JP2008162455A - Bogie for low-floor type railway vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bogie for a low-floor type railway vehicle capable of preventing wheel load omission with a low rolling rigidity at an shaft beam portion supporting right and left wheels and with a simple structure. <P>SOLUTION: A stationary axle 21 is formed by a shaft beam formed concave seen from a front view, and wheels 3 are rotatably supported on both sides of the stationary axle 21. A long shaft beam link member 22 integrally extends on one side of the stationary axle 21, and a short shaft beam link member 23 integrally extends on the other side, directing forward or backward, respectively. An extension shaft beam link member 24 is serially connected with a tip of the short side shaft beam link member 23 via a rubber bush 25 allowing bend in all directions. A shaft beam link 2 with a U-shape in plan view, which has an identical overall length of right and left link members is constituted. Both of side base ends of the shaft beam link 2 are journalled and connected to both of front and rear ends of a bogie frame body 51, in which side beams are integrally connected with each other by lateral beams formed concave seen from a front view, via rubber bushes 52, 53, so that the stationary axle 21 can rotate upward and downward. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a bogie for a low-floor railway vehicle that is particularly suitable for a low-floor type tram, and more specifically, for example, a bogie arranged in an intermediate vehicle of a knitted vehicle and applicable to a non-powered bogie, In particular, the present invention relates to a low-floor railcar bogie that is optimal as a power bogie.

  ・ In the 21st century, a full-fledged aging society is about to come, and LRV (Light Rail Vehicle) vehicles have been developed in Europe in response to mobility restrictions. A low-floor vehicle appeared. Later, low-floor vehicles were introduced or planned for introduction in various locations. In response to this background, the `` Ultra Low Floor Lbuoy Bogie Technology Research Association '' was established with the aim of developing a Japanese-style ultra-low floor LRV that can respond to environmental improvement and barrier-free by calling on the Ministry of Land, Infrastructure, Transport and Tourism. Various trucks were developed.

  ・ In parallel with this, purely domestic low-floor vehicles were first introduced in Kagoshima City (Transport), and were also introduced in Tosa Electric Railway and Iyo Electric Railway. For purely domestic vehicles, a two-axis bogie truck is installed under the cab, and the middle part has a low floor except for the truck part (partial low-floor vehicle: a vehicle with a part of the floor surface being a high floor and the other part being a low floor) Recently, a low-floor 30m class vehicle with similar specifications to that of European cars has been introduced to Hiroshima Electric Railway.

  ・ A 100% low-floor vehicle has been realized by using the independent wheel system used for the accompanying trolley of partially low-floor vehicles for power trolleys (trolleys for power vehicles, which are vehicles with power units). In order to use this independent-wheel-type carriage as a power carriage, manufacturers have come up with various ideas for the main motor mounting method and drive device, and are competing.

  ・ Conventionally constructed power bogies are equipped with a motor and a reduction gear device in the space between a pair of axles, and are called parallel cardan type or right angle cardan type because of differences in the main motor arrangement. On the other hand, in a 100% low floor vehicle, the space is included in the vehicle body, so the arrangement structure of the driving device and the main motor is a key point of the power truck.

  As described above, there are various arrangement methods for the 100% low-floor power truck, which can be roughly classified into the following methods (see FIG. 19).

1) Body-mounted main motor and propeller shaft system (Fig. 19 A type)
2) Wheel built-in main motor system (hub motor system) (Fig. 19 C type)
3) Main motor bogie mounting system (Fig. 19 B, E type and many E type variants)
4) Main motor vertical installation gate type articulated carriage (D type in Fig. 19)
・ The method 1) is a system in which the main motor mounted in the rail direction under the vehicle body floor is transmitted by a universal joint and a spline shaft, and power is transmitted to a pair of wheels by a torsion shaft.

  -The method of 2) is a method in which one main motor is built in one wheel and the rotational force is transmitted to the yoke of the main motor with the wheels integrated by a planetary gear. There is also a direct drive method without a planetary gear.

  ・ The method of 3) is the most, and various methods are used by each manufacturer. The characteristics are shown below.

    a) The method adopted in “Eurotram” (LTRV in Strasbourg, France) is a system in which one small main motor is mounted on one wheel in a suspended manner on the outside of the axle box and driven via gears. .

    b) “Conbino (LRV of Hiroshima Electric Railway) is a system in which a main motor that is elongated in the rail direction is mounted between two axle boxes on the side of a truck and driven through gears.

c) “Citades (LRV in Lyon, France)” uses a method in which a small main motor is mounted in the direction of a sleeper at the diagonal position of the carriage frame, and the wheels directly below are driven via gears. The wheel to become is driven by the torsion shaft.

d) The method adopted in "Incentro (LRV of Nantes, France)" is a system in which the main motor is attached to the carriage frame in the rail direction and one wheel is driven by one main motor via a gear.

    e) The method adopted in “Urubos (Leeds LRV)” has a short fixed shaft distance, so the main motor is mounted in the direction of the sleeper between the bogie axle boxes, and the front and rear wheels are driven via gears. To do.

  ・ The method of 4) is a two-wheel gate type connecting cart with a main motor mounted vertically, with the idea that wheels are arranged at the connecting part in order to secure the passage width of the low floor part.

by the way,
A) Wheel weight loss (a phenomenon in which the weight of the vehicle body that should be applied equally to all wheels becomes unbalanced for some reason and the weight of the vehicle body applied to one wheel decreases) Although it is also affected by the height, if the influence of the height of the center of gravity is ignored, this phenomenon occurs because the spring constant of the shaft spring is high (the spring is stiff) and the rigidity in the roll direction of each axis of the carriage (rolling) This is because the surface of each wheel does not exist on a single plane because the instability support is likely to occur. Therefore, because each wheel of the carriage is standing on a flat surface, if the wheel is lifted along the flange shape of the wheel due to an irregular track or lateral pressure, the adjacent wheel tends to float. In such a case, the wheel weight of the wheel may come off.

