JP2010214985A - Freight car - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a freight car for restraining size increase of a drive device turning a turn table even in receiving load in a vertical direction of the turn table with a sliding bearing. <P>SOLUTION: The freight car is configured to receive the load in a vertical direction of the turn table 10 only by the first sliding bearing 33 disposed between a bottom face of a shaft housing part 32 disposed at a support base 22 and an opposed face of a lower face 31a of a rotating shaft 31 and supporting the rotating shaft 31 when the weight of a loaded object is a predetermined value or less, and to receive the load in the vertical direction of the turn table 10 by the first sliding bearing 33 and the second sliding bearing 34 by bringing the plurality of second sliding bearings 34 disposed on an upper face of the support base 22 and located on a virtual circle D around the rotating shaft 31 into contact with a contact part 35 disposed on a lower face of the turn table 10 and having a predetermined clearance set at a space to the second sliding bearing 34 with no loading object loaded when the weight of the loaded object exceeds the predetermined value. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a freight car, and more particularly, to a freight car that can suppress an increase in the size of a drive device that rotates the turn table even when a sliding bearing receives a load in the vertical direction of the turn table.

  Conventionally, a freight car that travels on a rail installed in a factory has been used to transport heavy objects on the site of the factory. Since such a freight car travels on the rail, the position relative to the crane cannot be freely changed. Therefore, when loading a load with a crane, the longitudinal direction of the load cannot follow the longitudinal direction of the freight car, and the load may protrude from the loading platform.

  In this case, since the freight car cannot be driven, the direction of the load is changed so that the load is along the loading table by a turntable installed on the loading table of the freight car, thereby enabling the freight car to travel. Patent Document 1 discloses a conventional freight car.

  This freight car has a turntable on which a load is loaded, a loading table on which the turntable is arranged, and a circumference around a rotation axis so that the turntable can rotate with respect to the loading table. The sliding bearing for supporting the turntable and the drive device for rotating the turntable supported by the sliding bearing so as to be rotatable with respect to the loading table.

JP-B 63-58458 (Figure 3)

  However, in the configuration in which the load in the vertical direction of the turntable is received by the sliding bearing as in the conventional freight car described above, the size in the height direction is reduced compared to the configuration in which the load in the vertical direction of the turntable is received by the rolling bearing. Although it can be achieved, the frictional resistance increases when the turntable rotates, and a large driving force is required to rotate the turntable.

  In addition, the frictional resistance of the sliding bearing increases with the turning radius from the rotating shaft. In the conventional freight car described above, the sliding bearing that receives the load in the vertical direction of the turntable keeps a predetermined distance from the rotating shaft. Therefore, the frictional resistance increases. For this reason, there is a problem in that the driving force required to rotate the turntable increases and the drive device becomes larger.

  The present invention has been made to solve the above-described problems, and suppresses an increase in the size of the drive device that rotates the turntable even when the slide bearing receives a load in the vertical direction of the turntable. It aims to provide a freight car that can be used.

  In order to achieve this object, the freight car according to claim 1 is capable of rotating a turntable on which a load is loaded, a loading table on which the turntable is disposed, and the turntable with respect to the loading table. A rotation support mechanism supported by the rotation support mechanism, and a drive device that rotates a turntable rotatably supported by the rotation support mechanism with respect to the loading table. The direction of the load is changed by rotating a table, and the rotation support mechanism is formed as a rotation shaft projecting from the lower surface of the turntable and a recess for receiving the rotation shaft. A shaft housing portion disposed on a table, a first sliding bearing disposed between opposed surfaces of a bottom surface of the shaft housing portion and a lower surface of the rotating shaft, and supporting the rotating shaft; and the turntable A plurality of second sliding bearings disposed on one of the lower surface of the loading table and the upper surface of the loading table and positioned on an imaginary circle centered on the rotating shaft, and abutting against the second sliding bearing, and the turntable And a contact portion that is disposed on the other of the lower surface of the loading table and the upper surface of the loading table and has a predetermined gap between the second sliding bearing and the weight of the load is not more than a predetermined value. In this case, when the gap is maintained and only the first slide bearing receives a load in the vertical direction of the turntable, and the weight of the load exceeds the predetermined value, at least the turntable is deformed and the By filling the gap, the first slide bearing and the second slide bearing are configured to receive a load in the vertical direction of the turntable.

  The freight car according to claim 2 is the freight car according to claim 1, wherein the shaft housing portion includes an inner circumferential surface formed with an inner diameter larger than an outer diameter of the rotating shaft, and the inner circumferential surface of the shaft housing portion. And a cushioning material is disposed in a gap between the outer peripheral surface of the rotating shaft.

  The freight car according to claim 3 is the freight car according to claim 2, wherein at least three or more of the second sliding bearings are arranged at equal intervals in the circumferential direction, and the second sliding bearings are equally spaced in the circumferential direction. And a portion that overlaps in the vertical direction of the loading table with respect to a support member interposed between the loading table and a base that supports the axle of a wheel that rolls on the rail. A second plain bearing is provided.

  According to the freight car of the first aspect, the turntable disposed on the loading table is rotatably supported by the driving table via the rotation support mechanism. Therefore, when the load is loaded on the loading table by the crane, the longitudinal direction of the load cannot be aligned with the longitudinal direction of the freight car. By rotating with respect to the loading table, the direction of the loading item is changed so that the loading item is along the loading table.

