Patent Application
20180319411
The present invention relates to a railcar steering bogie including a link mechanism.
As a railcar bogie, there exists a steering bogie capable of changing directions of wheelsets in a yawing direction. Known as one example of such steering bogie is a steering bogie of PTL 1. The steering bogie of PTL 1 includes a link mechanism (Z link), and the Z link includes a vertical link and two horizontal links. The vertical link is attached to a bogie frame so as to be turnable and is coupled to a carbody through a parallel link. Further, the two horizontal links are attached to the vertical link. The two horizontal links extend from the vertical link to one side and the other side in a forward/rearward direction and are attached to respective axle boxes provided at respective wheelsets.
When the steering bogie 1 configured as above travels through a curved line, the carbody and the bogie swing relative to each other, and the vertical link turns. With this, the two horizontal links move the axle boxes in such directions that the axle boxes get close to each other or separate from each other. Thus, a wheel base at a curved line outer rail side is increased, and a wheel base at a curved line inner rail side is decreased. As a result, the wheelsets can be steered, and this can change the directions of the wheelsets in the yawing direction.
PTL 1: Japanese Laid-Open Patent Application Publication No. 6-87446
According to the steering bogie of PTL 1, when the carbody and the bogie swing relative to each other, the link mechanism operates, and thus, the wheelsets are steered in proportion to an angle (bogie angle) at which the carbody and the bogie swing relative to each other. A ratio of the angle at which the carbody and the bogie swing relative to each other to the displacement of each wheelset is determined based on a ratio (i.e., a lever ratio) of a distance between a coupling point, to which the parallel link is coupled, of the vertical link and a turning center of the vertical link to a distance between a coupling point, to which the horizontal link is coupled, of the vertical link and the turning center of the vertical link.
To smoothly pass through a curved section, an attack angle between a wheel and a rail needs to be reduced, and the lever ratio is set to, for example, 1:6 to 1:7. As described above, the lever ratio is the ratio of the distance between the coupling point of the parallel link and the turning center to the distance between the coupling point of the horizontal link and the turning center. To increase the lever ratio, it is necessary to increase the distance between the coupling point of the parallel link and the turning center or decrease the distance between the coupling point of the horizontal link and the turning center. When increasing the distance between the coupling point of the parallel link and the turning center, it is necessary to increase the length of the vertical link. However, when the length of the vertical link is increased, and the distance between the coupling point of the parallel link and the turning center is increased, an underfloor height increases, so that this cannot be applied to a low-floor vehicle. Therefore, the distance between the coupling point of the horizontal link and the turning center may be decreased. However, the two horizontal links and a pin member by which the vertical link is attached to the bogie frame are arranged on the same plane, so that when the horizontal links are arranged close to the turning center, i.e., the pin member, the horizontal links finally contact the pin member. As above, according to a steering mechanism including the link mechanism, since the ratio of the angle at which the carbody and the bogie swing relative to each other to the displacement of the wheelset depends on the lever ratio, design is largely restricted.
An object of the present invention is to provide a steering bogie capable of increasing the degree of freedom of the design of the steering mechanism.
A railcar steering bogie of the present invention includes: a bogie frame supporting a carbody or a bolster such that the carbody or the bolster is swingable relative to the bogie frame about a vertical axis; two wheelsets each including an axle and a pair of wheels; axle box suspensions including respective axle beams coupling corresponding axle boxes to the bogie frame, the axle boxes accommodating respective bearings supporting the corresponding axles; and a steering mechanism configured to steer at least one of the two wheelsets in accordance with the swinging of the carbody or the bolster relative to the bogie frame, the steering mechanism including a steering lever configured to turn relative to the bogie frame about a fulcrum axis, a coupling link coupling the steering lever and the carbody or the bolster and configured to operate in conjunction with the swinging of the carbody or the bolster relative to the bogie frame, and at least one steering link coupling the steering lever and the corresponding axle beam and configured to steer the corresponding wheelset by displacing the corresponding axle box through the corresponding axle beam in conjunction with the turning of the steering lever, the steering lever including a turning center member configured to turn about the fulcrum axis, the turning center member being a shaft portion or a groove portion, the turning center member being arranged at a position offset with respect to the steering link in an axial direction.