  B) From the current situation as described above, it is necessary to develop a cart that has a structure that does not cause wheel weight loss in advance.

  Now, as a prior art related to a low-floor railway vehicle power bogie, in order to lower the floor surface, large-scale equipment such as an electric motor is not placed under the floor of the vehicle, and the drive shaft is installed on both sides of the bogie frame. A low-floor railway vehicle has been proposed in which an axle disposed so as to face the vehicle traveling direction and an axle disposed so as to be orthogonal to the vehicle traveling direction and a drive shaft of the motor are connected via a gear device (for example, Patent Document 1 and Patent Document 2).

  In Patent Document 1, two electric motors are attached to intermediate positions in the longitudinal direction of beams on both sides of a carriage frame having concave lateral beams, and each electric motor has two sets of universal joints (universal joints). The power transmission device is provided between a gear device that includes a power transmission mechanism and is coupled to a wheel axle that is disposed orthogonal to the drive shaft of the electric motor, and is positioned before and after the electric motor on each side beam. Each wheel unit drives each wheel, and each gear unit has a built-in wheel box box, and a shaft box unit that supports each wheel / axle with respect to a support frame member extending in the longitudinal direction at the upper end of the bogie frame via a shaft spring. In addition, there is described a power trolley including an axle box support device supported so as to be displaceable in the vertical direction.

In Patent Literature 2, an electric motor with a rotating shaft arranged in the vehicle traveling direction is attached to both sides of the bogie frame, and a gear device that changes the axial direction of the driving shaft by 90 degrees is connected to the driving shaft of the electric motor. A wheel having an axle connected to a rotation shaft of the gear device is disposed inside the gear device, and the axle of the wheel is connected to the drive shaft of the electric motor via the gear device, and the axle is a gear. It is slidable in the axial direction of the axle with respect to the rotating shaft of the device, and is attached to the rotating shaft of the gear device via a coupling mechanism having a rotation stopping function so that the axle and the rotating shaft of the gear device rotate together. A power trolley of the same structure is described. The gear device is attached to the carriage frame via a suspension link, and the gear device is prevented from rotating.
JP 2003-25989 A (Pages 3 and 4 and FIGS. 1 and 2) JP-A-2005-212711 (pages 3 to 5 and FIGS. 1 to 4)

  The power truck for a low floor type railway vehicle described in Patent Document 1 and Patent Document 2 described above has the following problems.

  In the former case, the relative displacement between the electric motor and the gear device due to the deflection of the shaft spring, as determined from the arrangement of the shaft box support device and the gear device, is a telescopic structure of the drive shaft with two sets of universal joints interposed. It is absorbed by the expansion and contraction of the (spline mechanism or the like). Therefore, it is necessary to increase the length of the power transmission device. Moreover, in order to follow the vertical displacement of the speed reducer device including the wheel and the shaft box support device or the gear device, it is necessary to ensure a sufficiently long extension / contraction amount of the drive shaft using the extension / contraction structure.

  In the latter case, the arrangement of gears and electric motors is basically the same as that of the former device. However, the reaction force accompanying the vertical displacement of the gear device can be obtained by supporting the gear device on the carriage frame with a suspension link. Is received by a hanging link. For this reason, the attitude | position when the transmission including a gear apparatus displaces to an up-down direction can be hold | maintained. Moreover, the structure which can be displaced to an up-down direction is employ | adopted for the axle box support apparatus, maintaining a horizontal attitude | position for both front and rear persons. Further, since the gear device is displaced in the vertical direction by substantially the same distance in accordance with the vertical displacement of the axle and the wheel, the mass of the gear device is an unsprung mass (unsprung load). In the latter case, as in the former case, it is necessary to use a stretchable structure for the power transmission mechanism, which is structurally complicated.

  The present invention has been made to solve the above-mentioned problems. In order to lower the floor surface, motors are provided on both side surfaces of the outer side of the carriage frame so that the drive shaft faces the vehicle traveling direction (front-rear direction). Even when it is arranged so as to be orthogonal to the vehicle traveling direction, the wheels can be driven without using a telescopic structure on the drive shaft that extends from the electric motor in the vehicle traveling direction. Furthermore, the mass of the gear unit is also borne by the bogie frame, so the unsprung mass can be reduced, and the structure as a bogie is simple even when applied to a non-driving bogie, supporting the left and right wheels. Accordingly, the present invention is to provide a low-floor railcar bogie that has a low rolling rigidity at the shaft beam portion and that can prevent wheel weight loss.

  In order to solve the above-mentioned problems, a low-floor railway vehicle bogie (non-drive bogie) according to claim 1 of the present invention forms a fixed axle by a shaft beam having a concave shape when viewed from the front, and is provided on both sides of the fixed axle. A wheel is rotatably supported, and a long shaft beam link member is integrally extended toward the front or the rear on one side of the fixed axle, and a short shaft beam link member on the other side. The extended-axis beam link member is connected to the tip of the short-side shaft beam link member in a straight line, allowing bending in all directions under the intervention of an elastic body, etc., and the entire length of the left and right link members is equal. The shaft beam link has a U-shaped shaft beam link, and the both side base ends of the shaft beam link are opposed to the front and rear ends of both sides of the bogie frame integrally connected with the side beams by a concave beam viewed from the front. The fixed axle side is pivotally connected so that it can rotate in the vertical direction. It is characterized in.

