gear, the carrier, and the ring gear of the planetary gear set may be rotatably and/or rotationally restricted to the fixed end.

According to the embodiment, the radially inner front of the sun gear 30 is integrally connected with the input shaft 10 .

In front of the planetary gear set 20 , the centripetal end of the carrier 50 is connected to the fixed end 71 through the one-way clutch 73 . In front of the planetary gear set 20 , the carrier 50 has a carrier cover 51 extending in the centrifugal direction.

A ring gear cover 61 is connected to the rear of the ring gear 60 . The ring gear cover 61 extends from the ring gear 60 toward the centripetal side and is connected to rotate integrally with the output shaft flange 904 . The ring gear cover 61 extends distally from the ring gear 60 to face the carrier cover 51 in a radial direction.

Outside the ring gear 60 in a radial direction, the carrier cover 51 and the ring gear cover 61 face each other in a radial direction. According to an embodiment, the carrier cover 51 may be disposed further inside the ring gear cover 61 in the radial direction.

A clutch 77 may be installed between the carrier cover 51 and the ring gear cover 61 facing each other. As the clutch 77, a single-plate clutch, a multi-plate clutch, a dog clutch, and the like can be used. In the embodiment, it is exemplified that a multi-plate clutch is used as the clutch 77 . The multi-plate clutch may be of a wet type. The clutch 77 may be pressurized or depressurized by a pressure plate 772 disposed in front thereof.

A clutch cover 771 is coupled to the front end of the ring gear cover 61 . The ring gear cover 61 has teeth protruding forward, and the clutch cover 771 has teeth of a complementary shape to be fitted between the teeth of the ring gear cover 61 . After inserting the clutch cover 771 to the ring gear cover 61 from the front of the ring gear cover 61 , a C-shaped snap ring 773 is inserted into a groove provided on the inner circumferential surface of the ring gear cover 61 . . Then, the snap ring 773 prevents the clutch cover 771 from being separated from the front of the clutch cover 771 .

The clutch cover 771 supports the diaphragm 82 of the actuator 80 to be described later.

When the clutch 77 is pressed, the carrier 50 and the ring gear 60 are mutually rotationally constrained. In this state, the rotation of the sun gear 30 is transmitted to the carrier 50 and the ring gear 60 as it is. That is, the sun gear 30 , the carrier 50 , and the ring gear 60 rotate integrally. Therefore, when the clutch 77 operates, the input torque is transmitted as the output torque as it is. That is, the gear ratio is 1:1.

At the front of the carrier 50 , a lock-release portion 75 is provided. As the fixing-releasing part 75, a single plate clutch, a multi-plate clutch, a dog clutch, etc. can be used. The lock-release unit 75 may include a set-side clutch 751 fixed to the third element of the planetary gear set 20 and a fixed-end clutch 752 fixed to an actuator 80 to be described later. .

In the embodiment, it is exemplified that a dog clutch is used as the lock-release unit 75 . And the dog clutch includes a first dog clutch 751 fixed to the carrier 50 of the planetary gear set 20 and a second dog clutch 752 fixed to the slider 81 of the actuator 80 to be described later. can be provided The first dog clutch 751 and the second dog clutch 752 face each other in the front-rear direction. The second dog clutch 752 may be moved in the axial direction to be engaged with the first dog clutch 751 or separated from the first dog clutch 751 .

When the input shaft 10 rotates in one direction while both the clutch 77 and the lock-release unit 75 are released, the sun gear 30 rotates in one direction as shown in FIG. 2, and the first planetary The gear 41 rotates in the other direction, the second planetary gear 42 rotates in one direction, and the ring gear 60 rotates in one direction. At this time, the carrier 50 receives a force to rotate in the other direction, but rotation is prevented by the one-way clutch 73 . As a result, the output shaft 90 rotates in one direction at the speed at which the torque is multiplied and reduced.

When the input shaft 10 rotates in one direction while the clutch 77 operates and the lock-release unit 75 is released, the sun gear 30, the carrier 50, and the ring gear 60 rotate integrally. do. Accordingly, the output shaft 90 rotates in one direction at the same speed as the input shaft 10 . In this state, the one-way clutch 73 freewheels.