According to the present invention, the turning center member is arranged at a position offset with respect to the steering link in the axial direction. Therefore, even when the steering link is designed so as to be located close to the fulcrum axis, the steering link does not contact the turning center member. On this account, restrictions on the arrangement position of the steering link in a direction perpendicular to the axial direction can be reduced, and thus, the degree of freedom of the design regarding the arrangement position of the turning center member and the arrangement position of the steering link can be increased.
According to the present invention, the degree of freedom of the design of the steering mechanism can be increased.
The above object, other objects, features, and advantages of the present invention will be made clear by the following detailed explanation of preferred embodiments with reference to the attached drawings.
Hereinafter, railcar steering bogies (hereinafter simply referred to as “steering bogies”) 1 and 1A of Embodiments 1 and 2 according to the present invention will be explained in reference to the drawings. It should be noted that directions stated in the following explanations are used for convenience of explanation, and directions and the like of components of the present invention are not limited. Further, each of steering bogies 1, 1A, and 1B of respective embodiments explained below is just one embodiment of the present invention. Therefore, the present invention is not limited to the embodiments, and additions, deletions, and modifications may be made within the scope of the present invention.
A railcar 2 shown in
Steering Bogie
As shown in
As shown in
The pair of axle boxes 13 are provided at both respective axial direction side portions of the axle 16 of the wheelset 12. The axle boxes 13 accommodate respective bearings 18, such as journal bearings, and the bearings 18 support both respective axial direction side portions of the axle 16 such that the axle 16 is rotatable. Further, the axle box suspensions 14 are provided at the respective axle boxes 13, and the axle boxes 13 are coupled to the bogie frame 11 through the respective axle box suspensions 14 (also see
Each of the axle box suspensions 14 is, for example, an axle beam type axle box suspension and includes an axle beam 23 and an axle spring 24 (also see
The steering bogie 1 configured as above is a bogie with a bolster and includes a bolster beam 25. The bolster beam 25 is provided at the cross beam 22 through a support shaft (not shown) and turns relative to the cross beam 22 about a vertical axis. Further, the bolster beam 25 supports the carbody 4 through the air spring 5 and is coupled to the carbody 4 by a bolster anchor 26. Therefore, the bolster beam 25 swings integrally with the carbody 4. The steering bogie 1 includes a pair of steering mechanisms 15 configured to steer the pair of wheelsets 12 (i.e., to cause the pair of wheelsets 12 to turn in a yawing direction) in accordance with the swing operation of the bolster beam 25.
Steering Mechanism
As shown in
As shown in
An accommodating portion 41b constituting a lower portion of the lever main body 41 has a circular shape in a side view as shown in
The housing 49 accommodates at least a part of the steering lever 32, specifically the accommodating portion 41b and the lid body 42. The housing 49 includes a housing seat 50, a rear box 51, a front box 52, and a box lid 53. The housing seat 50 is a plate-shaped member having a substantially rounded-corner circular shape extending in the longitudinal direction in a side view. A back surface of the housing seat 50 is fixed to an outer surface of the side sill 21 of the bogie frame 11. Further, the rear box 51 is fixed to a front surface of the housing seat 50 by a fastening member, such as a bolt. The rear box 51 is formed in a substantially circular shape in a side view, and a bearing hole 51a is formed about a center of the rear box 51. The shaft portion 45 of the accommodating portion 41b is fitted in the bearing hole 51a through the thrust bushing 47. The shaft portion 45 turns relative to the rear box 51. Further, the front box 52 is provided at the rear box 51.