  Since the cart according to claim 1 having the above-described configuration supports the wheels on both sides via connecting means such as an axial beam link and an elastic body that allows bending in all directions with respect to the cart frame, The rolling frame of the entire supporting frame is low and has a certain degree of freedom, and the wheels are supported by a so-called flexible shaft beam support structure. Even when trying to lift up from the wheel, this lifting force is absorbed by the displacement of the connecting means such as an elastic body or the shaft-and-beam link, and is not transmitted directly to the other wheel, so the wheel load of the other wheel does not decrease. Accordingly, the wheels are not lifted up and are kept in contact with the track, so that stable running can be performed in a good state.

  In addition, when a wheel is displaced in the vertical direction during traveling and a shaft spring or the like that elastically supports the left and right wheels in the vertical direction is bent, the shaft beam link that supports each wheel is the wheel in the shaft beam link. The fixed axle (wheel) side rotates (swings) in the vertical direction around the pivot point (connection point) on the opposite side (cart frame side) as the rotation center, and follows the vertical displacement of the wheel. In addition, since the horizontal frame that connects the beams on both sides has a concave shape in the front view and the position (height) in the vertical direction of the floor surface can be set low, the bogie frame can realize a vehicle with 100% low floor. Needless to say.

  The low-floor railcar bogie (power bogie) according to claim 2 forms a fixed axle by a shaft beam having a concave shape when viewed from the front, and rotatably supports wheels on both sides of the fixed axle. A long shaft beam link member is integrally extended on one side of the two sides, and a short shaft beam link member is integrally extended forward or rearward on the other side, and an extension shaft is provided at the tip of the short side beam link member. The beam link members are connected in series in a straight line, allowing bending in all directions under the intervention of an elastic body, etc., and a shaft beam with a "U" shape in plan view in which the total length of the left and right link members is equal. Consists of a link, and the front and rear ends of both sides of the bogie frame that are integrally connected between the side beams by a concave horizontal beam when viewed from the front, both side base ends of the shaft beam link can be rotated vertically on the fixed axle side. It is pivotally connected and beams on both sides of the bogie frame. An electric motor is mounted at an intermediate position in the front-rear direction, and a power transmission mechanism that can be refracted in the vertical direction at an intermediate position in the longitudinal direction is projected from the electric motor to at least one of the front and rear, and through the power transmission mechanism and the reduction gear mechanism It is configured to drive at least one of the front and rear wheels, and a shaft beam member extends from the gear box covering the periphery of the reduction gear mechanism toward the outside of the driven wheel toward the carriage frame. One end of the shaft beam member is pivotally connected to the lower end of a suspension link that is suspended by pivotally connecting the upper end to the same carriage frame, and the gear box is vertically moved around the virtual rotation center position on the lower extension line of the suspension link. The imaginary rotation center position, the pivot connection position of the shaft beam link base end with respect to the carriage frame, and the refracting center position of the power transmission mechanism are respectively matched with each other. Characterized in that was.

  The cart according to claim 2 having the above-described configuration is the one in which the cart according to claim 1 is applied to a power cart, and when the left and right wheels are displaced in the vertical direction, the wheel support side of the shaft beam link is the cart frame. The power transmission mechanism wheel rotates and swings in the vertical direction around the center of rotation, and the wheel side of the power transmission mechanism also rotates and swings in the vertical direction around the center of refraction. And since the pivot connection position of the shaft beam link, the refractive center position of the power transmission mechanism, and the virtual rotation center position of the gear box coincide with each other, the longitudinal direction of the power transmission mechanism accompanying the displacement of the wheel in the vertical direction ( Since the expansion / contraction action in the axial direction) hardly occurs, it is not necessary to make the power transmission mechanism extendable / contractible in the axial direction. Thereby, the structure of the power transmission mechanism is simplified, and the power transmission efficiency is improved. In addition, since an electric motor, a power transmission mechanism, a reduction gear mechanism, and the like are provided on the outer surface side of the beam on the side of the carriage frame, and no large equipment is disposed under the floor of the vehicle (vehicle body), a 100% low floor vehicle is realized. . Further, even if one of the left and right wheels is lifted by the track due to, for example, an irregular track, this lifting force is absorbed by the bending and displacement of the connecting means such as the elastic body and the shaft beam link member, and the other wheel Since the wheel weight of the other wheel does not decrease, the wheel weight is unlikely to fall out and is kept in contact with the ground on the track. The effect similar to the effect by invention of Claim 1 arises.

  The overall shape of the link member comprising the long shaft beam link member, the fixed axle shaft and the short shaft beam link member is formed in a substantially J shape (substantially L shape) in plan view, The entire shape of the shaft beam link including the extended shaft beam link member can be formed in a substantially U shape (U-shape) in plan view.

  With this configuration, the shaft spring expands and contracts with the vertical movement of the left and right wheels, and at the same time, the substantially J-shaped link member mainly moves in the vertical direction with the pivot connection position on the cart frame side as the rotation center (left and right It is pivotally supported on the side of the carriage frame so that it rotates and swings (displaces) relatively, and the extension shaft beam link member follows the swing (displacement) of the substantially J-shaped link member. Relatively rotates and swings (displaces) in the vertical direction with the connection position as the center of rotation (in some cases, in the left-right and axial directions).

  The drive shaft projects from the electric motor to at least one of the front and rear sides of the electric motor, and a flexible joint (torque transmission is possible) is provided at an intermediate position of the drive shaft. The rotational force of the electric motor is rotated by 90 ° through a pair of (small and large gears) hypoid gears or a pair of bevel gears (for example, a bent bevel gear, a close bevel gear, and a helical bevel gear) that are engaged at right angles. It is configured to convert and transmit to the wheel to drive the wheel, and the bending center position of the flexible joint, the pivot connection position of the shaft beam link base end with respect to the carriage frame, and the virtual rotation center position mutually coincide with each other Can be made.

