WO2024029112A1

WO2024029112A1 - Bogie

Info

Publication number: WO2024029112A1
Application number: PCT/JP2023/005856
Authority: WO
Inventors: 俊朗浅野間; 篤湯下; 浩二内田; 浩幸河野; 康隆福家; 光史谷本; 雪秀矢延; 真史中窪
Original assignee: 三菱重工業株式会社
Priority date: 2022-08-05
Filing date: 2023-02-17
Publication date: 2024-02-08
Also published as: JP2024022191A

Abstract

This bogie is provided with: a bogie frame; an axle that is located beneath the bogie frame and that extends horizontally; a motor that is provided relatively displaceable in the vertical direction with respect to the bogie frame and that rotates the axle about the axis of the axle; a power transmission coupling that coaxially links the axle and the motor drive shaft; a motor bracket that is provided on the outer surface of the motor and that with respect to the axle is located radially outwardly from the axis; an elastic member that vertically connects the bogie frame and the motor bracket and that is elastically deformable vertically; a latch that regulates the vertical length of the elastic member; and a reverse centrifugal clutch that is provided annularly on the outer periphery of the axle, that supports the motor bracket along the radially inner side, and that can diametrically contract during rotation and diametrically expand when rotation is halted, undergoing centrifugal force produced by unitary rotation with the axle.

Description

trolley

The present disclosure relates to a trolley.
This application claims priority to Japanese Patent Application No. 2022-125592 filed in Japan on August 5, 2022, the contents of which are incorporated herein.

Patent Document 1 discloses a direct-drive electric bogie for railway vehicles that has a structure that directly transmits the torque of a motor to an axle. This truck includes a truck frame that fixedly supports the motor.

Japanese Patent Application Publication No. 11-301471

By the way, for example, when a passenger gets on or off the vehicle, the weight of the truck frame changes, causing the truck frame to move up and down. In the truck described in Patent Document 1, the motor is displaced as the truck frame moves up and down, resulting in relative displacement of the motor with respect to the axle. Relative displacement of the motor with respect to the axle causes a decrease in power transmission efficiency and an increase in vibration during driving.

The present disclosure has been made to solve the above problems, and an object of the present disclosure is to provide a truck that can absorb the relative displacement of the motor with respect to the axle.

In order to solve the above problems, a truck according to the present disclosure includes a truck frame, an axle located below the truck frame and extending in the horizontal direction, and a truck that is displaceable relative to the truck frame in the vertical direction. a motor that rotates the axle around the axis of the axle; a power transmission joint that coaxially connects the axle and the drive shaft of the motor; a motor bracket located on the outside in the radial direction; an elastic member that vertically connects the truck frame and the motor bracket and is elastically deformable in the vertical direction; and a latch that defines the length of the elastic member in the vertical direction. is provided in an annular shape on the outer circumferential side of the axle, supports the motor bracket from the inside in the radial direction, is capable of contracting in diameter during rotation in response to centrifugal force generated by rotating together with the axle, and expands when rotation stops. and a reversible centrifugal clutch.

According to the truck of the present disclosure, relative displacement of the motor with respect to the axle can be absorbed.

FIG. 1 is a diagram showing the configuration of a truck according to a first embodiment of the present disclosure. FIG. 1 is a diagram showing the configuration of main parts of a truck according to a first embodiment of the present disclosure. FIG. 2 is a diagram showing a latch according to a first embodiment of the present disclosure. FIG. 3 is a diagram showing the configuration of a reverse centrifugal clutch when the bogie is stopped according to the first embodiment of the present disclosure. FIG. 2 is a diagram showing the configuration of a reverse centrifugal clutch when the bogie is running according to the first embodiment of the present disclosure. It is a figure explaining the action of the reverse centrifugal clutch when the bogie is stopped according to the first embodiment of the present disclosure. It is a figure explaining the action of the reverse centrifugal clutch when the trolley is traveling according to the first embodiment of the present disclosure. FIG. 7 is a diagram showing a latch according to a second embodiment of the present disclosure. It is a figure which shows the structure of the principal part of the trolley|bogie based on 3rd embodiment of this indication.

<First embodiment>
Hereinafter, a truck 10 according to a first embodiment of the present disclosure will be described with reference to FIGS. 1 to 7.

(vehicle)
As shown in FIG. 1, a vehicle 1 in which a bogie 10 of this embodiment is used is, for example, a railway vehicle. The vehicle 1 includes a vehicle body 2 and a truck 10. A space is provided inside the vehicle body 2 for passengers to get on and off the vehicle.

Hereinafter, the vertical up-down direction may be simply referred to as the "up-down direction", and the traveling direction of the vehicle 1 may be simply referred to as the "front-rear direction".

(trolley)
The truck 10 supports the vehicle body 2 from below and runs on a rail L along the ground. The rail L extends in one direction. A pair of rails L are provided facing each other in a direction orthogonal to the longitudinal direction of the rails L. The truck 10 includes a truck frame 20, an axle 11, a holding mechanism 12, wheels 13, an axle spring 14, a motor 15, a power transmission joint 16, a motor bracket 19, a latch 40, and a reverse centrifugal clutch 50. Equipped with.