The front box 52 is a box-shaped body having a substantially annular shape in a side view. The front box 52 is provided at the rear box 51 so as to cover the accommodating portion 41b and the lid body 42 and is fixed to the rear box 51 by a fastening member, such as a bolt. An opening 52a is formed at a part of a lower portion of one of both longitudinal direction-side surfaces of the front box 52, and an opening 52b is formed at an entire upper portion of the other longitudinal direction surface of the front box 52. The below-described second steering link 34 projects from the opening 52a located at a second side in the longitudinal direction. The curved portion 41a projects upward from the opening 52b located at the first side in the longitudinal direction, and the below-described first steering link 33 projects from the opening 52b toward the first side in the longitudinal direction. Further, an inner hole 52c is formed about a center axis of the front box 52 (i.e., the fulcrum axis L1) and has a hole diameter larger than each of an outer diameter of the shaft portion 46 of the lid body 42 and an outer diameter of the thrust bushing 48. The shaft portion 46 and the thrust bushing 48 project from the inner hole 52c. The box lid 53 is provided at the front box 52 so as to close the inner hole 52c and is fixed to the front box 52 by a fastening member, such as a bolt. As shown in
As above, in the steering lever 32, the pair of shaft portions 45 and 46 are turnably fitted in the housing 49 (specifically, the rear box 51 and the box lid 53, respectively), fixed to the side sill 21, through the respective thrust bushings 47 and 48. With this, the steering lever 32 can turn relative to the bogie frame 11 about the pair of shaft portions 45 and 46, i.e., about the fulcrum axis L1. As above, since the steering lever 32 is supported at two points that are the pair of shaft portions 45 and 46, backlash of the steering lever 32 can be made smaller than a case where the steering lever 32 is supported at one point. In the steering lever 32 having such function, a part of the lid body 42 and a part of the accommodating portion 41b constitute a pair of plate portions 54 and 55 sandwiching the accommodating space 43 and opposing each other. Two pin members 56 and 57 are provided at the pair of plate portions 54 and 55 so as to extend between the pair of plate portions 54 and 55.
Each of the first pin member 56 serving as a turning shaft of the first steering link 33 and the second pin member 57 serving as a turning shaft of the second steering link 34 is a substantially columnar shaft member extending in the car width direction (axial direction). Two fitting holes 54a and 54b are formed at the plate portion 54 so as to sandwich the fulcrum axis L1 and be spaced apart from each other, and two fitting holes 55a and 55b are formed at the plate portion 55 so as to sandwich the fulcrum axis L1 and be spaced apart from each other. The fitting holes 54a and 54b of the plate portion 54 oppose the fitting holes 55a and 55b of the other plate portion 55, respectively. Both end portions of the first pin member 56 are fitted in the respective opposing fitting holes 54a and 55a so as not to be turnable, and both end portions of the second pin member 57 are fitted in the respective opposing fitting holes 54b and 55b so as not to be turnable. Hereinafter, the shapes of the first pin member 56, the second pin member 57, and the like will be explained in further detail.
As shown in
Each of the shapes of the end portions of the pin members 56 and 57 and the fitting holes 54a, 54b, 55a, and 55b is not limited to the substantially rounded-corner rectangular shape in a side view and may be a substantially oval shape, an egg shape, or a substantially circular shape including a key or a keyway. To be specific, each of the shapes of the end portions of the pin members 56 and 57 is only required to be formed such that a major axis of each of the end portions of the pin members 56 and 57 is longer than a minor axis of each of the fitting holes 54a, 54b, 55a, and 55b. With this, the pin member 56 and 57 are configured so as not to be turnable relative to the pair of plate portions 54 and 55. Further, spherical bushings 56a and 57a are provided at respective car width direction intermediate portions of the pin members 56 and 57. Self-lubrication rubber members 58 and 59 formed by a rubber material having lubricity are externally attached to respective outer surfaces of the spherical bushings 56a and 57a, or the outer surfaces of the spherical bushings 56a and 57a are coated with the respective self-lubrication rubber members 58 and 59.
The two pin members 56 and 57 configured as above are arranged so as to sandwich the fulcrum axis L1 in a side view and be spaced apart from each other in the car upward/downward direction. The steering link 33 is provided at the spherical bushing 56a of the pin member 56 through the self-lubrication rubber member 58, and the steering link 34 is provided at the spherical bushing 57a of the pin member 57 through the self-lubrication rubber member 59. The steering links 33 and 34 are coupled to the steering lever 32 through the pin members 56 and 57.