When the input shaft 10 rotates in the other direction while the clutch 77 is released and the lock-release unit 75 is operated, the sun gear 30 rotates in the other direction, and the first planetary gear 41 rotates in one direction, the second planetary gear 42 rotates in the other direction, and the ring gear 60 rotates in the other direction. At this time, the carrier 50 receives a force to rotate in one direction, but is fixed by the fixing-releasing unit 75 to prevent rotation. Accordingly, the output shaft 90 is rotated in the other direction at the speed at which the torque is multiplied and reduced.

<actuator>

The operation of the clutch 77 and the lock-release portion 75 is controlled by an actuator 80 . The actuator 80 is controlled by a control unit 85 . The control unit 85 controls the rotation direction and amount of rotation of the motor 830 .

The motor 830 rotates the first gear 831 . In an embodiment, the first gear 831 may be a worm gear. The first gear 831 has a rotation axis perpendicular to the axial direction at a position spaced apart from the fixed end.

The first gear 831 is engaged with the second gear 832 to transmit rotational force. The second gear 832 may be a worm wheel gear 832 surrounding the fixed end 71 . The rotation axis of the worm wheel gear 832 corresponds to the central axis of the fixed end 71 .

When the first gear 831 rotates in one direction, the second gear 832 rotates around the fixed end 71 in one direction.

Although the embodiment illustrates that the first gear 831 is a worm gear and the second gear 832 is a worm wheel gear, the technical spirit of the present invention is not limited thereto. For example, the first gear and the second gear may be spur gears. However, for the worm gear and the worm wheel gear, it is possible to transmit the rotational force from the worm gear to the worm wheel gear at a high reduction ratio, but it may not be possible to transmit the rotational force from the worm wheel gear to the worm gear. Accordingly, there is an advantage in that the elastic force of the diaphragm 82, which will be described later, prevents the worm gear from rotating.

A sliding member 833 is provided inside the second gear 832 in a radial direction. The sliding member 833 may be, for example, a cam. The profile of the cam may be a surface helically disposed along the axial direction.

A slider 81 is installed at the fixed end 71 . The slider 81 is installed on the fixed end 71 so as to be prevented from rotating with respect to the fixed end 71 and to be movable along the longitudinal direction (axial direction) of the fixed end 71 .

The slider 81 slides with the sliding member 833 . That is, the slider 81 may have a profile complementary to that of the cam of the sliding member 833 . Accordingly, as shown separately in FIG. 4 , the slider 81 may move in the axial direction along the fixed end 71 by the rotation of the sliding member 833 . For example, when the worm wheel gear 832 rotates in one direction, the cam profile of the sliding member 833 pushes the slider 81 backward in the axial direction.

The slider 81 is connected to the diaphragm 82 and is also connected to the dog clutch 75 .

A fulcrum 821 approximately in the vicinity of the center of the diaphragm 82 in the radial direction is connected and supported in the vicinity of the centripetal side of the clutch cover 771 . A force point 822 at the centripetal end of the diaphragm 82 is connected to the slider 81 . The slider 81 may press the diaphragm 82 in a direction that pushes the force point 822 of the diaphragm 82 backward. An action point 823 at the distal end of the diaphragm 82 is connected to the pressure plate 772 . When the slider 81 pushes the force point 822 of the diaphragm 82 backward, the pressure plate 772 moves forward.

The elastic force of the diaphragm 82 acts in a direction in which the pressure plate 772 presses the clutch 77 (rear), and acts in a direction in which the slider 81 is pushed forward. Accordingly, the slider 81 is elastically supported in a direction in close contact with the cam surface of the sliding member 833 by the elastic force of the diaphragm 82 .

When the worm wheel gear 832 rotates in one direction, the profile of the cam of the sliding member 833 overcomes the elastic force of the diaphragm 82 and pushes the slider 81 backward in the axial direction. And when the worm wheel gear 832 rotates in the other direction, the profile of the cam of the sliding member 833 retreats so that the slider 81 can move forward in the axial direction. Then, by the elastic force of the diaphragm 82 , the slider 81 moves forward in the axial direction to move into the space where the profile of the cam is retreated.