(Dolly frame)
The truck frame 20 is provided at a position spaced upward from the rail L. The truck frame 20 supports the vehicle body 2 from below. That is, the truck frame 20 supports the weight of the occupant from below. The truck frame 20 is a frame body extending in the horizontal direction.

(axle)
The axle 11 is located below the truck frame 20. The axle 11 is formed into a cylindrical shape extending in the horizontal direction.
Hereinafter, the axis O of the axle 11 may be simply referred to as "axis O", the radial direction of axis O may be simply referred to as "radial direction", and the circumferential direction of axis O may simply be referred to as "circumferential direction". The direction of the axis O is perpendicular to the longitudinal direction of the rail L. That is, the axis O direction is perpendicular to the front-rear direction.

(holding mechanism)
The holding mechanism 12 is a member that holds the axle 11. A pair of holding mechanisms 12 are provided on both sides of the motor 15 in the direction of the axis O. Each holding mechanism 12 is provided between the motor 15 and the wheel 13 in the direction of the axis O. The holding mechanism 12 includes a bearing box 12a and a first bearing 12b. The bearing box 12a is provided so as to sandwich the axle 11 from above and below. The first bearing 12b is provided between the axle 11 and the bearing box 12a. The first bearing 12b supports the axle 11 rotatably around the axis O.

(Wheel)
One wheel 13 is provided at each end of the axle 11 in the axis O direction. The wheel 13 is formed into a disc shape. The thickness direction of the wheel 13 coincides with the axis O direction. The wheel 13 is connected to the end of the axle 11 at the center. The wheel 13 is fixed to the axle 11 and rotates together with the axle 11. The wheels 13 rotate on the rails L.

(axis spring)
The shaft spring 14 is provided between the truck frame 20 and the holding mechanism 12. The shaft spring 14 vertically connects the truck frame 20 and the bearing box 12a. The shaft spring 14 is a coil spring that extends in the vertical direction and absorbs vibrations in the vertical direction. The shaft spring 14 supports the truck frame 20 from below. Therefore, when the weight changes as a passenger gets on and off the vehicle, the truck frame 20 moves up and down.

(motor)
The motor 15 is provided below the truck frame 20 at an intermediate position between the pair of wheels 13 in the direction of the axis O. The motor 15 is provided to be movable relative to the truck frame 20 in the vertical direction. The motor 15 rotates the axle 11 around the axis O. The motor 15 is a direct drive type motor 15. The motor 15 includes a stator 15a, a rotor 15b, and a drive shaft 15c. The stator 15a is formed into a cylindrical shape with a central axis along the axis O of the axle 11. The rotor 15b is provided radially inside the stator 15a. The rotor 15b is formed in a cylindrical shape with its center axis along the axis O of the axle 11, similarly to the stator 15a. The rotor 15b is inserted through the stator 15a and rotates around the axis O. Like the stator 15a, the drive shaft 15c is a hollow shaft formed in a cylindrical shape with its center axis along the axis O of the axle 11. The drive shaft 15c is inserted through the rotor 15b and fixed to the inner peripheral surface of the rotor 15b. The drive shaft 15c is rotatably provided around the axis O together with the rotor 15b. A power transmission joint 16 is provided at one end of the drive shaft 15c in the direction of the axis O.

(power transmission joint)
The power transmission joint 16 is provided between the motor 15 and the holding mechanism 12 in the direction of the axis O. The power transmission joint 16 coaxially connects the axle 11 and the drive shaft 15c of the motor 15, and transmits the power of the motor 15 to the axle 11. The power transmission joint 16 includes a motor-side joint member 16a, an axle-side joint member 16b, and a coupling 16c. The motor-side joint member 16a is formed in the shape of a flange that projects from the outer peripheral surface of the drive shaft 15c in the radial direction. The motor side joint member 16a is fixed to the drive shaft 15c and rotates around the axis O together with the drive shaft 15c. The axle-side joint member 16b is fixed to the outer peripheral surface of the axle 11. The axle-side joint member 16b has a cylindrical portion 17 and a flange portion 18. The axle 11 is press-fitted into the cylindrical portion 17 . The flange portion 18 projects from the outer peripheral surface of the cylindrical portion 17 in the radial direction. The flange portion 18 is formed integrally with the cylinder portion 17. The coupling 16c is provided between the motor-side joint member 16a and the axle-side joint member 16b. The coupling 16c connects the motor-side joint member 16a and the axle-side joint member 16b. The coupling 16c is formed to be elastically deformable. The power transmission joint 16 absorbs the relative displacement of the motor 15 with respect to the axle 11 by deforming the coupling 16c.

(motor bracket)
As shown in FIGS. 1 and 2, the motor bracket 19 is provided on the outer surface of the motor 15 and is located on the outside of the axle 11 in the radial direction of the axis O. In this embodiment, one motor bracket 19 is provided on each side of the motor 15 on both sides in the axis O direction. Each motor bracket 19 is fixed to the motor 15. The motor bracket 19 is formed in a T-shape when viewed from the axis O direction. The axle 11 is inserted into the motor bracket 19 .