The first steering link 33 is a member extending in the longitudinal direction. The spherical bushing 56a of the first pin member 56 to which the self-lubrication rubber member 58 is externally attached is inserted into one longitudinal direction end portion of the first steering link 33. Thus, the first steering link 33 is coupled to the steering lever 32. Since the spherical bushing 56a has a partially spherical shape, the first steering link 33 swivels about a center point of the spherical bushing 56a. As above, the first steering link 33 is arranged between the pair of plate portions 54 and 55 of the steering lever 32. Thus, the first steering link 33 can turn about an action axis L2 that is a center axis of the first pin member 56 and also pivot in the car width direction.
Similarly, the second steering link 34 is a member extending in the longitudinal direction. The spherical bushing 57a of the second pin member 57 to which the self-lubrication rubber member 59 is externally attached is inserted into one longitudinal direction end portion of the second steering link 34. Since the spherical bushing 57a has a partially spherical shape, the second steering link 34 swivels about a center point of the spherical bushing 57a. As above, the second steering link 34 is arranged between the pair of plate portions 54 and 55. Thus, the second steering link 34 can turn about an action axis L3 that is a center axis of the second pin member 57 and also pivot in the car width direction.
As above, one end portion of the first steering link 33 and one end portion of the second steering link 34 are coupled to the steering lever 32 through the respective pin members 56 and 57 and are arranged so as to be spaced apart from each other in the car upward/downward direction. Further, by arranging the two pin members 56 and 57 in the accommodating space 43, the end portion of the first steering link 33 and the end portion of the second steering link 34 are accommodated in the accommodating space 43. The accommodating space 43 communicates with an outside through openings 32a and 32b formed at both respective longitudinal direction-side surfaces of the accommodating portion 41b. The opening 32a is formed at an obliquely upper portion of a surface of the accommodating space 43 which surface is located at the first side in the longitudinal direction, and the first steering link 33 projects from the opening 32a. The projecting first steering link 33 further extends through the opening 52a toward the first side in the longitudinal direction. The opening 32b is formed at an obliquely lower portion of a surface of the accommodating space 43 which surface is located at the second side in the longitudinal direction, and the second steering link 34 projects from the opening 32b. The projecting second steering link 34 further extends through the opening 52a toward the second side in the longitudinal direction. As above, the steering link 33 extends toward the first side in the longitudinal direction, and the steering link 34 extends toward the second side in the longitudinal direction. As shown in
As shown in
Further, the second axle beam-side link receiving member 38 is formed in a substantially L shape in a plan view. A base end portion of the second axle beam-side link receiving member 38 is fixed to the axle beam main body portion 23a of the axle beam 23F located at the second side in the longitudinal direction, and one end portion of the second axle beam-side link receiving member 38 is coupled to the second steering link 34. Therefore, the second steering link 34 is arranged offset outside the axle beam 23F in the car width direction by the second axle beam-side link receiving member 38. The second steering link 34 arranged as above can turn in the car width direction relative to the second axle beam-side link receiving member 38 about a turning axis L5 extending in the car width direction (also see
The steering mechanisms 15 configured as above are arranged outside the respective side sills 21 of the bogie frame 11 in a posture shown in
Operations of Steering Mechanisms
When the bolster beam 25 and the bogie frame 11 swing relative to each other in a curved section, the steering mechanism 15 operates in conjunction with this swing operation. To be specific, as shown in
For example, as shown in
On the other hand, as shown in
The steering mechanisms 15 configured as above are mirror-symmetrically arranged outside the respective side sills 21 in the car width direction. When the bolster beam 25 and the bogie frame 11 swing relative to each other, the steering links 33 and 34 of one of the steering mechanisms 15 and the steering links 33 and 34 of the other steering mechanism 35 move in opposite directions. To be specific, when the steering bogie 1 travels through the curved section, and the bolster beam 25 and the bogie frame 11 swing relative to each other toward the first side in the swing direction, as shown in
Further, when the steering bogie 1 travels from the curved section to a straight section, the steering bogie 1 returns to an original posture such that the bolster beam 25 and the cross beam 22 become parallel to each other. In accordance with this, the pair of steering mechanisms 15 perform opposite operations to the above-described operations. To be specific, the steering mechanism 15 close to the outer rail 3a moves the first steering link 33 and the second steering link 34 such that the first steering link 33 and the second steering link 34 get close to each other to be returned to original positions. The steering mechanism 15 close to the inner rail 3b moves the first steering link 33 and the second steering link 34 such that the first steering link 33 and the second steering link 34 separate from each other to be returned to original positions. With this, the coupling point P1, the fulcrum P0, and the action points P2 and P3 are aligned on the same straight line in the car upward/downward direction, and the pair of front and rear wheelsets 12 are straightened. Therefore, a straight advancing property of the steering bogie 1 in the straight section of the rail 3 can be prevented from deteriorating.