  Here, according to the freight car according to claim 1, the bottom surface of the rotating shaft that protrudes from the bottom surface of the turntable, and the bottom surface of the shaft housing portion that is formed as a concave portion that accommodates the rotating shaft and is disposed on the loading table. The first sliding bearing that supports the rotating shaft is disposed between the opposing surfaces of the rotating table, and the second sliding bearing is provided on one of the lower surface of the turntable and the upper surface of the loading table on a virtual circle centered on the rotating shaft. A contact portion that contacts the second slide bearing is disposed on the other of the lower surface of the turntable or the upper surface of the loading table, and a predetermined gap is set between the contact portion and the second slide bearing. Has been.

  The gap is maintained when the weight of the load is equal to or less than a predetermined value, and when the load of the load exceeds the predetermined value while receiving the load in the vertical direction of the turntable only with the first slide bearing, Since the first sliding bearing and the second sliding bearing that comes into contact with the abutting portion when the gap is filled are set to receive the load in the vertical direction of the turntable, the sliding bearing receives the load in the vertical direction of the turntable. Even if it is a case, there exists an effect that the enlargement of the drive device which rotates a turntable can be suppressed.

  That is, when the weight of the load is equal to or less than the predetermined value, a predetermined gap is maintained between the second slide bearing and the contact portion. Load in the direction. On the other hand, when the weight of the load exceeds a predetermined value, at least the turntable is deformed, so that the gap described above is filled and the second sliding bearing and the contact portion come into contact with each other. When the table rotates, the load in the vertical direction of the turntable is received by the first sliding bearing and the second sliding bearing.

  Therefore, the first sliding bearing located at the rotation center is set to have a shorter turning radius than the second sliding bearing located on the virtual circle centered on the rotation axis, so that the weight of the load is not more than a predetermined value. However, not only when the load is received only by the first slide bearing, but also when the load exceeds the predetermined value and the load is received by the first slide bearing and the second slide bearing, the second slide The overall frictional resistance generated between the turntable and the loading table can be reduced when the turntable rotates around the rotation axis, compared to the case where the bearing alone receives the full load in the vertical direction of the turntable. it can.

  Therefore, since the driving force required to rotate the turntable can be reduced, the increase in size of the driving device can be suppressed. As a result, there is an effect that the drive device can be accommodated between the turntable and the loading table.

  In addition, when the load is loaded on the turntable, if the load is received only at the rotation center (first sliding bearing), the pressure receiving area is small, so the rotating shaft and the rotating shaft are accommodated by the impact load during loading. The rigidity of the rotating shaft and the shaft housing portion must be improved so that the shaft housing portion is not damaged. Therefore, measures such as increasing the size of the rotating shaft and reinforcing the shaft housing portion are required.

  On the other hand, according to the freight car according to claim 1, even when an impact load is generated when the load is loaded on the turntable, at least the turntable is deformed by the load when the load is loaded. Thus, the gap set between the second sliding bearing and the abutting portion is filled, and the load is calculated between the rotation center (first sliding bearing) and the virtual circle (second sliding bearing) centered on the rotating shaft. You can receive both.

  In this case, since the loaded load is received not only on the rotation center (first sliding bearing) but also on a virtual circle (second sliding bearing) centered on the rotation axis, the loaded load is received only on the rotation center (first sliding bearing). The pressure receiving area can be increased as compared with the case where the pressure is received. Therefore, it is possible to prevent the rotating shaft and the shaft accommodating portion that accommodates the rotating shaft from being damaged by the impact of the loading load, and the durability of the rotating shaft and the loading platform can be improved.

  In addition, when receiving the load when the load is loaded on the first sliding bearing at the rotation center and the second sliding bearing on the virtual circle, first, the loading load is received at the rotation center (first sliding bearing), At least after the gap is filled by the deformation of the turntable, the loaded load is received on the virtual circle (second sliding bearing). Therefore, the load table can be absorbed by the deformation of the turntable, and the load applied to the loading table can be reduced as compared with the case where the load is received only at the rotation center (first sliding bearing). There is.

  According to the freight car according to claim 2, in addition to the effect produced by the freight car according to claim 1, the shaft housing portion includes an inner peripheral surface formed with an inner diameter larger than the outer diameter of the rotating shaft, and the inner peripheral surface thereof. Since the cushioning material is disposed in the gap between the rotating shaft and the outer peripheral surface of the rotating shaft, even if the rotating shaft is inclined with respect to the axial direction, the driving force required to rotate the turntable is suppressed. There is an effect that damage to the rotating shaft can be prevented.

  That is, when a load is loaded on one side of the turntable and the turntable is about to rotate while the rotation shaft is inclined with respect to the axial direction, the inner circumferential surface of the shaft housing portion and the rotation shaft If the cushioning material is not arranged in the gap between the outer peripheral surface, the rotating shaft is pressed against the inner peripheral surface of the shaft accommodating portion, and the rotational resistance is increased. Therefore, it is necessary to rotate the turntable. Driving force increases. Alternatively, the rotation shaft is damaged by the collision between the rotation shaft and the inner peripheral surface of the shaft housing portion due to the rotation.

  On the other hand, according to the freight car according to claim 2, since the cushioning material is disposed in the gap between the inner peripheral surface of the shaft housing portion and the outer peripheral surface of the rotation shaft, the rotation shaft is in the axial direction. Even when the turntable is about to rotate in a state inclined with respect to the rotation axis, the rotation shaft is pressed by the cushioning material. Therefore, as compared with the case where the rotating shaft is pressed against the outer peripheral surface of the rotating shaft, an increase in the rotational resistance generated between the rotating shaft and the cushioning material is suppressed, so that it is necessary to rotate the turntable. An increase in driving force can be suppressed. Therefore, it is possible to suppress the driving force necessary for rotating the turntable and prevent the rotating shaft from being damaged.