(elastic member)
Two elastic members 30 are provided on each motor bracket 19. One elastic member 30 is provided on the upper surface of each motor bracket 19 at both ends in the front-rear direction. The elastic member 30 connects the truck frame 20 and the motor bracket 19 in the vertical direction. The elastic member 30 is a member that can be elastically deformed in the vertical direction. The elastic member 30 is, for example, a coil spring extending in the vertical direction.

(latch)
The latch 40 defines the length of the elastic member 30 in the vertical direction. In this embodiment, the latch 40 is provided at the rear with respect to the motor 15. The latch 40 includes a first latch member 41, a second latch member 42, and a latch spring 43.

The first latch member 41 is provided on the truck frame 20. In this embodiment, the first latch member 41 is provided at the rear of the motor 15. The first latch member 41 extends downward from the truck frame 20. The first latch member 41 is fixed to the truck frame 20. The first latch member 41 has a first latch base 44 and a latch groove 45. The first latch base 44 is formed into a plate shape extending downward from the truck frame 20. The latch groove 45 is formed on the side surface of the first latch base 44 facing the motor 15 side. A plurality of latch grooves 45 are provided in the vertical direction. The latch groove 45 is open to the motor 15 side. The latch groove 45 extends in the direction of the axis O.

The second latch member 42 is provided on the motor bracket 19 and faces the first latch member 41. The second latch member 42 is provided so as to be engageable with the first latch member 41. In this embodiment, the second latch member 42 has a latch protrusion 46 . As shown in FIG. 3, a plurality of latch protrusions 46 are provided in parallel in the vertical direction. The latch protrusion 46 is provided so as to be protrusive and retractable. With the latch protrusion 46 in the protruding state, the latch protrusion 46 and the latch groove 45 engage with each other. Further, when the latch protrusion 46 is in the retracted state, the engagement between the latch protrusion 46 and the latch groove 45 is released.

The latch spring 43 is provided inside the motor bracket 19. The latch spring 43 pushes the latch protrusion 46 outward from the inside of the motor bracket 19 and causes the latch protrusion 46 to protrude from the motor bracket 19 . When an external force is applied to the latch protrusion 46 , the latch spring 43 contracts, and the latch protrusion 46 moves inside the motor bracket 19 .

(Reverse centrifugal clutch)
The reverse centrifugal clutch 50 is provided in an annular shape on the outer peripheral side of the axle 11. The reverse centrifugal clutch 50 rotates integrally with the axle 11. The reverse centrifugal clutch 50 supports the motor bracket 19 from the inside in the radial direction when the bogie is stopped. The reverse centrifugal clutch 50 of this embodiment is in contact with the inner peripheral surface 19a of the motor bracket 19 when the bogie is stopped. The reverse centrifugal clutch 50 is capable of contracting in diameter when rotating in response to centrifugal force generated by rotating integrally with the axle 11 when the bogie is traveling, and is capable of expanding in diameter when the rotation is stopped. As shown in FIGS. 4 and 5, the reverse centrifugal clutch 50 includes a clutch base 51, a clutch shoe 52, a rotating pin 53, a spring 54, a movable pin 55, a clutch connecting portion 56, and a centrifugal force increasing mechanism. 57. FIG. 4 shows the state when the bogie is stopped, and FIG. 5 shows the state when the bogie is running.

The clutch base 51 is formed into an annular plate shape that covers the axle 11 from the outer peripheral side. The clutch base 51 is fixed to the outer peripheral surface of the axle 11 and rotates together with the axle 11. Clutch shoe 52 is provided on clutch base 51. A plurality of clutch shoes 52 are provided side by side in the circumferential direction. The clutch shoe 52 is formed in a V-shape that is convex radially outward when viewed from the axis O direction. One end of the clutch shoe 52 is connected to the clutch base 51 by a rotating pin 53. The clutch shoe 52 is rotatably provided around a rotating pin 53. The clutch shoe 52 spreads radially outward from the outer peripheral edge of the clutch base 51 when the bogie is stopped. Therefore, when the bogie is stopped, the outer circumferential edge of the clutch shoe 52 becomes the outer circumferential edge of the reverse centrifugal clutch 50. The clutch shoe 52 rotates inward in the radial direction and moves inward in the radial direction from the outer circumferential edge of the clutch base 51 when the truck is traveling. Therefore, when the bogie is stopped, the outer circumferential edge of the clutch base 51 becomes the outer circumferential edge of the reverse centrifugal clutch 50.