In the steering bogie 1 configured as above, the steering links 33 and 34 are arranged between the pair of shaft portions 45 and 46 which serve as a turning center about which the steering lever 32 turns. To be specific, the pair of shaft portions 45 and 46 are arranged at positions offset with respect to the steering links 33 and 34 in the car width direction. With this, restrictions on the arrangement positions of the steering links 33 and 34 in the car upward/downward direction can be reduced. To be specific, the degree of freedom of the design regarding the arrangement positions of the steering links 33 and 34 can be increased. Therefore, the pair of shaft portions 45 and 46 and the steering links 33 and 34 can be arranged so as to overlap one another in a side view.
Further, since the pair of shaft portions 45 and 46 and the steering links 33 and 34 are arranged so as to overlap one another in a side view, a distance X2 between the fulcrum P0 and the action point P2 of the link 33 and a distance X3 between the fulcrum P0 and the action point P3 of the link 34 can be reduced. In the steering bogie 1, to steer the pair of wheelsets 12 at a turning angle corresponding to a ratio predetermined in accordance with a relative swinging angle, a lever ratio (a ratio of the distance X2 to a distance X1 between the fulcrum P0 and the coupling point P1 or a ratio of the distance X3 to the distance X1 (X2:X1 or X3:X1)) is set to a predetermined ratio, such as 1:6 to 1:7. Therefore, the distance X1 and an external dimension of the steering lever 32 are uniquely determined in accordance with the distances X2 and X3. Since the distances X2 and X3 can be made short in the steering mechanism 15, the external dimension of the steering lever 32 can be made small (especially, the height of the steering lever 32 can be suppressed). With this, the height of the steering mechanism 15 can be made low, and the height of the steering bogie 1 can be made low. Therefore, the steering bogie 1 as a low-floor bogie can be realized. Further, the steering mechanism 15 is formed by stacking plate-shaped members in a direction in which the fulcrum axis L1 extends, and a thickness of the steering mechanism 15 in the car width direction is smaller than the height of the steering mechanism 15. Therefore, by attaching the steering mechanism 15 to the bogie frame 11 such that the fulcrum axis L1 extends in the width direction, the amount of projection of the steering mechanism 15 projecting from the bogie frame 11 in the car width direction can be suppressed, and a length of the steering bogie 1 in the car width direction, i.e., the width of the steering bogie 1 can be suppressed.
As shown in
Further, in the steering bogie 1, the pin members 56 and 57 are fixed to the steering lever 32 so as not to be turnable relative to the steering lever 32. Therefore, it is possible to prevent a case where while the steering bogie 1 is traveling, the pin members 56 and 57 turn relative to the steering lever 32 to be worn away. With this, it is possible to prevent a case where backlash is generated between the steering lever 32 and each pin member 56, 57, and this deteriorates steering responsiveness or steering performance. Further, in the steering bogie 1, each of the end portions of the pin members 56 and 57 of the steering lever 32 and the fitting holes 54a, 54b, 55a, and 55b is formed in a substantially rounded-corner rectangular shape in a side view, and the end portions of the pin members 56 and 57 are fitted in the fitting holes 54a, 54b, 55a, and 55b. With this, the pin members 56 and 57 can be fixed to the steering lever 32 so as not to be turnable relative to the steering lever 32. Therefore, as compared to a case where the pin members 56 and 57 are fixed by a different member, such as a key, so as not to be relatively turnable, assembly workability can be facilitated, and the number of parts can be reduced.