  By configuring in this way, the rotational force generated by the motor is driven in the order of drive shaft, flexible joint, drive shaft, hypoid gear (small gear, large gear) or bevel gear (bevel gear, bevel gear), wheel (axle). The rotation direction is changed by 90 ° with a gear and transmitted to the wheel, and the wheel rotates. When the wheel is displaced up and down due to an irregular track or the like when the vehicle is running, the shaft beam link rotates and swings in the vertical direction with the pivot connection position as the rotation center, and at the same time, the wheel side of the drive shaft is at the center position of the flexible joint. It rotates and swings in the vertical direction with the (refractive center position) as the rotation center, and follows the displacement of the wheel. Further, since the drive shaft itself with the refracting power transmission mechanism interposed therebetween does not need to have a telescopic structure, the structure is not complicated and the transmission efficiency of the rotational force (driving force) is improved. It will not decline.

  Since the low-floor railcar bogie according to the present invention is configured as described above, the following excellent effects can be obtained. That is, since each wheel is supported on both sides via a connecting means such as a shaft beam link and an elastic body that allows bending in all directions with respect to the bogie frame main body, the rolling rigidity of the entire bogie frame that supports the wheels is low, Since the wheels are supported by a so-called flexible shaft beam support structure with a certain degree of freedom, even if one of the left and right wheels is lifted from the track due to an irregular track, for example, this lifting force is It is absorbed by the displacement of the connecting means such as the shaft beam link or the elastic body and is not transmitted directly to the other wheel, so the wheel weight of the other wheel does not decrease, the wheel is lifted carelessly or the wheel weight is lost. Since it does not occur and is maintained in a grounded state on the track, a good and stable running state can be maintained. In addition, when the wheel is displaced in the vertical direction during running and the shaft springs etc. that elastically support the left and right wheels bend, the shaft beam link that supports each wheel is the opposite side of the wheel in the shaft beam link ( The wheel side rotates (swings) in the vertical direction around the pivot connection position on the cart frame side), and follows the vertical displacement of the wheel.

  Embodiments of a low-floor railway vehicle carriage according to the present invention will be described below with reference to the drawings.

  FIG. 1 is a side view vertical sectional view showing a three-car train low-floor type tram equipped with a carriage according to an embodiment of the present invention, and FIG. 2 (a) is a low-floor type tram shown in FIG. 2B is a cross-sectional view taken along the line bb in FIG. 2A, and FIG. 2C is a cross-sectional view taken along the line cc in FIG. 2A. FIG. 3A is an enlarged plan view of the carriage portion of the carriage, and FIG. 3B is a side view thereof. 4A is a plan view taken along line aa showing a part of FIG. 3A in cross section, FIG. 4B is a view taken along line bb in FIG. 3A, and FIG. ) Is a sectional view taken along line cc in FIG. 4A, and FIG. 4D is a sectional view taken along line dd in FIG. 4A. FIG. 5A is a plan view conceptually showing the basic principle of the shaft beam support structure of the cart of this example, and FIG. 5B is a plan view conceptually showing the basic principle of a general shaft beam support structure. is there. 6A is a view in the direction of the arrows (A)-(A) in FIG. 3A, FIG. 6B is a view in the direction of the arrows BB in FIG. 3A, and FIG. ) Is a view in the direction of arrows CC in FIG. In FIG. 5, the bogie frame is omitted.

  As shown in FIGS. 1 and 2, the cart 1 of this example is used as a power cart (driving cart) in an intermediate vehicle 6 of a three-car train low-floor type tram 10. Further, the shaft beam support structure for rotatably supporting the wheels 3 on both sides is a fixed axle disposed in the vehicle width direction of the shaft beam link 2 as shown in FIGS. 5 (a) and 6 (a). A non-rotating axle 21a projects outwardly on both sides of the wheel 21, and wheels 3 and 3 are rotatably supported on the axle 21a via bearing devices 4j (see FIG. 8). As shown in FIG. 4B, the fixed axle 21 is formed in a concave shape when viewed from the front by a shaft beam. As shown in FIG. 5A, one of the two sides of the fixed axle 21 (on the left side in this example) is provided. One end of the long shaft beam link member 22 extends toward the rear or front bogie frame main body 51 (see FIGS. 3 and 6), and one end of the short shaft beam link member 23 is connected to the other fixed axle 21. It extends integrally toward the front or rear bogie frame main body 51 (see FIG. 3), and is formed in a substantially L (or substantially J) shape when seen from the plane. An extension shaft beam link member 24 is pivotally connected to the tip of the short-side shaft beam link member 23 via a rubber cylinder (hereinafter also referred to as a rubber bush) 25, and one of the left and right shaft beam links is connected. The member 22 and the other axial beam link member (23 + 24) are configured such that their full lengths L1 and L2 are equal to each other. Further, the short-side shaft beam link member 23 and the extended shaft beam link member 24 allow bending in all directions (mainly in the vertical direction) by a rubber bush 25 described below. In this way, the axial beam link 2 having an overall shape of “U” in plan view is configured, and the base ends on both sides of the axial beam link 2 are as shown in FIGS. 3 (a), 6 (b) and 6 (c). Are pivotally connected to the front and rear ends of both sides of the main body 51 of the carriage frame 5 via rubber cylinders (hereinafter also referred to as rubber bushes) 52 and 53 so as to be swingable at least in the vertical direction. Further, the shaft spring 4 is mounted between the shaft box 41 (upper surface) of the shaft beam link 2 and the front / rear horizontal plate-like portion 54a (lower surface) of the carriage frame 5 described below.