The spring 54 is provided on the clutch base 51 similarly to the clutch shoe 52. The spring 54 extends along the axle 11. One end of the spring 54 is fixed to the rotation pin 53. A movable pin 55 is provided at the other end of the spring 54. The movable pin 55 is fixed to the other end of the spring 54, and is provided so as to be movable on the clutch base 51 in the circumferential direction along the inner peripheral edge of the clutch base 51. The movable pin 55 is located at a lock position P where the clutch shoe 52 is fixed when the bogie is stopped. Note that the clutch shoe 52 is fixed by a locking mechanism (not shown). This locking mechanism operates when the movable pin 55 is located at the locking position P to fix the clutch shoe 52. When the movable pin 55 is removed from the lock position P, the clutch shoe 52 is released from being fixed by the lock mechanism. Further, when the bogie is traveling, the spring 54 expands in the circumferential direction on the opposite side from the rotating pin 53 due to centrifugal force. As a result, the movable pin 55 moves from the lock position P in the circumferential direction away from the rotary pin 53, and the clutch shoe 52 is released from being fixed.

The movable pin 55 is connected to the other end of the clutch shoe 52 by a clutch connecting portion 56. The clutch connecting portion 56 is, for example, a string-like member.

Furthermore, the movable pin 55 is provided with a centrifugal force increasing mechanism 57. The centrifugal force increasing mechanism 57 increases the centrifugal force applied to the spring 54. The centrifugal force increasing mechanism 57 includes a weight connecting portion 57a, a weight 57b, and a weight guide 57c. The weight connecting portion 57a is a member extending in one direction, and may be a wire, for example. In addition, examples of the weight connecting portion 57a include a rod, etc. in addition to a wire. A movable pin 55 is connected to one end of the weight connecting portion 57a. Further, a weight 57b is connected to the other end of the weight connecting portion 57a. The weight 57b moves along the weight guide 57c as centrifugal force increases or decreases. Weight guide 57c defines the moving direction of weight 57b. The weight guide 57c is formed, for example, in a shape to sandwich the weight 57b from both sides in a direction intersecting the extending direction of the weight connecting portion 57a. The weight guide 57c is, for example, formed into a cylindrical shape in which the weight 57b is accommodated.

When the bogie travels, when the spring 54 expands due to the centrifugal force of the weight 57b and the movable pin 55 moves in the circumferential direction, the clutch connecting portion 56 moves the other end of the clutch shoe 52 radially inward. When the truck 10 stops, the centrifugal force disappears, the spring 54 contracts, and the movable pin 55 moves to the lock position P. At this time, the movable pin 55 moves while the clutch connecting portion 56 pulls the other end of the clutch shoe 52. Therefore, the clutch shoe 52 rotates around the rotating pin 53, and the other end of the clutch shoe 52 moves radially outward.

4 and 5, mechanisms such as the rotary pin 53, spring 54, movable pin 55, clutch connection part 56, etc. are disclosed in detail only for one clutch shoe 52, but in reality, other A similar mechanism is provided for all clutch shoes 52 as well. In addition, in FIG. 4, the state of one clutch shoe 52 when the truck is running is indicated by a chain double-dashed line.

Further, in this embodiment, the case where the reverse centrifugal clutch 50 has the centrifugal force increasing mechanism 57 has been described, but if the movable pin 55 is sufficiently heavy, the spring 54 can be expanded by the centrifugal force of the movable pin 55. , the centrifugal force increasing mechanism 57 may not be provided. Further, the centrifugal force increasing mechanism 57 may be any mechanism that increases the centrifugal force applied to the spring 54, and is not limited to the mechanism having the weight connecting portion 57a, the weight 57b, and the weight guide 57c described above.

(effect)
Hereinafter, the operation of the trolley 10 of this embodiment will be explained with reference to FIGS. 1, 3, 6, and 7.
Basically, the relative position between the axle 11 and the truck frame 20 changes as a passenger gets on and off the truck when the truck is stopped.
In response to changes in the relative position between the axle 11 and the truck frame 20, the reverse centrifugal clutch 50 expands in diameter and becomes larger when the truck is stopped (when the motor 15 is stopped) to push the motor bracket 19 up or down. It is provided. Since the motor bracket 19 is fixed to the motor 15, the motor 15 is pushed up or down by the reverse centrifugal clutch 50. The operation of this reverse centrifugal clutch 50 will be explained in detail below.

When the bogie is stopped, the reverse centrifugal clutch 50 expands in diameter to become larger and comes into contact with the inner peripheral surface 19a of the motor bracket 19, as shown in FIG. Thereby, when the bogie is stopped, the load from the axle 11 is favorably transmitted to the motor bracket 19 via the reverse centrifugal clutch 50. In this state, for example, as shown in FIG. 1, a case will be considered in which the weight of the truck 10 increases due to an occupant getting on the vehicle, and a downward load is applied to the truck frame 20, causing the truck frame 20 to descend. Since the motor bracket 19 is fixed to the motor 15 and the reverse centrifugal clutch 50 is in contact with the motor bracket 19, the reaction force from the ground acting on the axle 11 is transferred to the motor 15 through the reverse centrifugal clutch 50. communicated. As a result, the motor 15 is pushed up by the reverse centrifugal clutch 50. Then, the elastic member 30 contracts in the vertical direction, and the upward load and downward reaction force are absorbed. Thereby, the height of the motor 15 is maintained.