The steering bogie 1A of Embodiment 2 is similar in configuration to the steering bogie 1 of Embodiment 1. Hereinafter, different components of the steering bogie 1A of Embodiment 2 from the steering bogie 1 of Embodiment 1 will be mainly explained. The same reference signs are used for the same components as the steering bogie 1 of Embodiment 1, and explanations thereof are omitted.
As shown in
In the steering bogie 1A configured as above, since the distances X2 (distance between P0 and P2) and X3 (distance between P0 and P3) of the steering mechanism 15A can be made short, the external dimension of the steering lever 32 can be made small (especially, the height of the steering lever 32 can be suppressed). With this, the width of the steering mechanism 15A can be made small, and the width of the steering bogie 1A can be suppressed. Further, the steering mechanism 15A is formed by stacking plate-shaped members in a direction in which the fulcrum axis L1 extends, and a height of the steering mechanism 15A is smaller than a width of the steering mechanism 15A. Therefore, by attaching the steering mechanism 15A to the bogie frame 11 such that the fulcrum axis L1 extends in the car upward/downward direction, the amount of projection of the steering mechanism 15A projecting from the bogie frame 11 in the car upward/downward direction can be suppressed. With this, the height of the steering bogie 1A can be made low.
Other than the above, the steering bogie 1A has the same operational advantages as the steering bogie 1 of Embodiment 1.
Each of the steering bogies 1 and 1A of Embodiments 1 and 2 is a bogie with a bolster, i.e., a bogie including the bolster beam 25. However, each of the steering bogies 1 and 1A does not necessarily have to include the bolster beam 25. To be specific, each of the steering bogies 1 and 1A may be a bolsterless bogie. In this case, the coupling link 31 of each of the steering mechanisms 15 and 15A is turnably coupled to a link receiving member projecting downward from a lower surface of the carbody 4. With this, the coupling link 31 moves toward the first or second side in the longitudinal direction in conjunction with the swing operation of the carbody 4 relative to the bogie frame 11, and thus, the steering mechanism 15, 15A operates. In each of the steering bogies 1 and 1A of Embodiments 1 and 2, both of the front and rear wheelsets 12 are steered by the steering mechanisms 15. However, both of the wheelsets 12 do not necessarily have to be steered. Each of the steering bogies 1 and 1A may be configured such that any one of the front and rear wheelsets 12 is steered by the steering mechanism 15 or 15A.
In each of the steering bogies 1 and 1A of Embodiments 1 and 2, the pair of shaft portions 45 and 46 as turning center members are formed at the steering lever 32 of the steering mechanism 15 or 15A. However, the turning center members do not necessarily have to be the pair of shaft portions 45 and 46. For example, as in a steering mechanism 15B shown in
In each of the steering bogies 1 and 1A of Embodiments 1 and 2, the shaft portions 45 and 46 are formed at both respective axial direction-side surfaces of the steering lever 32. However, the turning center member (the shaft portion 45 or the insertion groove 45B) may be formed on only one of the axial direction-side surfaces of the steering lever 32. Further, in each of the steering bogies 1 and 1A of Embodiments 1 and 2, the shaft portions 45 and 46 and the steering links 33 and 34 are arranged so as to overlap one another in a side view. However, at least one of the steering links 33 and 34 may be arranged so as to overlap the shaft portions 45 and 46. Further, even when the steering links 33 and 34 do not overlap the shaft portions 45 and 46, an effect of improving the degree of freedom of the design of the steering links 33 and 34 can be obtained by arranging the shaft portions 45 and 46 offset with respect to the steering links 33 and 34. It should be noted that the bogie 1 may include plate springs instead of the side sills 21 and the axle springs 24. To be specific, the bogie 1 may be configured such that: the spring receiving portions of the pair of front and rear axle boxes 13 support both longitudinal direction end portions of each of the plate springs from below; and longitudinal direction middle portions of the plate springs support the cross beam 22 from below.
From the foregoing explanation, many modifications and other embodiments of the present invention are obvious to one skilled in the art. Therefore, the foregoing explanation should be interpreted only as an example and is provided for the purpose of teaching the best mode for carrying out the present invention to one skilled in the art. The structures and/or functional details may be substantially modified within the scope of the present invention.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2015-212678 | Oct 2015 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2016/081045 | 10/20/2016 | WO | 00 |