  According to the freight car according to claim 3, in addition to the effect achieved by the freight car according to claim 2, at least three or more of the second slide bearings are arranged at equal intervals in the circumferential direction, and the wheel rolling on the rail is provided. Since the second sliding bearing is disposed at a position overlapping the support member interposed between the base supporting the axle and the loading table in the vertical direction of the loading table, the weight of the load is a predetermined value. Even when an excessive load is applied to the second sliding bearing beyond the range, there is an effect that the rotation shaft can be prevented from being inclined with respect to the axial direction.

  That is, since at least three or more of the second sliding bearings are arranged at equal intervals in the circumferential direction, the weight of the load exceeds a predetermined value, the gap is closed, and the turntable is placed on the upper surface of the loading table. In the case of contact, for example, even if the weight of the load is loaded at an uneven position of the turntable, it is possible to close a gap in at least one or more second sliding bearings among the plurality of second sliding bearings. The turntable can be kept horizontal, and the rotation axis can be prevented from being inclined with respect to the axial direction.

  In addition, a second sliding bearing is disposed at a position overlapping the support member interposed between the base supporting the axle of the wheel rolling on the rail and the loading base in the vertical direction of the loading base. Therefore, the rigidity of the loading table can be ensured. Therefore, even when an excessive load is applied to the turntable, the platform can be prevented from being deformed. Therefore, when the load is received even by the second slide bearing, the rotating shaft is inclined with respect to the axial direction. Can be prevented.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings. With reference to FIG.1 and FIG.2, the freight car 1 in one embodiment of this invention is demonstrated. FIG. 1 is a schematic side view of a freight car 1, and a part of a portion where a turntable 10 to be described later is disposed is shown in cross section. FIG. 2 is a partially enlarged plan view of the freight car 1 in which a portion where the turntable 10 of the freight car 1 is disposed as viewed from the II direction in FIG. 1 is enlarged.

As shown in Figure 1, wagons 1 is a vehicle for carrying the cargo is heavy in the site of the plant, and is capable row run on rails R installed in the factory.

  The freight car 1 includes a plurality of wheels 3 that roll on the rail R, a plurality of axles 4 that support the wheels 3, and a drive device 5 for traveling (see FIG. 3), and is fitted to the axle 4. Further, a chain 7 is wound around a sprocket 4a (see FIG. 4) on the axle 4 side and a drive sprocket 6a (see FIG. 4) fitted to the drive shaft 6 (see FIG. 4) of the driving device 5 for traveling. Then, the driving force of the driving device for traveling 5 is transmitted to the axle 4 (wheel 3), so that the vehicle travels on the rail R.

  Further, the freight car 1 includes a turntable 10 on which a load is loaded, a loading table 20 on which the turntable 10 is disposed, and a rotation support mechanism that rotatably supports the turntable 10 with respect to the loading table 20. 30 and a motor device 40 (see FIG. 2) for rotating the turntable 10 rotatably supported by the rotation support mechanism 30 with respect to the loading table 20.

  Therefore, since the turntable 10 is rotatably supported by the motor device 40 via the rotation support mechanism 30 with respect to the loading table 20, the load table is mounted on the loading table 20 by a crane (not shown). In the case where the longitudinal direction of the load cannot follow the longitudinal direction of the freight car 1 (the left-right direction in FIG. 1) and the load protrudes from the loading table 20 to the outside (the front side or the back side in FIG. 1). Even if the turntable 10 is rotated with respect to the loading table 20, the direction of the loading object is changed so that the loading object is along the loading table 20.

  Therefore, since the freight car 1 can travel on the rail R without the load interfering with facilities in the factory, the freight car 1 can smoothly carry the load.

  As shown in FIGS. 1 and 2, the turntable 10 includes an upper table 11 and a lower table 12 set to have a smaller diameter than the upper table 11, and a chain 13 described later on the lower surface of the lower table 12. And the adjusting member 14 are fixed. In the present embodiment, the upper table 11 and the lower table 12 are configured separately, and are integrated by being integrally coupled via a bolt 15, but the upper table 11 and the lower table are integrated. The table 12 may be integrally formed.

  As shown in FIG. 1, the loading table 20 is a table that extends in the front-rear direction (left-right direction in FIG. 1) of the freight car 1 and on which a load is mounted, and includes a front side (right side in FIG. 1) and a freight car 1. It is supported on the axle 4 via bases 8 disposed on the rear side (left side in FIG. 1).

  As shown in FIGS. 1 and 2, the loading table 20 extends in the front-rear direction (the left-right direction in FIG. 1) of the freight car 1 and a pair of vertical beam members 21 that constitute frames on both sides of the loading table 20. The support base 22 is a base that is laid between the pair of vertical beam members 21 and connected to the pair of vertical beam members 21. The vertical beam member 21 and the support base 22 are connected to each other between the upper surface and the lower surface via a plate 23 (see FIG. 3). Therefore, since the vertical beam member 21 and the support base 22 are reinforced by the plate 23, the rigidity of the stacking base 20 is ensured.

  As shown in FIG. 1, the loading table 20 has an accommodation recess 24 that is recessed downward in the center portion of the support table 22. Since the turntable 10 is housed in the housing recess 24, the amount of protrusion from the support base 22 (vertical beam member 21) can be kept low.