On the other hand, if the number of trucks 10 increases due to, for example, an occupant getting off the vehicle, the downward load applied to the truck frame 20 decreases, and the truck frame 20 rises. At this time, the reverse centrifugal clutch 50 expands in diameter to become larger and is in contact with the motor bracket 19, so the reverse centrifugal clutch 50 pushes down the motor 15 via the motor bracket 19. Then, the elastic member 30 extends in the vertical direction. As a result, upward displacement of the truck frame 20 is absorbed, and the height of the motor 15 is maintained.

When the bogie travels, as shown in FIG. 7, the clutch shoe 52 of the reverse centrifugal clutch 50 moves radially inward, and the reverse centrifugal clutch 50 contracts in diameter and becomes smaller. As a result, the outer circumferential edge of the reverse centrifugal clutch 50 is separated from the inner circumferential surface 19a of the motor bracket 19. That is, the reverse centrifugal clutch 50 does not come into contact with the motor bracket 19 when the bogie is running. Therefore, the axle 11 can rotate around the axis O without being affected by friction between the reverse centrifugal clutch 50 and the motor bracket 19.

Further, as shown in FIG. 3, the elastic member 30's elastic length is defined by the latch 40. When the trolley is stopped, the weight of the trolley 10 fluctuates greatly due to passengers getting on and off the vehicle. As a result, when the bogie is stopped, an external force is applied to the latch 40 that is sufficient to compress the latch spring 43 and move the latch protrusion 46 inside the motor bracket 19. Therefore, when the bogie is stopped, the elastic member 30 can expand and contract in the vertical direction, and the vertical position of the motor 15 with respect to the bogie frame 20 can be adjusted. On the other hand, when the bogie is running, no occupants are getting on or off, so no external force is applied to the latch 40 to compress the latch spring 43 and move the latch protrusion 46 inside the motor bracket 19. Therefore, when the bogie is running, the engagement between the latch groove 45 and the latch protrusion 46 is maintained, and the vertical expansion/contraction length of the elastic member 30 is maintained. That is, when the truck is traveling, the vertical position of the motor 15 with respect to the truck frame 20 is maintained.

Hereinafter, the advantages of the trolley 10 of this embodiment will be explained.

According to this embodiment, the truck 10 includes a motor bracket 19 that is provided on the outer surface of the motor 15 and is located on the outside in the radial direction of the axis O with respect to the axle 11, and a truck frame 20 and the motor bracket 19 in the vertical direction. An elastic member 30 that is connected and can be elastically deformed in the vertical direction; a latch 40 that defines the length of the elastic member 30 in the vertical direction; The reverse centrifugal clutch 50 is supported by the axle shaft 11 and is capable of contracting in diameter when rotating in response to centrifugal force generated by rotating integrally with the axle 11, and expanding the diameter when the rotation is stopped.

According to this embodiment, when the bogie is stopped, the reverse centrifugal clutch 50 can support the motor bracket 19 from the inside in the radial direction. In this state, when the weight of the truck 10 increases due to an occupant getting on the vehicle, a downward load is applied to the truck frame 20, causing the truck frame 20 to descend. In contrast, an upward reaction force from the ground is applied to the axle 11. At this time, the reverse centrifugal clutch 50 receives an upward reaction force from the axle 11 and pushes up the motor bracket 19. This suppresses eccentricity of the axle 11 with respect to the motor 15. Conversely, when the weight of the truck 10 decreases due to the occupant getting off the vehicle, the truck frame 20 rises. In contrast, the motor 15 also tries to rise together with the truck frame 20, but the eccentricity of the axle 11 with respect to the motor 15 is suppressed by the reverse centrifugal clutch 50. In this manner, when the bogie is stopped, the elastic member 30 expands and contracts in the vertical direction while the eccentricity of the axle shaft 11 with respect to the motor 15 is suppressed by the reverse centrifugal clutch 50. Therefore, displacement of the motor 15 in the vertical direction is well absorbed, and the height of the motor 15 is maintained. That is, the truck 10 can sufficiently absorb the relative displacement of the motor 15 with respect to the axle 11.

Further, when the bogie is traveling, the diameter of the reverse centrifugal clutch 50 is reduced and the motor bracket 19 is no longer pushed up by the reverse centrifugal clutch 50, but the height of the motor bracket 19 is maintained by the latch 40. That is, a state in which the relative displacement of the motor 15 with respect to the axle 11 is sufficiently absorbed is maintained.
In this manner, the bogie 10 can sufficiently absorb the relative displacement of the motor 15 with respect to the axle 11 when the bogie is stopped, and can maintain a state in which the relative displacement of the motor 15 is absorbed when the bogie is running. Therefore, the amount of displacement to be absorbed by the power transmission joint 16 is reduced, and the degree of freedom in designing the power transmission joint 16 is increased. Furthermore, since the stress amplitude of the power transmission joint 16 is reduced, the life of the power transmission joint 16 can be extended.

Further, a direct drive system is adopted for the motor 15, and the motor 15 and the axle 11 are directly connected via a power transmission joint 16. Therefore, the weight and volume of the truck 10 are reduced compared to a case where the motor 15 and the axle 11 are connected via, for example, a gear box. Further, the motor 15 is suspended from the truck frame 20 via an elastic member 30. As a result, at least a portion of the weight of the motor 15 is borne by the truck frame 20, so the weight of the wheels 13 and the axle 11 is reduced. Therefore, it is possible to reduce rail damage.