  FIG. 5 (b) shows a basic structure of a conventional general shaft beam link 2 ′, and is provided integrally with link members 22 having an equal length that extend toward the carriage frame 5 on both sides of the fixed axle 21. For this reason, the fixed axle 21 serves as a torsion bar, and the shaft beam link member 22 serves as a torsion bar arm, which constitutes a torsion bar of a so-called anti-rolling device. The beam link 2 ′ itself lacks flexibility, and if the wheel 3 on one side is lifted by the rail due to an irregular track or the like, the lifting force is directly transmitted to the wheel 3 on the other side, and wheel load loss is likely to occur. .

  In FIG. 5 (a), the bogie frame 5 (see FIG. 3) is omitted, but the base ends on both sides of the shaft beam link 2 are connected to the rubber bushes 52 and 53 on the front and rear sides of the bogie frame main body 51 (see FIG. 3). Via the horizontal pin 57 (refer to FIG. 5B), the wheel 3 side is pivotally connected so as to be rotatable (swingable) in the vertical direction. Since the structure of the shaft beam link 2 is as described above, the description thereof is omitted.

  Further, the shaft beam link 2 divides the shaft beam link member 22 on one side into a link member 23 and a link member 24, and when rolling displacement occurs, a connecting portion 25 (rubber bush or spherical bearing) of both the link members 23 and 24. Therefore, unlike the axial beam link 2 'in FIG. 5B, an anti-rolling device is not configured.

  As shown in FIG. 6 (a), the carriage frame 5 is integrally connected by a lateral beam 55 having a concave shape when viewed from the front side. In addition, the horizontal beam 55 is provided with a plurality of substantially rectangular openings 55a as shown in FIG. 3A for light weight, rational arrangement of components, arrangement of strength members, and maintenance. In the carriage frame main body 51, the side beams 54 extend upward, the horizontal plate portions 54b project horizontally from the upper ends of the side beams 54 on both sides, and the front and rear horizontal plate portions 54a are horizontally directed forward or rearward. Overhangs. Further, the vehicle body 6A (FIG. 1) is placed via pillow springs 56 that are respectively installed on the front part and the rear part of the side horizontal plate-like parts 54b of the carriage frame body 51. The carriage 1 and the vehicle body 6A placed thereon are connected by a pair of traction devices 61, 61, and stoppers 62, 62 disposed opposite to each other in the opening 55a of the lateral beam 55 of the carriage 1. This restricts the rolling of the vehicle body 6A. For this reason, the support piece 63 protrudes downward from the bottom of the vehicle body 6A toward the stoppers 62 and 62.

  The rubber bushes 25 and 52 (53) include, for example, a flexible joint using an elastic body or a spherical bearing that allows bending deformation in all directions as shown in FIGS. Torque cannot be transmitted) 25-1 (FIG. 12) and flexible joint 25-2 (FIG. 13) are used. The flexible joints 52-3 and 53-3 shown in FIG. 14 are integrally formed at the end of the long-side shaft beam link member 22 or the short-side shaft beam link member 23. The flexible joints 25-4 and 53-4 shown in FIG. 15 have the same structure as the flexible joints 52-3 and 53-3, and are attached to both ends of the extension shaft beam link member 24 and the traction device 61 by press fitting or the like. Is done.

  At the intermediate position in the longitudinal direction of each side beam 54, the electric motor 8 is mounted with projecting drive shafts 81 (see FIG. 7) projecting in the front and rear sides, and can rotate integrally with the front end portion of each drive shaft 81g (FIG. 7). Reduced gears that reduce the speed and change the direction of rotation to a right angle, such as the attached bevel gear 82a (or hypoid gear small gear) and the bevel gear 82b (or hypoid gear large gear) that are attached to the tip of the axle 21a so as to be integrally rotatable. A rotational force is transmitted to the wheel 3 by the gear mechanism 82 (FIG. 7). In FIG. 8, the drive shaft 81g and the bevel gear 82a are shown in the vertical direction in the drawing, but are actually in the horizontal direction. Further, the following flexible joint (power shaft joint) 84 is provided at an intermediate position between the front and rear drive shafts. Therefore, in this example, the power transmission mechanism 12 is configured by combining the drive shaft 81 (FIG. 7), the flexible joint 84, and the reduction gear mechanism 82 (FIG. 7).

  The flexible joint 84 includes a power shaft joint (flexible gear joint 84-1, double universal joint 84-2, constant velocity joint 84-3, illustrated in FIG. Can be used. Further, as shown in FIG. 3, the pivot connection positions (rubber bushings 52 and 53) at both ends of the shaft beam link 2 and the center position (refractive part center point) of the flexible joint 84 are made to coincide with each other. .

  Further, as shown in FIG. 8, a bevel gear 82b (or hypoid gear) is attached to the wheel 3 so as to be rotatable integrally with the wheel 3 on the outer side of the wheel 3 of the axle 21a, and the bevel gear 82a (or the gear meshed perpendicularly to the bevel gear 82b) The reduction gear mechanism 82 including the hypoid gear) is surrounded by the gear box 31. As shown in FIG. 3, the gear box 31 is integrally connected to the tip of a “beam-shaped” shaft beam 32 (in other words, the shaft beam 32 extends backward slightly upward from the gear box 31). The base end of the shaft beam 32 is pivotally connected to the lower end of a suspension link 33 that hangs down from the front end or the rear end on both sides of the carriage frame main body 51 with a shaft beam pin 32a. Further, the upper end of the suspension link 33 is pivotally connected to a bracket 51a attached to the upper end on both sides of the carriage frame main body 51 by a suspension link pin 33a. With this configuration, the gear box 31 is located on the lower extension line of the suspension link 33, the pivot connection positions (rubber bushings 52 and 53) on both ends of the shaft beam link 2 (FIG. 5A), and the flexible joint 84. The position corresponding to the refraction center position is displaced in the vertical direction with the virtual rotation center as the position.