  As shown in FIG. 1, a support member 9 is interposed between the loading table 20 and the base 8. The support member 9 is located between the adjacent axles 4 and, as shown in FIG. 2, passes through the center O1 of the rotating shaft 31 and extends in the longitudinal direction of the loading table 20 along the center line E of the loading table 20 (see FIG. 5). Are arranged on both sides of the imaginary circle, and are arranged on a virtual circle D (see FIG. 5) described later. The loading table 20 is supported on the base 8 by the support member 9.

  Since the support member 9 is disposed between the pair of wheels 3, the load loaded on the turntable 10 can be evenly held by the axles 4 of the pair of wheels 3. Therefore, the load in the vertical direction of the load loaded on the turntable 10 acts equally on the pair of axles 4. Therefore, when a vertical load is applied to one of the pair of axles 4, the wheel 3 of one axle 4 is less likely to roll on the rail R than the wheel 3 of the other axle 4. Therefore, the freight car 1 can be run smoothly.

  As shown in FIG. 2, the motor device 40 is accommodated in the motor accommodating portion 26. The motor housing portion 26 is a recess (see FIG. 3) that is deeper than the shaft housing portion 32, which will be described later, and is positioned behind the shaft support portion 25 (to the left in FIG. 2). And it is arrange | positioned in the location where the accommodation recessed part 24 and the support stand 22 overlap in the up-down direction.

  Therefore, since the motor device 40 can be prevented from being exposed to the outside, it is possible to prevent the motor device 40 from being defective due to dust in the factory.

  The motor device 40 includes a drive unit 41 that is fixed to the support base 22 and generates a driving force, a sprocket 42 that meshes with a later-described chain 13 that is fixed to the lower surface of the lower table 12, and a drive unit 41. It is comprised with the transmission part 43 which transmits a driving force to the sprocket 42. FIG.

  Therefore, the sprocket 42 is rotated by the drive unit 41 in a state where the groove 13 of the sprocket 42 is engaged with a pin 13 a of the chain 13 described later, whereby the turntable 10 rotates in the rotation direction of the sprocket 42. Therefore, the direction of the load can be changed. In one embodiment of the present invention, the rotation angle of the turntable is set to a total of 90 degrees, 45 degrees in the forward direction and 45 degrees in the reverse direction.

  Next, the rotation support mechanism 30 (see FIG. 1) will be described with reference to FIGS. 3 is a cross-sectional view of the freight car 1 along the line III-III in FIG. 2, and FIG. 4 is a cross-sectional view of the freight car 1 along the line IV-IV in FIG. In addition, the part shown by A in FIG. 3, the part shown by B in FIG. 4, and the part shown by C in FIG.

  As shown in FIGS. 3 and 4, the rotation support mechanism 30 (see FIG. 1) includes a rotation shaft 31 protruding from the lower surface of the turntable 10, and a support base 22 formed as a recess that accommodates the rotation shaft 31. A first sliding bearing 33 that is disposed between the bottom surface of the shaft housing portion 32 and the opposite surface of the lower surface 31a of the rotating shaft 31 and supports the rotating shaft 31, and the upper surface of the support base 22. And a plurality of second slide bearings 34 positioned on a virtual circle D centered on the rotation shaft 31, abutting against the second slide bearing 34, and disposed on the lower surface of the turntable 10. A contact portion 35 in which a predetermined gap L1 (see FIG. 7A) is set between the second slide bearing 34 and the second slide bearing 34.

  Therefore, when the weight of the load is equal to or less than the predetermined value, the load in the vertical direction of the turntable 10 is received only by the first slide bearing 33, and when the weight of the load exceeds the predetermined value, the first slide bearing 33 is received. And the second sliding bearing 34 are configured to receive a load in the vertical direction of the turntable 10.

  Here, with reference to FIG. 7, the turntable 10 which deform | transforms with the weight of a load is demonstrated. FIG. 7 is a partially enlarged cross-sectional view of the freight car 1 at a portion indicated by VII in FIG. 3, and FIG. 7 (a) shows a case where the weight of the load is not more than a predetermined value. ) Is illustrated when the weight of the load exceeds a predetermined value.

  As shown in FIG. 7A, when the weight of the load is equal to or less than a predetermined value, the contact portion 35 fixed to the lower surface of the lower table 12 of the turntable 10 via the adjustment member 14, and the second Since the predetermined gap L1 is set between the sliding bearing 34 and the sliding bearing 34, the contact portion 35 and the second sliding bearing 34 do not contact. On the other hand, when the weight of the load exceeds a predetermined value, the upper table 11 and the lower table 12 are bent and deformed to the support base 22 side (the lower side in FIG. 7A).

  As shown in FIG. 7B, when the movement amount of the outer peripheral portion (the right side portion in FIG. 7) to which the second sliding bearing 34 of the lower table 12 is attached reaches the distance L1, the upper table 11 and the lower table The side table 12 is inclined downward (downward in FIG. 7 (b)), the gap L1 is filled and disappears, and the contact portion 35 and the second plain bearing 34 come into contact.

  Therefore, the load in the vertical direction of the turntable 10 can be received not only by the first sliding bearing 33 but also by the second sliding bearing 34 on the outer peripheral side. Accordingly, the turntable 10 can be maintained in a horizontal state, and the rotation shaft 31 of the turntable 10 can be prevented from being inclined with respect to the axial direction (the vertical direction in FIG. 7). In FIG. 7B, the upper table 11 and the lower table 12 that are inclined downward (downward in FIG. 7B) are partially enlarged, so that the upper table 11 and the lower table 12 are enlarged. Is shown in a horizontal state in which it is bent and deformed to the support base 22 side (the left portion in FIG. 7B).