In this embodiment, the latch 40 includes a first latch member 41 provided on the truck frame 20 and a second latch member provided on the motor bracket 19 that faces the first latch member 41 and is engageable with the first latch member 41. and two latch members 42.

According to this embodiment, the latch 40 can engage the first latch member 41 and the second latch member 42 when the truck is traveling. Thereby, the height of the motor bracket 19 is maintained, and the state in which eccentricity of the axle shaft 11 is suppressed is reliably maintained.

<Second embodiment>
Hereinafter, a truck 210 according to a second embodiment of the present disclosure will be described with reference to FIG. 8. Configurations similar to those of the first embodiment described above will be given the same names and numerals, and descriptions thereof will be omitted as appropriate.

In this embodiment, as shown in FIG. 8, the latch 240 has a lock release mechanism 243. The lock release mechanism 243 utilizes the voltage of the motor 15 to engage the first latch member 41 and the second latch member 42 and release the engagement between the first latch member 41 and the second latch member 42 .

According to this embodiment, in order to engage the first latch member 41 and the second latch member 42 and release the engagement between the first latch member 41 and the second latch member 42, a special There is no need to provide a power source. This further reduces the weight and volume of the truck 210.

<Third embodiment>
Hereinafter, a truck 310 according to a third embodiment of the present disclosure will be described with reference to FIG. 9. Configurations similar to those of the first embodiment described above will be given the same names and numerals, and descriptions thereof will be omitted as appropriate. Note that in FIG. 9, the structure of the reverse centrifugal clutch 50 is simplified.

As shown in FIG. 9, the motor bracket 319 includes a positioning frame 319a and a protruding plate portion 319b.
The positioning frame 319a is provided on the end face of the motor 15 in the axis O direction. The positioning frame 319a has a rectangular frame portion 319d and an intermediate rod 319e. The rectangular frame portion 319d is formed in a rectangular frame shape that extends in the vertical direction when viewed from the axis O direction. The upper end of the rectangular frame portion 319d is fixed to the outer peripheral surface of the motor 15. The intermediate rod 319e is provided inside the rectangular frame portion 319d at an intermediate position in the vertical direction of the rectangular frame portion 319d. The intermediate rod 319e extends in the front-rear direction and connects the front edge and rear edge of the rectangular frame portion 319d. The inner surface of the rectangular frame portion 319d and the radially oriented surface of the intermediate rod 319e form an inner circumferential surface 319c of the positioning frame 319a.

The protruding plate portion 319b protrudes from the outer peripheral surface of the motor 15 in the front-rear direction. Each protruding plate portion 319b is connected to the truck frame 20 by an elastic member 30.

The latch 340 includes an interlocking mechanism 360 in addition to the first latch member 41 and the second latch member 342. The interlocking mechanism 360 engages the first latch member 41 and the second latch member 342 and engages the first latch member 41 and the second latch member 342 in conjunction with the diameter contraction and expansion of the reverse centrifugal clutch 50. cancel the connection. The interlocking mechanism 360 includes a first pin 361, a first bar 362, a second pin 363, a second bar 364, a third pin 365, a third bar 366, and a fourth pin 367.

The first pin 361 is provided on the end face of the motor 15 in the axis O direction. A first pin 361 rotatably connects a first bar 362 to the motor 15 . The first bar 362 is a rod-shaped member that extends in the vertical direction. The upper end of the first bar 362 is connected to the annular portion by a first pin 361. The first bar 362 is provided at a position where it contacts the reverse centrifugal clutch 50. The second pin 363 is provided at the lower end of the first bar 362. A second pin 363 rotatably connects a second bar 364 to the first bar 362 . The second bar 364 is a rod-shaped member that extends in the front-rear direction. The front end of the second bar 364 is connected to the first bar 362 by a second pin 363. A third pin 365 is provided at the rear end of the second bar 364. A third pin 365 rotatably connects a third bar 366 to the second bar 364 . The third bar 366 is a rod-shaped member that extends in the vertical direction. The lower end of the third bar 366 is connected to the second bar 364 by a third pin 365. A fourth pin 367 is provided at the middle portion of the third bar 366 in the extending direction. The fourth pin 367 rotatably connects the third bar 366 to the protruding plate portion 319b of the motor bracket 319.

A second latch member 342 is provided at the upper end of the third bar 366. The second latch member 342 has a second latch base 346 and a latch protrusion 347 . Second latch base 346 is secured to third bar 366 . The latch protrusion 347 protrudes from the second latch base 346 toward the first latch member 41 .

Next, the operation of the reverse centrifugal clutch 50 in this embodiment will be explained.
Basically, in this embodiment as well as in the first embodiment, the relative position between the axle 11 and the bogie frame 20 changes as a passenger gets on and off the bogie when the bogie is stopped.
In response to changes in the relative position between the axle 11 and the truck frame 20, the reverse centrifugal clutch 50 expands in diameter and becomes larger when the truck is stopped (when the motor 15 is stopped) to push up or down the positioning frame 319a. It is provided. Since the positioning frame 319a is fixed to the motor 15, the motor 15 is pushed up or down by the reverse centrifugal clutch 50.