  7 (a) and 7 (b) schematically show the basic structure of the carriage 1 of the present invention. The shaft beam support structure is omitted, and the shaft beam link member and the gear box are overlapped when viewed from the side. Represents. In the case of this example, when the wheel 3 is displaced in the vertical direction, the shaft beam link member 22 swings in the vertical direction together with the gear box 31 around the shaft beam pins 52 and 53, and at the same time in the power transmission mechanism 12 of the electric motor 8. The reduction gear mechanism 82 side swings up and down (arc-shaped rotation) together with the drive shaft 81g with the intermediate position in the longitudinal direction of the flexible joint 84 as the rotation center. 7 (c) and 7 (d) show a known structure (method shown in the prior art) in which the axle box 41 is supported by a pair of axle springs 4 and 4. In the case of this example, gears are shown. The box 31 moves up and down. Further, since the drive shaft 81 and the drive shaft 81g are displaced in parallel up and down, the distance changes in an oblique direction connecting the center of the drive force transmission gear portion between the drive shafts 81 and 81g. There is a stretching action.

  Returning to the explanation of FIG. 3, as a result, when the carriage 1 travels on the rail R, the left and right wheels 3 are temporarily moved by the rail R (trajectory) due to irregularities such as the height of the rail R (trajectory). Even if it is lifted, this lifting force is absorbed by the displacement of the flexible beam-beam link 2 and is not transmitted directly to the opposite wheel 3. The weight is not reduced, and therefore, the wheel 3 on the opposite side does not float up, and is kept in contact with the rail R, and there is almost no risk of wheel weight loss. Further, when the left and right wheels 3 and 3 are displaced in the vertical direction during traveling and the shaft springs 4 and the like that elastically support the wheels 3 are bent, the shaft beam links 2 that support the wheels 3 The wheel 3 side rotates in the vertical direction around the pivot point (connection point) of the shaft beam link 2 on the opposite side (the carriage frame main body 51 side) and follows the displacement of the wheel 3 in the vertical direction.

  When there is a difference between the deflections of the left and right shaft springs, the shaft beam link members 23 and 24 are bent and buffered in the vertical direction at the connecting portions 25 of the shaft beam link members 23 and 24. If the influence of this case is explained by an assumed value, when the deflection difference between the left and right shaft springs is 10 mm and the extension shaft beam link member 24 has a length of 200 mm, the displacement in the front-rear direction is about 0.25 mm and is absorbed by the elastic body of each part It is an error range as far as possible.

  Further, as shown in FIG. 3B, the rail brake 9 is suspended by a pair of front and rear springs 91 immediately above the rail R between the front and rear wheels 3 and 3 at the lower end of the bogie frame main body 51. . A magnetic force is generated by passing a current through an electromagnetic coil (not shown) in the rail brake 9, and the magnetic force is attracted to the rail R to act as a brake. On the other hand, when the current is cut off, the rail brake 9 is raised by the urging force of the spring 91 and separated from the rail R.

  Next, the vehicles 7 and 7 of the first and third cars will be described. As shown in FIGS. 1 and 2, a pair of left and right pillow springs 72 are provided below the frontmost end and the rearmost end of the vehicle 7. A uniaxial bogie bogie 71 with a guide wheel provided with a pillow beam 73 to be attached is provided. Each uniaxial bogie bogie 71 is provided with a bogie frame 75 supported at the center position in the width direction of the pillow beam 73 so as to be able to turn horizontally around the center plate 74. The bogie frame 75 includes a main wheel bogie frame portion 77 in which a main wheel shaft provided with large-diameter wheels 76 so as to be integrally rotatable on both sides of an axle 76a is rotatably mounted across the main axle frame, and both sides of the axle 78a. A sub-wheel shaft provided with guide wheels 78 made of small-diameter wheels so as to be integrally rotatable is divided into a guide wheel frame portion 79 that is rotatably mounted across the sub-axle frames.

  The left and right guide wheels 78 rotate with respect to the main wheel bogie frame portion 77 in the roll direction about the support shaft, and swing in the pitch direction about the horizontal pin via the auxiliary axle frame. Further, since the guide wheel 78 is urged downward by the shaft spring, it is pressed against the rail R with a constant load. Thereby, wheel weight loss such as the guide wheel 78 floating above the rail R is prevented, and at the same time, contact between the guide wheel 78 and the lower surface of the vehicle body 7A of the vehicle 7 is avoided.

  As described above, the three-car train low-floor type tramway including the carriage according to the embodiment of the present invention is configured. As shown in FIG. 1 or FIG. 2, the low floor type tram 10 of the present example has a cab D at the front and rear ends of the first and third vehicles 7, and is 100% lower from the cab D toward the center. In the cabin P on the floor, the cab D is slightly higher than the cabin P, and the pillow beam 73 of the single-shaft carriage 71 with a guide wheel is attached via a pillow spring 72 below the floor 7b of each cab D. The large-diameter wheel 76 is disposed under the cab D. The guide wheel 78 is disposed near the center of the vehicle body 7A and below the low floor surface 7a of the passenger cabin P. In the passenger compartment P of the intermediate vehicle 6 and the vehicle 7, the seats 6c and 7c are arranged facing each other in the vehicle width direction, and the floor surface under the seat 7c and the floor surfaces 6a and 7a of the passages 6d and 7d are both low floor surfaces. ing. Further, an entrance / exit 7e is provided adjacent to the seat 7c of each vehicle 7 before and after the tram 10, but the floor surface of the entrance / exit 7e has the same low floor surface as the passage 7d. That is, the tram 10 is a 100% low floor vehicle except for the cab D. Reference numeral 95 in FIG. 1 is a pantograph.