That is, the rearward movement of the slider 81 in the axial direction may be performed by the rotational force of the worm wheel gear 832 , and the forward movement of the slider 81 in the axial direction may be performed by the elastic force of the diaphragm 82 .

If the slider 81 is positioned forward in the axial direction and does not elastically deform the diaphragm 82 , the elastic force of the diaphragm 82 acts on the pressure plate 772 to press the clutch 77 .

The embodiment exemplifies a structure in which the sliding member 833 and the slider 81 slide in a cam manner. However, the structure in which the rotational motion of the sliding member 833 is converted into a linear motion of the slider 81 is not necessarily limited thereto. For example, the sliding member 833 may have a female thread, and the slider 81 may have a male thread engaged therewith. That is, if the rotational motion of the sliding member 833 is converted into a linear motion of the slider 81, various known structures may be applied.

The force point 822 of the slider 81 and the diaphragm 82 is interconnected through a thrust bearing 84 . Since the force point of the diaphragm 82 has a small diameter, the diameter of the thrust bearing 84 allowing relative rotation with the slider 81 may be small. That is, by using the diaphragm 82 to increase the radial distance between the friction plate of the clutch 77 and the rotational shaft, the position of the force point 822 that presses the diaphragm 82 is placed close to the rotational shaft, so that a small diameter thrust bearing ( 84) can be used. According to the embodiment, by reducing the diameter of the thrust bearing 84 , the unit cost of the thrust bearing 84 can be lowered, and the linear speed of the thrust bearing 84 can be reduced when the thrust bearing 84 rotates. reliability can be ensured.

A second dog clutch 752 is connected to the rear end of the slider 81 . The second dog clutch 752 may operate integrally with the slider 81 .

When the motor 830 rotates in one direction, the slider 81 may move backward. And when the motor 830 rotates in the other direction, the slider 81 may move forward. In a state in which the motor 830 is stopped, the slider 81 may also maintain a stopped state in its place. When the motor 830 is stopped, the elastic force of the diaphragm 82 presses the slider 81 forward. However, since the already stopped worm gear 831 blocks the rotation of the worm wheel gear 832 without receiving the rotational force of the worm wheel gear 832 , the slider 81 is not pushed forward despite the elastic force of the diaphragm 82 . .

The slider 81 may move to a first position P1, a second position P2, and a third position P3 depending on whether the clutch 77 and the dog clutch 75 are operated, and the corresponding positions can stay on the spot. The controller 85 may control the rotation direction and amount of the motor 830 to control the position of the slider 81 .

The second position P2 may be a position in which the slider 81 is most forward in the axial direction, and the third position P3 may be a position in which the slider 81 is rearward. The first position P1 may be disposed between the second position P2 and the third position P3 .

When the slider 81 is in the first position P1, both the clutch 77 and the dog clutch 75 are released. When the slider 81 is in the second position, the clutch 77 operates and the dog clutch 75 is released. When the slider 81 is in the third position, the dog clutch 75 operates and the clutch 77 is released.

The clutch 77 and the dog clutch 75 are operated by one actuator 80, and the actuator 80 determines whether the clutch 77 and the dog clutch 75 are operated according to their operating positions. . And the operating position of the actuator 80 includes the above-described first position (P1), the second position (P2), and the third position (P3). Therefore, if the position of the actuator 80, more precisely, the slider 81, is controlled by the control unit 85, the operation of the clutch 77 and the dog clutch 75 can be controlled as a result.

On the other hand, when the clutch 77 and the dog clutch 75 are simultaneously operated, the input of the vehicle driving motor is not transmitted to the output shaft 90 and is concentrated on the dog clutch 75 and the clutch 77, which may cause damage. There are concerns. The actuator of the embodiment operates the clutch 77 when it is in the second position P2 and operates the dog clutch 75 when it is in the third position P3. And the second position (P2) and the third position (P3) are located at both ends of each other in the trajectory of the slider (81). Therefore, according to the embodiment, there is no fear that the second position P2 and the third position P3 are simultaneously implemented. Also, the first position P1 exists between the second position P2 and the third position P3. Since both the clutch 77 and the dog clutch 75 are released when the slider 81 is in the first position, even if the slider 81 is between the second position P2 and the third position P3, There is no fear that the clutch 77 and the dog clutch 75 operate at the same time.