A change in the position of the axle 11 changes the position of the motor 15 via the reverse centrifugal clutch 50 and the positioning frame 319a. At this time, the height of the motor 15 (the vertical position of the motor 15) is adjusted so that the axis O of the axle 11 and the center axis of the motor 15 coincide.

When the truck 10 starts traveling, the reverse centrifugal clutch 50 contracts in diameter and becomes smaller, and no longer contacts the positioning frame 319a. Therefore, rotation of the axle 11 is not inhibited by the reverse centrifugal clutch 50.

Next, the operation of the interlocking mechanism 360 will be explained.
In FIG. 9, the interlocking mechanism 360 when the bogie is traveling is indicated by a solid line, and the interlocking mechanism 360 when the bogie is stopped is indicated by a two-dot chain line. When the bogie is traveling, the reverse centrifugal clutch 50 is reduced in diameter, and the first bar 362 of the interlocking mechanism 360 extends perpendicularly to the horizontal plane. In this state, the third bar 366 also extends perpendicularly to the horizontal plane like the first bar 362, and the second latch member 342 is engaged with the first latch member 41.

When the bogie is stopped, the clutch shoes 52 of the reverse centrifugal clutch 50 expand, and the reverse centrifugal clutch 50 expands in diameter. As a result, the first bar 362 of the interlocking mechanism 360 is pushed toward the first latch member 41 . Then, the third bar 366 rotates around the fourth pin 367, and the second latch member 342 separates from the first latch member 41. In this way, when the bogie is stopped, the engagement between the first latch member 41 and the second latch member 342 is released.

The advantages of the trolley 310 of this embodiment will be explained below.
In this embodiment, the latch 340 engages the first latch member 41 and the second latch member 342 in conjunction with the diameter contraction and expansion of the reverse centrifugal clutch 50, and the engagement between the first latch member 41 and the second latch member. 342 is provided.

According to this embodiment, the trolley 310 immediately engages the first latch member 41 and the second latch member 342 and engages the first latch member 41 and the second latch member 342 in response to switching between the running state and the stopped state. The member 342 can be disengaged. Furthermore, in order to engage the first latch member 41 and the second latch member 342 and disengage the first latch member 41 and the second latch member 342, it is necessary to provide a special power source in the trolley 310. disappears. This further reduces the weight and volume of the truck 310.

(Other embodiments)
Although the embodiment of the present disclosure has been described above in detail with reference to the drawings, the specific configuration is not limited to this embodiment, and includes design changes within the scope of the gist of the present disclosure. .

In addition, although the said embodiment demonstrated the case where the trolley|bogie 10,210,310 is a railway vehicle trolley, it is not restricted to this. The

trolleys

10, 210, and 310 may be used, for example, as forklifts or electrically assisted trolleys that are manually pushed by people when transporting heavy objects.

In the above embodiment, a case has been described in which the reverse centrifugal clutch 50 contacts the

motor bracket

19, 319 and directly pushes it up or down, but the invention is not limited to this. A second bearing (not shown) may be provided on the outer peripheral side of the reverse centrifugal clutch 50, and the

motor brackets

19, 319 may be pushed up or down via this second bearing.

<Additional notes>
The

carts

10, 210, and 310 described in each embodiment are understood as follows, for example.

(1) The

carts

10, 210, 310 according to the first aspect include a cart frame 20, an axle 11 located below the cart frame 20 and extending in the horizontal direction, and an axle 11 extending in the vertical direction with respect to the cart frame 20. A motor 15 that is provided to be relatively displaceable and rotates the axle 11 around an axis O of the axle 11, a power transmission joint 16 that coaxially connects the axle 11 and a drive shaft 15c of the motor 15, and the motor

A motor bracket

19, 319 provided on the outer surface of the vehicle 15 and located radially outside of the axis O with respect to the axle 11 connects the bogie frame 20 and the

motor bracket

19, 319 in the vertical direction. an elastic member 30 that can be elastically deformed in the direction; latches 40, 240, and 340 that define the length of the elastic member 30 in the vertical direction; 319 from the inside in the radial direction, and is provided with a reverse centrifugal clutch 50 that can contract in diameter during rotation in response to centrifugal force generated by rotating together with the axle shaft 11, and can expand in diameter when rotation is stopped.

According to this aspect, when the bogie is stopped, the reverse centrifugal clutch 50 can support the

motor bracket

19, 319 from the inside in the radial direction. In this state, when the weight of the

truck

10, 210, 310 increases, a downward load is applied to the truck frame 20, causing the truck frame 20 to descend. In contrast, an upward reaction force from the ground is applied to the axle 11. At this time, the reverse centrifugal clutch 50 receives an upward reaction force from the axle 11 and pushes up the motor bracket 19,319. This suppresses eccentricity of the axle 11 with respect to the motor 15. The elastic member 30 expands and contracts in the vertical direction while eccentricity of the axle 11 with respect to the motor 15 is suppressed by the reverse centrifugal clutch 50. Therefore, displacement of the motor 15 in the vertical direction is well absorbed, and the height of the motor 15 is maintained.
Furthermore, when the bogie is running, the diameter of the reverse centrifugal clutch 50 is reduced and the motor bracket 19,319 is no longer pushed up by the reverse centrifugal clutch 50, but the height of the motor bracket 19,319 is maintained by the

latches

40, 240, 340. Ru.