  In the freight car 1 according to the embodiment, the case where the turntable 10 is deformed has been described. However, the present invention is not necessarily limited to this, and the turntable 10 and the housing recess 24 portion of the support base 22 are both deformed. It may be.

  Returning to FIG. 3 and FIG. Therefore, as shown in FIGS. 3 and 4, when the weight of the load is equal to or less than a predetermined value, the gap L1 (see FIG. 7A) is maintained between the second sliding bearing 34 and the contact portion 35. Therefore, the load in the vertical direction of the turntable 10 can be received only by the first slide bearing 33 when the turntable 10 rotates. On the other hand, when the weight of the load exceeds a predetermined value, the turntable 10 is deformed to fill the gap L1 described above, and the second sliding bearing 34 and the contact portion 35 come into contact with each other. Therefore, when the turntable 10 rotates, the first slide bearing 33 and the second slide bearing 34 can receive a load in the vertical direction of the turntable 10.

  The turning radius of the first sliding bearing 33 located at the center of rotation (the separation distance between the center of the rotating shaft 31 and the outer end of the first sliding bearing 33) is a virtual circle D centered on the rotating shaft 31 (see FIG. 5). Since the turning radius of the second sliding bearing 34 positioned above (the distance between the center of the rotary shaft 31 and the outer end of the second sliding bearing 34) is set shorter, the weight of the load is not more than a predetermined value. Even when the load is received only by the first slide bearing 33, even when the weight of the load exceeds a predetermined value and the load is received by the first slide bearing 33 and the second slide bearing 34, Compared with the case where only the second slide bearing 34 receives the full load in the vertical direction of the turntable 10, the whole generated between the turntable 10 and the support base 22 when the turntable 10 rotates around the rotation shaft 31. As the friction resistance can be reduced

  Therefore, since the driving force of the motor device 40 necessary for rotating the turntable 10 can be reduced, an increase in the size of the motor device 40 can be suppressed. As a result, the motor device 40 can be accommodated between the turntable 10 and the support base 22 (accommodating recess 24).

  In addition, when the load is loaded on the turntable 10, if the load is received only at the rotation center (first sliding bearing 33), the pressure receiving area is small, so the rotary shaft 31 and the rotary shaft are affected by the impact load during loading. The rigidity of the rotary shaft 31 and the shaft housing portion 32 must be improved so that the shaft housing portion 32 that houses 31 is not damaged. Accordingly, measures such as increasing the size of the rotating shaft 31 and reinforcing the shaft housing portion 32 are required.

  On the other hand, according to the freight car 1 according to the embodiment, even when an impact load is generated when a load is loaded on the turntable 10, at least the turntable 10 is caused by the load when the load is loaded. By deforming, the gap L1 (see FIG. 7A) set between the second slide bearing 34 and the contact portion 35 is filled, and the second slide bearing 34 contacts the contact portion 35. The loaded load can be received both at the rotation center (first sliding bearing 33) and on the virtual circle D (second sliding bearing 34) centered on the rotation shaft 31.

  In this case, since the loaded load is received not only on the rotation center (first sliding bearing 33) but also on the virtual circle D (second sliding bearing 34) centered on the rotation shaft 31, the loaded load is received on the rotation center (first sliding bearing 33). The pressure receiving area can be increased as compared with the case of receiving only by the sliding bearing 33). Therefore, it is possible to prevent the rotating shaft 31 and the shaft accommodating portion 32 that accommodates the rotating shaft 31 from being damaged by the impact of the loading load, and the durability of the rotating shaft 31 and the support base 22 can be improved.

  In addition, when the loaded load at the time of loading the load is received by the first sliding bearing 33 at the rotation center and the second sliding bearing 34 on the virtual circle D, first, the loaded load is received at the rotation center (first sliding bearing 33). ) And at least the turntable 10 is deformed to fill the gap L1 (see FIG. 7A), and then the loaded load is received on the virtual circle D (second sliding bearing 34). Therefore, the deformation of the turntable 10 can absorb the loaded load and reduce the load applied to the support base 22 as compared with the case where the loaded load is received only at the rotation center (first sliding bearing 33). it can.

  As shown in FIGS. 3 and 4, the rotation shaft 31 is a shaft serving as the rotation center of the turntable 10 and has a predetermined length L2 in the axial direction (vertical direction in FIGS. 3 and 4). Yes. A rod-shaped retaining portion 31c extends downward (downward in FIGS. 3 and 4) from the center of the lower surface 31a of the rotating shaft 31, and the retaining portion 31c is a hole that penetrates a shaft support portion 25 described later. Inserted. The plate 31d having a diameter larger than the hole penetrating the shaft support portion 25 is fixed to the lower end (the lower end portion in FIGS. 3 and 4) of the retaining portion 31c, thereby preventing the rotating shaft 31 from coming off.

  As shown in FIGS. 3 and 4, the shaft support portion 25, which is a portion reinforced from the other portions of the support base 22, overlaps with the rotation shaft 31 in the axial direction (vertical direction in FIGS. 3 and 4). Is formed. The shaft support portion 25 is disposed substantially at the center of the housing recess 24 of the support base 22 described above, and is formed in a rectangular shape when viewed from above the housing recess 24 (upper side in FIGS. 3 and 4). . Further, the shaft support portion 25 protrudes above the upper surface of the accommodation recess 24 (upward in FIG. 4).