  In this example, the case where the present invention is applied to a three-car train low-floor type tram is described. However, as shown in FIG. An intermediate vehicle 6 'is connected between the carriages 1 and 1 of the intermediate vehicle 6, and a uniaxial carriage 71 with guide wheels is provided at the foremost end of the first vehicle 7 and the rearmost end of the fifth vehicle 7, % Low-floor vehicles can also be realized. In addition, since it is the same as that of the tram 10 shown in FIG. 1 about other configurations, common members are denoted by the same reference numerals and description thereof is omitted.

  Further, as shown in Fig. 18, a three-car train low-floor type tram 10 "can be used, and a carriage 1 is arranged under a driver's cab D. In this example, the vehicles at both the front and rear ends are illustrated. 16, the vehicle 7 with the cab D and the intermediate vehicle 6 are overlapped with each other, and the front-end cart 71 with the guide wheel is omitted. The intermediate vehicle 6 'shown in Fig. 16 is connected between the two to form a single-unit vehicle, and also in this example, a vehicle with 100% low floor near the center from the cab D is realized. Since other configurations are common to the tram 10 shown in Fig. 1, common members are denoted by the same reference numerals, and description thereof is omitted.

  Moreover, although the case where the cart 1 was applied to the power cart was shown in the above embodiment, for example, the power transmission mechanism 12 including the support mechanism of the gear box 31 via the shaft beam 32 and the motor 8 and the flexible joint 84 in FIG. It is also possible to configure a non-powered carriage with only the axial beam link 2 as shown in FIG.

  Although the embodiment of the present invention has been described above, the present invention is not limited to the above-described embodiment. For example, the axle 21a on which the wheel 3 is rotatably mounted can be rotated on both side surfaces of the fixed axle 21 of the shaft beam link 2. It can also be attached to.

  As for the driving method of the wheel 3 of the carriage 1, a diagonal driving method, a method of driving only one of the front and rear wheels, and a combination of two motors (not one motor) in the front-rear direction are combined. The wheel can be driven by the integrated electric motor.

  Furthermore, although the embodiment of the present invention has been described based on a low-floor tram, the same system can be applied to a high-floor general railway vehicle. In this case, it is possible to configure the fixed axle 21 and the horizontal beam 55 at the upper part without lowering the central part.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a side view longitudinal sectional view showing a three-car train low-floor type tram equipped with a carriage according to an embodiment of the present invention in an intermediate vehicle. 2A is a floor layout of the low-floor type tram shown in FIG. 1, FIG. 2B is a cross-sectional view taken along the line bb of FIG. 2A, and FIG. 2C is FIG. It is a cc line sectional view of). FIG. 3A is an enlarged plan view of the bogie portion of the intermediate vehicle, and FIG. 3B is a side view thereof. 4A is a plan view taken along line aa showing a part of FIG. 3A in cross section, FIG. 4B is a view taken along line bb in FIG. 3A, and FIG. ) Is a sectional view taken along line cc in FIG. 4A, and FIG. 4D is a sectional view taken along line dd in FIG. 4A. FIG. 5A is a plan view conceptually showing the basic principle of the shaft beam support structure of the cart of this example, and FIG. 5B is a plan view conceptually showing the basic principle of a general shaft beam support structure. is there. 6A is a view in the direction of the arrows (A)-(A) in FIG. 3A, FIG. 6B is a view in the direction of the arrows BB in FIG. 3A, and FIG. ) Is a view in the direction of arrows CC in FIG. 7 (a) and 7 (b) are side views schematically showing a basic structure including a power transmission mechanism in the carriage of the present invention, and FIG. 7 (b) is a state in which the wheel is displaced by rotating in a vertical arc shape. Represents. FIGS. 7C and 7D are side views schematically showing a state in which the power transmission mechanism in the carriage of the present invention is applied to a shaft box support structure in which the wheels are vertically displaced in the vertical direction, and FIG. This represents a state in which the wheel is displaced vertically in the vertical direction. It is sectional drawing which expands and shows the reduction gear mechanism and its periphery in the trolley | bogie of this example. It is sectional drawing which shows the flexible gear joint 84-1, which is an example of a flexible joint, (a) is the state in which the front-and-rear drive shaft 81 does not have a relative displacement, (b) is only the front drive shaft 81 up and down. An inclined state (c) shows a state in which the front and rear drive shafts 81 are inclined and relatively displaced in parallel. FIG. 10A is a side view showing a double universal joint 84-2 as an example of a flexible joint, and FIG. 10B is a cross-sectional view taken along line BB of FIG. 10A. It is a side view which shows the constant velocity joint 84-3 which is an example of a flexible joint. 12A is a plan view showing a flexible joint 25-1, which is an example of a flexible joint using an elastic body that allows bending deformation in all directions, and FIG. 12B is a side view thereof. is there. FIG. 13A is a side view showing a part of a flexible joint 25-2, which is an example of a flexible joint using a spherical bearing that allows bending deformation in all directions, and FIG. b) is a plan view of the same. 14A is a plan view showing a flexible joint as an example of a flexible joint using an elastic body that allows bending deformation in all directions, and FIG. 14B is a cross-sectional view showing the same part. FIG. 14 (c) is a side view thereof. FIG. 15B is a plan view showing a structure in which flexible members having the same structure as the flexible joint in FIG. 14 are provided on both sides of the extension shaft beam link member 24, and FIG. 15 (c) is a cross-sectional view showing a flexible joint portion. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal side view showing a 5-car train low-floor type tram provided with a carriage according to an embodiment of the present invention. It is explanatory drawing showing operation | movement at the time of the fixed axle 21 side being displaced to an up-down direction in the axial beam support structure of the trolley | bogie of this example. 1 is a side view longitudinal sectional view showing a three-car train low-floor type tram equipped with a dolly according to an embodiment of the present invention under a cab D. FIG. It is a reference drawing which shows the form and application example of a power trolley for 100% low floor vehicles.