The actuator 80 of the embodiment is controlled so that the slider 81 can stay in the first position P1. In addition, the slider 81 positioned at the first position P1 can move directly to the second position P2 without passing through another position (the third position), and directly without passing through another position (the second position). It can move to the third position P3.

<Control and operation of reducer>

Hereinafter, with reference to FIGS. 5 to 10, the control and operation of the reducer of the embodiment will be described.

Referring to FIG. 5 , the slider 81 is positioned at a first position P1 . 6, when the slider 81 is in the first position P1, the slider 81 is in a state in which the diaphragm 82 is slightly elastically deformed. In this state, the pressure plate 772 connected to the action point 823 of the diaphragm 82 is spaced apart from the clutch 77 so that the clutch 77 is released, and the second dog clutch 752 is connected to the first dog clutch ( 751), so that the dog clutch 75 is released.

In this state, when the forward driving rotation of the vehicle driving motor is input through the input shaft 10 , the input shaft 10 and the sun gear 30 rotate integrally in one direction. Accordingly, the first planetary gear 41 rotates in the other direction and the second planetary gear 42 rotates in one direction, and the ring gear 60 also rotates in one direction. The carrier 50 supporting the planetary gear 40 receives a force to rotate in the other direction in response to the rotation of the sun gear 30 and the ring gear 60 . The carrier 50 is connected to the fixed end 71 through a one-way clutch 73, and the one-way clutch 73 allows one-way rotation of the carrier 50 with respect to the fixed end 71, but Since rotation in the other direction is prevented, the carrier 50 is maintained in a fixed state. Then, the rotational force of the input shaft 10 is decelerated, and the torque is also multiplied and transmitted to the output shaft 90 . In a state in which the input shaft is connected to the sun gear and the output shaft is connected to the ring gear, a gear ratio of 2 to 11 may be implemented.

As described above, in the state in which the slider 81 is in the first position P1, torque multiplication and deceleration are performed. Therefore, when a large torque is required to move the vehicle, for example, the vehicle starts to move from a standstill or when the inclination is high. When climbing the slope, the control unit 85 may cause the slider 81 to be in the first position P1.

The one-way clutch 73 operates when the input of the input shaft 10 is less than the load on the output shaft 90, that is, when the driver slows down the acceleration for a while or takes the foot off the accelerator pedal. This allows freewheeling beyond the reduction ratio for the input shaft 10 . This prevents the vehicle driving motor from acting as a load for vehicle movement when the driver briefly stops acceleration in an environment requiring acceleration with high torque. In particular, when acceleration is temporarily slowed or stopped in an environment requiring acceleration with a high torque, it is more preferable in terms of acceleration of the vehicle or smooth movement of the vehicle to allow the output shaft 90 to freewheel rather than to regenerate rotation.

This is to become an environment similar to a neutral environment in a conventional vehicle transmission. That is, according to the embodiment, when the slider 81 is in the first position P1, the torque is multiplied in the vehicle forward process, and when the input disappears, neutralization is achieved. In general, torque multiplication is performed in the acceleration process of the initial movement of the vehicle, the uphill process, etc. In these processes, the regenerative braking does not need to be operated because the input temporarily disappears. In this process, rather, the load of the vehicle driving motor itself is disconnected from the vehicle body by freewheeling of the one-way clutch 73, so that the moving distance of the vehicle can be made longer.

In addition, even when the one-way clutch 73 is freewheeling as described above, if an input is generated again due to the user pressing the accelerator pedal, etc., the one-way clutch 73 is locked up, so that the torque can be multiplied immediately.

According to the embodiment, since a state such as a so-called neutral is mechanically operated by the one-way clutch 73, there is no need for separate electronic control for implementing the neutral.