  Therefore, the shaft housing portion 32 is necessary to support the rotating shaft 31 housed in the housing recess 24 without reducing the thickness L3 of the shaft support portion 25 in the vertical direction (the vertical direction in FIGS. 3 and 4). Length is secured. Therefore, since the rigidity of the shaft housing portion 32 can be ensured by the thickness L3 of the shaft support portion 25, the inner side of the shaft housing portion 32 is caused by the load in the lateral direction (the left and right directions in FIGS. 3 and 4) of the turntable 10. Even when the peripheral surface 32b and the outer peripheral surface 31b of the rotating shaft 31 collide, the shaft housing portion 32 can be prevented from being damaged.

  The shaft accommodating portion 32 is a recess recessed in a columnar shape on the shaft support portion 25, and the recess is provided upright from the circular bottom surface 32 a and the outer edge of the bottom surface 32 a, and the outer diameter of the rotating shaft 31. The inner peripheral surface 32b is formed with a larger inner diameter. A first sliding bearing 33 described later is accommodated in the shaft accommodating portion 32.

  A cushioning material 37 is disposed in a gap between the inner peripheral surface 32 b of the shaft housing portion 32 and the outer peripheral surface 31 b of the rotating shaft 31. As shown in FIGS. 3 and 4, the cushioning material 37 is a member for absorbing the impact of the collision when the outer peripheral surface 31 b of the rotating shaft 31 collides with the inner peripheral surface 32 b of the shaft accommodating portion 32. It is formed in a cylindrical shape extending in the axial direction of the rotating shaft 31.

  If the cushioning material 37 is not disposed in the gap between the inner peripheral surface 32b of the shaft accommodating portion 32 and the outer peripheral surface 31b of the rotating shaft 31, the load is biased to one side of the turntable 10. When the turntable 10 rotates with the rotation shaft 31 inclined with respect to the axial direction, the rotation shaft 31 is pressed against the inner peripheral surface of the shaft housing portion 32, and the rotation resistance is increased. The driving force required to rotate the table 10 increases. Alternatively, the rotating shaft 31 is damaged by the collision between the outer peripheral surface 31 b of the rotating shaft 31 and the inner peripheral surface 32 b of the shaft housing portion 32 due to the rotation.

  On the other hand, since the cushioning material 37 is disposed in the gap between the inner peripheral surface 32b of the shaft accommodating portion 32 and the outer peripheral surface 31b of the rotary shaft 31, the rotary shaft 31 is inclined with respect to the axial direction. In this state, even if the turntable 10 is about to rotate, the rotating shaft 31 is pressed by the buffer material 37. Therefore, compared with the case where the rotary shaft 31 is pressed against the outer peripheral surface of the rotary shaft 31, an increase in rotational resistance generated between the rotary shaft 31 and the buffer material 37 is suppressed, so that the turntable 10 is rotated. It is possible to suppress an increase in driving force necessary to achieve this. Therefore, it is possible to prevent the driving force necessary for the rotation of the turntable 10 and the breakage of the rotating shaft 31.

  Here, the process of fixing the motor device 40 and the turntable 10 on the loading table 20 will be described. As shown in FIG. 4, the motor device 40 is installed in the motor housing portion 26 and is fixed to the lower surface of the support base 22. In this case, the sprocket 42 of the motor device 40 protrudes from the upper surface of the support base 22.

  Next, the chain 13 that meshes with the sprocket 42 is disposed on the upper surface of the support base 22. The chain 13 is a member for transmitting the driving force of the motor device 40 to the turntable 10, and a plurality of columnar pins 13 a meshed with the sprocket 42 are arranged in parallel at predetermined intervals.

  The chain 13 and a plurality of adjustment members 14 (four in the embodiment of the present invention) set to the height of the chain 13 are assembled on the upper surface of the support base 22 so as to form one ring. . The contact portion 35 is fixed to the lower surface of the chain 13 and the adjustment member 14 assembled in the ring shape.

  The chain 13 and the adjustment member 14 assembled in the ring shape are installed on the above-described virtual circle D (see FIG. 5), whereby the abutting portion 35 abuts on the second sliding bearing 34 and The sprocket 42 and the pin 13a of the chain 13 are engaged with each other.

  Next, the retaining portion 31 c is inserted into the hole penetrating the shaft support portion 25, and the rotating shaft 31 is accommodated in the shaft accommodating portion 32. By fixing the plate material 31d to the lower end (the lower end portion in FIGS. 3 and 4) of the retaining portion 31c, the turntable 10 is secured to the support base 22 while being retained from the support base 22.

  And the chain 13 and the adjustment member 14 which were formed in ring shape with fastening members, such as volt | bolt 15 (refer FIG. 2), are fixed to the lower surface of the turntable 10 (lower table 12). In this case, since the chain 13 and the adjusting member 14 installed on the virtual circle D are pulled up and fixed to the turntable 10 side (FIGS. 3 and 4), the second slip disposed on the virtual circle D is secured. A gap L <b> 1 (see FIG. 7A) is generated between the bearing 34 and the contact portion 35 fixed to the lower surface of the chain 13 and the adjustment member 14.

  A shim (not shown) is disposed and adjusted between the second slide bearing 34 and the support base 22 so that the length of the gap L1 (see FIG. 7A) becomes a predetermined value. Thereby, the turntable 10 is installed on the loading table 20 in a state where the predetermined gap L1 is held between the second sliding bearing 34 and the contact portion 35.