Explanation of symbols

1 dolly (powered dolly)
2 axle beam link 3 wheel 4 axle spring 5 bogie frame 6 intermediate vehicle 6 'intermediate vehicle 6A vehicle body 6a, 7a low floor surface of guest room P 6c, 7c seat 6d, 7d passage 7 vehicle 7' vehicle 7A vehicle body 7b of cab D Floor surface 7e Entrance / exit 8 Electric motor 9 Rail brake 10 Low floor type streetcar 12 Power transmission mechanism 21 Intermediate vehicle 21 Fixed axle 21a Non-rotating axle 22 Long side shaft beam link member 23 Short side shaft beam link member 24 Extension shaft beam link Member 25, 52, 53 Rubber bushing 25-1 Flexible joint 31 Gear box 32 Shaft beam 33 Suspension link 32a Shaft beam pin 33a Suspension link pin 41 Shaft box 51 Bogie frame main body 51a Bracket 54 Side beam 54a Horizontal of bogie frame 5 Plate-like part 55 Horizontal beam 56 Pillow spring 57 Horizontal pin 61 Traction device 62 Stopper 71 Uniaxial bogie with guide wheel 72 Pillow spring 7 Pillow beam 74 heart quite common 75 bogie frame 76 large diameter wheel 77 main wheels carriage frame 78 derived wheel (small wheel)
79 Guide wheel stand frame 81 Drive shaft 82 Reduction gear mechanism 84 Flexible joint 95 Pantograph D Driver's cab P Guest room

Claims (4)

A fixed axle is formed by a shaft beam that is concave when viewed from the front, and wheels are rotatably supported on both sides of the fixed axle.
A long shaft beam link member is extended integrally on one side of the fixed axles, and a short shaft beam link member is integrally extended forward or rearward on the other side,
The extension shaft beam link member is connected to the tip of the short side shaft beam link member in a straight line while allowing bending in all directions under the intervention of an elastic body or the like, and the total length of the left and right link members is equal. Constructing an axial beam link with a “U” shape in plan view
The front and rear ends of both sides of the bogie frame integrally connected between the side beams with a concave beam that is concave when viewed from the front are pivotally connected to the base ends of both sides of the shaft beam link so that the fixed axle side can rotate in the vertical direction. A low-floor railcar bogie that features. A fixed axle is formed by a shaft beam that is concave when viewed from the front, and wheels are rotatably supported on both sides of the fixed axle.
A long shaft beam link member is extended integrally on one side of the fixed axles, and a short shaft beam link member is integrally extended forward or rearward on the other side,
The extension shaft beam link member is connected to the distal end of the short side shaft beam link member in a straight line, allowing bending in all directions under the intervention of an elastic body, etc., and the total length of the left and right link members is equal. The axial beam link of the “U” shape in plan view
With respect to the front and rear ends of both sides of the bogie frame integrally connected between the side beams with a concave horizontal beam when viewed from the front, both side base ends of the shaft beam link are pivotally connected so that the fixed axle side can be rotated in the vertical direction, respectively.
An electric motor is attached to the intermediate position in the longitudinal direction of the beam on both sides of the bogie frame, and a power transmission mechanism that can refract vertically from the electric motor at an intermediate position in the longitudinal direction is projected to at least one of the front and rear to transmit the same power. A configuration in which at least one of the front and rear wheels is driven via a mechanism and a reduction gear mechanism;
A suspension link that extends from a gear box that covers the periphery of the reduction gear mechanism toward the outside of the driven wheel, extends toward the carriage frame, and is suspended by pivotally connecting the upper end of the carriage frame. One end of the shaft beam member is pivotally connected to the lower end of the shaft, and the gear box is configured to be swingable in the vertical direction around the virtual rotation center position on the lower extension line of the suspension link,
A low-floor railway, characterized in that the virtual rotation center position, the pivot connection position of the shaft beam link base end with respect to the carriage frame, and the refractive center position of the power transmission mechanism coincide with each other. Vehicle trolley.   The long side shaft beam link member, the fixed axle, and the short side shaft beam link member are formed in a substantially J shape in plan view, and the entire shaft beam link including the extension shaft beam link member is substantially U shape in plan view. The bogie for a low-floor railway vehicle according to claim 1 or 2, wherein the bogie is formed. A pair of hypoid gears or a pair of bevel gears projecting the drive shaft from the electric motor to at least one of the front and rear and having a flexible joint at an intermediate position of the drive shaft and meshing perpendicularly to each other Through which the rotational force of the electric motor is converted by 90 ° and transmitted to the wheel to drive the wheel,
4. The low position according to claim 2, wherein the refractive center position of the flexible joint, the pivot connection position of the shaft beam link base end with respect to the carriage frame, and the virtual rotation center position coincide with each other. Floor type railcar bogie.

Images