On the other hand, after the vehicle starts moving forward and the speed increases to a certain extent, driving at a higher rotational speed is required rather than driving at a high torque. At this time, the controller 85 rotates the motor 830 of the actuator 80 in the other direction as shown in FIG. 7 . Then, the worm gear 831 rotates in the other direction, the worm wheel gear 832 also rotates in the other direction, and the sliding member 833 also rotates in the other direction. Since the slider 81 is pressed forward by the elastic force of the diaphragm 82 , the slider 81 comes into contact with the sliding member 833 and moves forward.

When the diaphragm 82 is elastically restored by pushing the slider 81 forward, the pressure plate 772 connected to the action point 823 of the diaphragm 82 as shown in FIG. 8 engages the clutch 77. pressurized, and thus the clutch 77 operates. Also, as shown, the second dog clutch 752 is further away from the first dog clutch 751 .

When the clutch 77 operates, the carrier 50 and the ring gear 60 rotate integrally. Then, eventually, the rotational force of the input shaft 10 is directly connected to the output shaft (90). Accordingly, by the forward driving of the vehicle driving motor input through the input shaft 10 , the planetary gear set 20 rotates integrally in one direction. Since the one-way clutch 73 permits rotation of the carrier 50 with respect to the fixed end 71 in one direction, the planetary gear set 20 is allowed to rotate integrally with respect to the fixed end in one direction.

When the load applied to the vehicle driving motor for accelerating the vehicle gradually decreases while the vehicle is moving forward, the control unit 85 rotates the motor 830 in the other direction so that the slider 81 of the actuator 80 moves in the first direction. It is controlled to move from the position P1 to the second position P2.

The controller 85 may control the slider 81 to stay at the second position P2 while the vehicle moves at a certain speed. In this case, since the clutch 77 couples the two elements of the planetary gear set 20 , regenerative braking may be performed in the process of reducing the speed.

The control unit 85 recognizes the magnitude of the load required for the forward movement of the vehicle, for example, from an electric signal such as a vehicle driving motor, and sets the position of the slider 81 to a first position P1 or a second position P2. You can decide which one you want it to be in.

When the vehicle is reversing, the control unit 85 moves the slider 81 to the third position P3. When the vehicle is reversing, normally, the vehicle is temporarily stopped, so that the slider 81 is moved to the first position P1 by the control unit 85 . In this state, when the driver controls the transmission to reverse the vehicle, the controller 85 moves the slider 81 from the first position P1 to the third position P3.

At this time, the controller 85 rotates the motor 830 of the actuator 80 in one direction as shown in FIG. 9 . Then, the worm gear 831 rotates in one direction, the worm wheel gear 832 also rotates in one direction, and the sliding member 833 also rotates in one direction. The cam profile of the sliding member 833 overcomes the elastic force of the diaphragm 82 and pushes the slider 81 rearward.

When the slider 81 is moved to the third position P3, the elastic deformation of the diaphragm 82 is further increased, so that the pressure plate 772 is further away from the clutch 77, and the second dog clutch 752 is It operates in engagement with the first dog clutch 751. Accordingly, the carrier 50 is fixed without rotating in any direction.

When the driver presses the accelerator pedal with the reverse gear engaged, the vehicle drive motor rotates in the reverse direction. Accordingly, the input shaft 10 rotates in the other direction, and the sun gear 30 also rotates in the other direction integrally therewith. Accordingly, the first planetary gear 41 rotates in one direction and the second planetary gear 42 rotates in the other direction, and the ring gear 60 also rotates in the other direction. The carrier 50 supporting the planetary gear 40 receives a force to rotate in one direction in response to the rotation of the sun gear 30 and the ring gear 60 . Since the one-way clutch 73 allows one-way rotation of the carrier 50 with respect to the fixed end 71 , the one-way clutch 73 does not block the rotation of the carrier 50 . However, since the slider 81 moves to the third position P3 and the dog clutch 75 fixes the carrier 50 , the carrier 50 does not rotate. Then, the rotational force of the input shaft 10 is decelerated, and the torque is also multiplied and transmitted to the output shaft 90 .