  Therefore, without moving the turntable 10, the chain 13 and the adjusting member 14 can be moved to the sprocket 42 side so that the chain 13 can be engaged with the sprocket 42. Compared to the case where the sprocket 42 and the chain 13 are engaged with each other, the efficiency of the work of engaging the sprocket 42 and the chain 13 can be improved.

  Next, the first sliding bearing 33 and the second sliding bearing 34 will be described with reference to FIGS. 5 and 6. FIG. 5 is a partially enlarged plan view of the freight car 1 enlarged about the portion of the turntable 10 of the freight car 1 in the VV line of FIG. 4, and FIG. 6 is a turn of the freight car 1 in the VI-VI line of FIG. It is a partial expanded plan view of the freight car 1 expanded about the table 10 part.

  As shown in FIG. 5, the first sliding bearing 33 is a member that supports the rotating shaft 31 that rotates with respect to the shaft housing portion 32, and is disposed in the shaft housing portion 32. Therefore, since the rotating shaft 31 is pivotally supported by the shaft housing portion 32 via the first sliding bearing 33, the rotating shaft 31 can be rotated accurately and smoothly, and the rotating shaft 31 and the shaft housing portion 32 are directly connected to each other. Friction generated by contact can be reduced. Thereby, the energy loss and heat_generation | fever of the rotating shaft 31 can be reduced, and the burning of the rotating shaft 31 can be prevented.

  Moreover, since the 1st sliding bearing 33 is arrange | positioned in the rotation center, the increase in rotational resistance by the increase in a turning radius can be suppressed. Therefore, in the case where the load in the vertical direction of the turntable 10 is received by the first slide bearing 33 as compared with the case where the load in the vertical direction of the turntable 10 is received only by the second slide bearing 34 disposed in the virtual circle D. The rotational resistance can be reduced, and the motor device 40 can be reduced in size.

  As shown in FIG. 5, the second sliding bearing 34 is a rectangular bearing member located on a virtual circle D centered on the rotation shaft 31, and rotates the turntable 10 that rotates with respect to the support base 22. I support it as possible. A shim (not shown) is interposed between the second sliding bearing 34 and the support base 22, and a predetermined gap L1 (see FIG. 7A) is adjusted by the shim.

  Four second sliding bearings 34 are equally arranged in the circumferential direction on the virtual circle D, and among the four second sliding bearings 34, the front side (right side in FIG. 5) and the rear side (left side in FIG. 5). The second sliding bearings 34 disposed in the upper portion of the support base 22 are disposed at positions that overlap the support member 9 in the vertical direction of the support base 22 (from the front to the rear in FIG. 5).

  Therefore, the weight of the load exceeds a predetermined value, the gap L1 (see FIG. 7A) is closed, and the upper surface of the support base 22 and the lower surface of the lower table 12 are interposed via the second slide bearing 34. In the case of contact, for example, even if the weight of the load is applied to an uneven position of the turntable 10, the clearance L <b> 1 (at least one or more second sliding bearings 34 among the four second sliding bearings 34 ( Since the turntable 10 can be kept in a horizontal state, the rotation shaft 31 can be prevented from being inclined with respect to the axial center direction (from the front side to the back side in FIG. 5).

  In addition, the second slip occurs at a position overlapping the support base 22 in the vertical direction with respect to the support member 9 interposed between the base 8 (see FIG. 4) supporting the axle 4 of the wheel 3 and the support base 22. Since the bearing 34 is disposed, the rigidity of the support base 22 can be ensured. Therefore, even when an excessive load is applied to the turntable 10, it is possible to prevent the support base 22 from being deformed.

  On the other hand, the second sliding bearings 34 disposed on the left side (upper side in FIG. 5) and the right side (lower side in FIG. 5) of the freight car 1 are disposed in the vicinity of the connecting portion with the longitudinal beam member 21 that is a rigid member. Therefore, the rigidity of the support base 22 can be ensured. Therefore, even when an excessive load is applied to the turntable 10, it is possible to prevent the support base 22 from being deformed.

  Therefore, when the second sliding bearing 34 comes into contact with a contact portion 35 to be described later and the second sliding bearing 34 receives the load in the vertical direction acting on the turntable 10 in addition to the first sliding bearing 33, the rotating shaft 31 can be prevented from inclining with respect to the axial direction (from the front side to the back side in FIG. 5). Therefore, the turntable 10 can be smoothly rotated, and the efficiency of the work of reloading the load can be improved.

  Further, the second sliding bearings 34 disposed on the front side (right side in FIG. 5) and the rear side (left side in FIG. 5) of the freight car 1 are disposed on the center line E of the loading platform 20, and on both sides thereof. Support members 9 are respectively disposed. Therefore, when the second sliding bearing 34 and a contact portion 35 to be described later come into contact with each other and a load in the vertical direction of the turntable 10 acts on the support base 22, the load is supported on both sides of the second sliding bearing 34. The members 9 can be supported evenly. Therefore, since this load can be made to act equally on the axle 4 (see FIG. 4), the cargo can be transported smoothly by the freight car 1.

  As shown in FIG. 6, the abutting portion 35 is an iron plate formed in a ring shape, and a fastening member such as a bolt on the lower surface of the chain 13 and the adjusting member 14 fixed to the lower surface of the lower table 12. It is fixed with.

  For example, when the load in the vertical direction of the turntable 10 is received only by the second sliding bearing 34 disposed in the virtual circle D, the load of the turntable 10 is increased by the first sliding bearing 33 and the second sliding bearing 34. Compared to the case of receiving, the turning radius increases. Therefore, since the frictional resistance of the second sliding bearing 34 increases, the second sliding bearing 34 must be enlarged and the number thereof must be increased in order to improve the durability of the second sliding bearing 34. Therefore, rotational resistance increases and the motor apparatus 40 becomes large.