(2) The

truck

10, 210, 310 of the second aspect is the

truck

10, 210, 310 of (1), and the

latch

40, 240, 340 is a first latch provided on the truck frame 20. The motor may include a member 41 and a

second latch member

42, 342 that is provided on the

motor bracket

19, 319, faces the first latch member 41, and is engageable with the first latch member 41. .

According to this aspect, the latch 40 can engage the first latch member 41 and the

second latch member

42, 342 when the truck is traveling.

(3) The truck 210 of the third aspect is the truck 210 of (2), in which the latch 240 uses the voltage of the motor 15 to connect the first latch member 41 and the second latch member 42. The lock release mechanism 243 may be provided to engage the first latch member 41 and the second latch member 42, and to release the engagement between the first latch member 41 and the second latch member 42.

According to this aspect, in order to engage the first latch member 41 and the second latch member 42 and disengage the first latch member 41 and the second latch member 42, special power is applied to the cart 210. There is no need to provide a source.

(4) The truck 310 of the fourth aspect is the truck 310 of (2), in which the latch 340 is connected to the first latch member 41 in conjunction with the diameter contraction and expansion of the reverse centrifugal clutch 50. It may include an interlocking mechanism 360 that engages with the second latch member 342 and disengages the first latch member 41 and the second latch member 342.

According to this aspect, the trolley 310 immediately engages the first latch member 41 and the second latch member 342 and engages the first latch member 41 and the second latch member in response to switching between the running state and the stopped state. 342 can be disengaged. Furthermore, in order to engage the first latch member 41 and the second latch member 342 and disengage the first latch member 41 and the second latch member 342, it is necessary to provide a special power source in the trolley 310. disappears.

1... Vehicle 2... Vehicle body 10... Truck 11... Axle 12... Holding mechanism 12a... Bearing box 12b... First bearing 13... Wheel 14... Shaft spring 15... Motor 15a... Stator 15b... Rotor 15c... Drive shaft 16... Power transmission joint 16a...Motor side joint member 16b...Axle side joint member 16c...Coupling 17...Cylinder part 18...Flange part 19...Motor bracket 19a...Inner peripheral surface 20...Dolly frame 30...Elastic member 40...Latch 41...First latch member 42...Second latch member 43...Latch spring 44...First latch base 45...Latch groove 46...Latch protrusion 50...Reverse centrifugal clutch 51...Clutch base 52...Clutch shoe 53...Rotating pin 54...Spring 55...Movable pin 56...Clutch connection part 57...Centrifugal force increasing mechanism 57a...Weight connection part 57b...Weight 57c...Weight guide 210...Dolly 240...Latch 243...Lock release mechanism 310...Dolly 319...Motor bracket 319a...Positioning frame 319b...Protruding plate part 319c...Inner peripheral surface 319d...Rectangular frame 319e...Intermediate bar 340...Latch 342...Second latch member 346...Second latch base 347...Latch protrusion 360...Interlocking mechanism 361...First pin 362...First bar 363... Second pin 364...Second bar 365...Third pin 366...Third bar 367...Fourth pin 370...Second bearing L...Rail O...Axis line P...Lock position

Claims

trolley frame,
an axle located below the truck frame and extending in the horizontal direction;
a motor that is provided to be movable relative to the truck frame in the vertical direction and rotates the axle about the axis of the axle;
a power transmission joint that coaxially connects the axle and the drive shaft of the motor;
a motor bracket provided on an outer surface of the motor and located radially outward of the axis with respect to the axle;
an elastic member that vertically connects the truck frame and the motor bracket and is elastically deformable in the vertical direction;
a latch that defines the length of the elastic member in the vertical direction;
The motor bracket is provided in an annular shape on the outer circumferential side of the axle, and supports the motor bracket from the inside in the radial direction, and is capable of contracting in diameter during rotation in response to centrifugal force generated by rotating together with the axle, and expands in diameter when rotation stops. possible reverse centrifugal clutch,
A trolley equipped with.
The latch is
a first latch member provided on the truck frame;
a second latch member provided on the motor bracket, facing the first latch member and engageable with the first latch member;
The trolley according to claim 1, comprising:
The latch is
A lock release mechanism that utilizes the voltage of the motor to engage the first latch member and the second latch member and release the engagement between the first latch member and the second latch member. The trolley according to item 2.
The latch is
Interlocking operation that engages the first latch member and the second latch member and disengages the first latch member and the second latch member in conjunction with the diameter contraction and expansion of the reverse centrifugal clutch. The trolley according to claim 2, comprising a mechanism.