Reversing of the vehicle is temporarily performed in the process of parking, etc., and long-distance driving is not performed by reversing itself. Therefore, it can be said that it is an environment that requires torque multiplication at low speed. In addition, since reversing does not continuously drive, it is desirable to immediately perform regenerative braking when acceleration is stopped while reversing.

According to the embodiment, when the vehicle is reversing, the dog clutch 75 is continuously engaged even if the driver does not accelerate for a while. Accordingly, the rotational force of the output shaft 90 is accelerated through the planetary gear set 20 and transmitted to the input shaft 10 , so that regenerative braking can be performed.

When the reverse is completed and the user puts the forward gear again, the actuator 80 returns the slider 81 to the first position P1.

As described above, according to the reducer of the embodiment, the first forward stage (first position), the second forward stage (second position), and the reverse (third position) are implemented by controlling one actuator 80 .

As described above, the present invention has been described with reference to the illustrated drawings, but the present invention is not limited by the embodiments and drawings disclosed in this specification, and a variety of It is obvious that variations can be made. In addition, even if the effect of the configuration of the present invention is not explicitly described and described while describing the embodiment of the present invention, it is natural that the effect predictable by the configuration should also be recognized.

1: Reducer
10: input shaft
101: neglected police department
102: input shaft bearing jaw
103: Ministry of Foreign Affairs
104: inner diameter
105: input shaft spline
20: planetary gear set
30: sun gear
40: planetary gear
41: first planetary gear
42: second planetary gear
50: carrier
51: carrier cover
60: ring gear
61: ring gear cover
70: casing
71: fixed end
711: small internal cervical region
712: bearing receiving part
713: Ministry of Internal Affairs and Communications
721: first needle bearing
722: second needle bearing
73: one-way clutch
75: fixed-release part (dog clutch), first clutch
751: first dog clutch (set side clutch)
752: second dog clutch (fixed end clutch)
77: clutch (wet multi-plate clutch), second clutch
771: clutch cover
772: pressure plate
773: snap ring
80: actuator
P1: 1st position - 1st stage forward
P2: 2nd position - 2nd stage forward
P3: 3rd position - Reverse 1st stage
81: slider
82: diaphragm
821: fulcrum
822: power point
823: point of action
83: drive unit
830: motor
831: worm gear (first gear)
832: worm wheel gear (second gear)
833: cam (sliding member)
84: thrust bearing
85: control unit
90: output shaft
901: output shaft spline
902: outer diameter
903: output shaft bearing jaw
904: output shaft flange
B: bearing

Claims (18)