  Furthermore, in order to cope with an increase in the size of the second slide bearing 34, the width of the ring-shaped contact portion 35 must be increased, and the weight of the contact portion 35, which is an iron plate material, is increased. The weight of the turntable 10 to which the part 35 is fixed also increases. Therefore, the motor device 40 is increased in size. Further, when the weight of the turntable 10 increases, the weight of the load that can be loaded on the turntable 10 must be reduced by the increase.

  On the other hand, in the embodiment of the present invention, the load of the turntable 10 is received by the first sliding bearing 33 and the second sliding bearing 34. There is no need to increase the weight of the portion 35. Therefore, the enlargement of the motor device 40 can be prevented.

  The present invention has been described above based on the above embodiment, but the present invention is not limited to the above embodiment, and various improvements and modifications can be made without departing from the spirit of the present invention. Something can be easily guessed.

  For example, in the above embodiment, the case where four second sliding bearings 34 are installed in the freight car 1 is described. However, the present invention is not limited to this, and three second sliding bearings 34 are installed. Also good. Thereby, the cost reduction by reduction of a number of parts can be aimed at. However, three or more are preferably installed in order to keep the turntable 10 horizontal.

  In the above embodiment, the case where the second sliding bearing 34 is fixed to the support base 22 has been described. However, the present invention is not limited to this, and the second sliding bearing 34 is fixed to the turntable 10. Also good. In this case, the abutting portion 35 can be omitted, and an attaching operation for attaching the abutting portion 35 to the lower table can be eliminated, so that the assembly work of the turntable 10 can be made more efficient.

  Further, the contact portion 35 fixed to the turntable 10 may be configured by the second sliding bearing 34. In this case, the frictional resistance between the turntable 10 and the support base 22 can be further reduced, and the motor device 40 can be downsized.

It is a side view of a freight car in one embodiment of the present invention. FIG. 2 is a partially enlarged plan view of a freight car in which a portion where a turntable of the freight car is viewed from the II direction in FIG. 1 is enlarged. It is sectional drawing of the freight car in the III-III line | wire of FIG. It is sectional drawing of the freight car in the IV-IV line of FIG. FIG. 5 is a partially enlarged plan view of a freight car enlarged with respect to a turntable portion of the freight car on line VV in FIG. 4. FIG. 5 is a partially enlarged plan view of a freight car enlarged with respect to a turntable portion of the freight car on line VI-VI in FIG. 4. FIG. 4 is a partially enlarged cross-sectional view of a freight car at a portion indicated by VII in FIG. 3, in which (a) illustrates the case where the weight of the load is equal to or less than a predetermined value, and (b) illustrates the weight of the load. The case where the value is exceeded is illustrated.

DESCRIPTION OF SYMBOLS 1 Freight car 3 Wheel 4 Axle 8 Base 9 Support member 10 Turntable 11 Upper table 12 Lower table 20 Loading base 30 Rotation support mechanism 31 Rotating shaft 31b Outer peripheral surface 32 Axis accommodating part 32b Inner peripheral surface 37 Cushioning material 33 1st Slide bearing 34 Second slide bearing 35 Contact portion 40 Motor device (drive device)
R rail D virtual circle L1 gap (predetermined gap set between the second sliding bearing and the contact portion)
L4 gap (gap between the inner peripheral surface of the shaft housing portion and the outer peripheral surface of the rotary shaft 31)

Claims (3)

A turntable on which a load is loaded, a loading table on which the turntable is disposed, a rotation support mechanism that rotatably supports the turntable with respect to the loading table, and the loading table by the rotation support mechanism A freight car that rotates a turntable that is rotatably supported with respect to the vehicle, travels on a rail, and rotates the turntable by the drive apparatus to change the direction of the load.
The rotation support mechanism is
A rotating shaft protruding from the lower surface of the turntable;
A shaft accommodating portion formed as a recess for accommodating the rotating shaft and disposed on the loading table;
A first sliding bearing disposed between opposed surfaces of the bottom surface of the shaft housing portion and the lower surface of the rotating shaft and supporting the rotating shaft;
A plurality of second plain bearings disposed on one of the lower surface of the turntable or the upper surface of the loading table and positioned on a virtual circle centered on the rotation axis;
An abutting portion that is in contact with the second sliding bearing and is disposed on the other of the lower surface of the turntable or the upper surface of the loading table and has a predetermined gap between the second sliding bearing; Prepared,
When the weight of the load is equal to or less than a predetermined value, the gap is maintained and the load in the vertical direction of the turntable is received only by the first sliding bearing,
When the weight of the load exceeds the predetermined value, at least the turntable is deformed and the gap is filled, so that the first slide bearing and the second slide bearing move in the vertical direction of the turntable. A freight car configured to receive a load. The shaft accommodating portion includes an inner peripheral surface formed with an inner diameter larger than the outer diameter of the rotating shaft,
The freight car according to claim 1, wherein a cushioning material is disposed in a gap between an inner peripheral surface of the shaft housing portion and an outer peripheral surface of the rotating shaft. At least three or more of the second sliding bearings are arranged at equal intervals in the circumferential direction,
The second sliding bearing is disposed at a position overlapping the support member interposed between the base supporting the axle of the wheel rolling on the rail and the loading base in the vertical direction of the loading base. The freight car according to claim 2, wherein:

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