A speed reducer (1) comprising an input shaft (10) to which a rotational force is input, an output shaft (90) to which a rotational force is output, and a planetary gear set (20) for transmitting the rotational force of the input shaft (10) to the output shaft (90),
The planetary gear set 20 includes:
sun gear 30;
a ring gear 60 surrounding the sun gear 30;
a planetary gear 40 disposed between the sun gear 30 and the ring gear 60 to transmit a rotational force between the sun gear 30 and the ring gear 60; and
Includes; carrier 50 for supporting the planetary gear 40;
The input shaft 10 is connected to transmit a rotational force to a first element selected from among the sun gear 30, the ring gear 60, and the carrier 50,
A second element selected from among the sun gear 30 , the ring gear 60 and the carrier 50 is connected to transmit a rotational force to the output shaft 90 ,
The third element selected from among the sun gear 30, the ring gear 60, and the carrier 50, allows rotation in one direction with respect to the fixed end 71 of the reducer 1, and restricts rotation in the other direction. It is connected to the fixed end 71 through the one-way clutch 73,
The third element is rotationally constrained or rotationally constrained with respect to the fixed end 71 by a fixing-releasing part 75 provided separately from the one-way clutch 73,
two selected elements of the first element, the second element and the third element are coupled or uncoupled by a clutch (77).
The method according to claim 1,
wherein the lock-release portion (75) and the clutch (77) are actuated and disengaged by a common actuator (80).
3. The method according to claim 2,
The actuator 80 has a first position P1 for disengaging the locking-release portion 75 and disengaging the clutch 77 , and a first position P1 for disengaging the locking-release portion 75 and disengaging the clutch 77 . a second position (P2) of actuating (77) and a third position (P3) of actuating the lock-release portion (75) and disengaging the clutch (77).
4. The method according to claim 3,
The second position (P2) is located farthest from the third element, and the third position (P3) is located closest to the third element.
The method according to claim 1,
The first element is a sun gear (30), and the second element is a ring gear (60).
6. The method of claim 5,
The planetary gear 40 includes a first planetary gear 41 meshing with the sun gear 30 and a second planetary gear 42 meshing with the ring gear 60,
The first planetary gear (41) and the second planetary gear (42) mesh with each other, a reduction gear.
3. The method according to claim 2,
The fastening-releasing portion (75) includes a first dog clutch (751) fixed to the third element and a second dog clutch (752) fixed to the actuator (80).
The method according to claim 1,
The clutch 77 is a wet multi-plate clutch.
The method according to claim 1,
The two elements coupled or uncoupled by the clutch (77) are a carrier (50) and a ring gear (60).
10. The method of claim 9,
The carrier (50) has a carrier cover (51) extending outwardly in the radial direction,
The ring gear 60 has a ring gear cover 61 extending outward in the radial direction,
The carrier cover (51) and the ring gear cover (61) are connected to each other by the clutch (77) radially outside the ring gear (60).
3. The method according to claim 2,
The actuator (80) is rotation-limited with respect to the fixed end, the slider (81) is movable in the axial direction along the fixed end;
a diaphragm (82) connected to the slider (81) and configured to press the clutch (77) or release the pressure to the clutch (77) according to the axial movement position of the slider (81); and
and a driving unit (83) for providing a force for moving the slider (81) in the axial direction.
12. The method of claim 11,
The driving unit 83 includes:
a worm wheel gear (832) installed rotatably relative to the fixed end, limited in movement in the axial direction with respect to the fixed end, and connected to the cam with the slider (81); and
a worm gear 831 engaged with the worm wheel gear 832;
A reducer including; a motor 830 for rotating the worm gear 831 in a forward or reverse direction.
12. The method of claim 11,
The slider (81) and the diaphragm (82) are connected by a bearing (84).
12. The method of claim 11,
The fulcrum of the diaphragm 82 is supported by a clutch cover 771 connected to the clutch 77,
The force point of the diaphragm 82 is connected to the slider 81 radially inside the fulcrum of the diaphragm 82,
The operating point of the diaphragm (82) is connected to a pressure plate (772) that presses the clutch (77) radially outside the fulcrum of the diaphragm (82).
15. The method of claim 14,
The slider 81 has a first position P1 for disengaging the lock-disengaging portion 75 and disengaging the clutch 77, and a first position P1 for disengaging the lock-disengaging portion 75 and disengaging the clutch 77. moving to a second position (P2) of operating 77) and a third position (P3) of operating the lock-release unit (75) and disengaging the clutch (77);
The elastic force of the diaphragm 82 presses the slider 81 to move from the third position P3 to the first position P1 and from the first position P1 to the second position P2. , reducer.
As a control method of any one of claims 1 to 15,
When a driving force for forward movement starts to be input to the input shaft 10 , the lock-release unit 75 is released and the clutch 77 is released so that the one-way clutch 73 engages the third element. A method of controlling a speed reducer including a; a step of multiplying a forward torque to restrict rotation with respect to the fixed end (71).
As a control method of any one of claims 1 to 15,
When the input of the driving force for forward movement is continuously input to the input shaft 10 and the multiplication of the torque is not required, the lock-release unit 75 is released and the clutch 77 is operated to operate the planetary gear set 20 ) integrally rotated and the one-way clutch (73) freewheeling the forward direct connection step; including a control method of a reducer.
As a control method of any one of claims 1 to 15,
When a driving force for reverse is input to the input shaft 10 , the lock-release unit 75 is operated and the clutch 77 is released to cause torque multiplication through the planetary gear set 20 . Torque multiplication step; including, the control method of the reducer.

Images