Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B61—RAILWAYS
  • B61H—BRAKES OR OTHER RETARDING DEVICES SPECIALLY ADAPTED FOR RAIL VEHICLES; ARRANGEMENT OR DISPOSITION THEREOF IN RAIL VEHICLES
  • B61H9/00—Brakes characterised by or modified for their application to special railway systems or purposes
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B61—RAILWAYS
  • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
  • B61F7/00—Rail vehicles equipped for use on tracks of different width

Definitions

• the present invention relates to a variable-wheel-gauge bogie for rolling stock and a wheel gauge changing track arrangement and, more particularly, to a variable-wheel-gauge bogie capable of automatically adjusting its wheel gauge to a rail gauge of a track, and the wheel gauge changing track arrangement for changing the wheel gauge of the variable-wheel-gauge bogie.
• variable-wheel-gauge bogies for rolling stock intended for use on a track of a standard rail gauge of 1435 mm, such as tracks for the Shinkansen line, and on a track of a narrow rail gauge of 1067 mm, such as a track for the old line, and various wheel gauge changing track arrangements.
• a wheel gauge changing technique disclosed in, for example, JP-A No. 5-39036 employs a car lifting device, such as a pneumatic cylinder actuator, mounted on a railroad car and changes the wheel gauge of a bogie supporting the railroad car by lifting up the railroad car by the car lifting device and shifting the wheels by actuators after stopping the railroad car.
• a car lifting device such as a pneumatic cylinder actuator
• a tubular sliding shaft is mounted on an axle restrained from rotation, wheels are supported on bearings on a tubular sliding shaft and a stator of a drive motor is fixedly coupled with the tubular sliding shaft, and the sliding shaft is moved axially to move both the wheels and the drive motor for wheel gauge changing.
• Journal boxes, the axle and the sliding shaft are provided with through holes for receiving power-driven positioning-and-locking pins.
• the wheels are positioned and locked in place in a desired wheel gauge by fitting the positioning-and-locking pins in the corresponding through holes of the journal boxes, the axle and the sliding shaft, respectively, to unite the journal boxes, the axle and the sliding shaft fixedly. Since locked in place, the wheels are unable to move transversely so that a fixed wheel gauge is maintained while the variable wheel gate bogie is traveling.
• journal boxes supporting the axles of independent wheels are supported on a wheel frame by a parallel linkage.
• a car support base is installed along a gauge changing section of a track.
• the weight of the railroad car is born by the car support base to relieve the wheels of the weight of the railroad car, so that the links of the parallel linkage supporting the unloaded wheels are able to move freely and the wheel gauge can be adjusted to a rail gauge.
• the wheels are fixed in place by fitting pins in holes formed at the opposite ends of the parallel linkage.
• the weight of the railroad car is born by additional load bearing rails laid along the rails of the gauge changing section to relieve the wheels of the weight of the railroad car, so that the wheels are able to move freely transversely for automatic wheel gauge changing while the railroad car is traveling.
• the wheel gauge changing systems disclosed in JP-A Nos. 5-39036 and 6-40335 need to lift up all the railroad cars of a train simultaneously for wheel gauge changing operation by the car lifting devices while the railroad cars are stopped. Therefore the wheel gauge chang-ing operation takes much time and, when the train consists of a large number of railroad cars, many car lifting devices or a very long car support structure is necessary.
• the diameter of the through holes must be slightly larger than that of the corresponding positioning-and-locking pins to enable the positioning-and-locking pins to be smoothly fitted in the through holes when positioning and locking the wheels in place. Therefore, the wheel positioning-and-locking mechanism for locking the wheel in place unavoidably permits play and, consequently, each pair of wheels on an axle move individually transversely and the wheel gauge varies minutely and continually. Such a minute variation of the wheel gauge enhances the meandering motion of the railroad car during high-speed traveling, causing problems including spoiling riding comfort in the traveling performance of the railroad car.
• a very high impulsive transverse force acts on the bogie when the bogie travels along a curve or passes a railroad switch. Therefore, the play between the components of the wheel positioning-and-locking mechanism cause problems including distortion, breakage and abrasion of the structural components of the bogie that shortens the life of the bogie.
• journal box Since the journal box is not fixed and is elastically suspended from the frame of the bogie by an axle spring, a special means is necessary for aligning the through hole of the journal box with those of the axle and the sliding shaft.
• the Talgo automatic wheel gauge changing system that shifts each pair of independent wheels transversely together with the journal boxes is suitable for application to a single axle bogie
• the Talgo automatic wheel gate changing system has structural difficulties in applying the same to a two-axle bogie. It is very difficult to apply the Talgo automatic wheel gauge changing system to a bogie for narrow rail gauge because of dimensional restrictions thereon.
• FR-A-2383810 discloses a variable wheel gauge system for rolling stock, the rolling stock having a variable wheel gauge bogie comprising journal boxes suspended from side beams of a truck frame by elastic members, axles vertically movably supported on the journal boxes and axle sleeves axially slidably mounted on the axles for movement between a broad gauge and a narrow gauge position. Wheels are supported for rotation on bearings on the axle sleeves and on-sleeve locking members are formed on an outer circumference of the axle sleeves. On-box locking means are formed on the journal boxes, capable of engaging with the on-sleeve locking members to restrain the axle sleeves from axial movement when each of the axle sleeves is at its broad gauge or narrow gauge position and when the weight of the truck frame act thereon through the journal boxes.
• the document further discloses wheel gauge changing rails interconnected to rails of a broad gauge and those of a narrow gauge, and car support rails extended on an outer side of, and along said wheel gauge changing rails, the rails of the broad gauge and the rails of the narrow gauge, so as to come into engagement with the journal boxes to raise the journal boxes relative to the axle sleeves so that the locking means is disengaged.
• the document further discloses pairs of journal boxes suspended from side beams of a truck frame by elastic members, and provided with locking means in their upper walls respectively; car support units each formed on the lower surface of each journal box to support the body of a railroad car when changing the wheel gauge; axles vertically movably supported on the journal boxes with the opposite ends thereof contained in the journal boxes, respectively; pairs of axle sleeves axially slidably fitted on the axles, respectively, for movement between a broad gauge position and a narrow gauge position; pairs of wheels supported for rotation on the pairs of axle sleeves; pairs of locking blocks attached to the outer circumference of the pairs of axle sleeves, each having an upper surface for bearing the weight of the railroad car through the journal box and locking projections projected from the upper surface of each locking block to be engaged with the locking means of the journal boxes when the axle sleeve is at a position for the broad gauge of a narrow gauge.
• An embodiment of the present invention provides a variable-wheel-gauge bogie for rolling stock, capable of changing its wheel gauge while traveling and of functioning with high safety and reliability, and applicable to railroad cars for narrow gauges and those equipped with drive motors, and to provide a wheel gauge changing track arrangement for use in combination with the variable-wheel-gauge bogie.
• Another embodiment of the invention provides a variable-wheel-gauge bogie for rolling stock, having a wheel positioning-and-locking mechanism capable of locking wheels in place without permitting any play with high safety and reliability.
• a system for changing the gauge of a rolling stock bogie having, a pair of side beams for supporting wheel axles on a railroad via wheels, journal boxes provided under said side beams, respectively, to receive ends of said wheel axles, and axle sleeves rotably supporting said wheels, thereon and fitted on said wheel axles slidably along the wheel axles, respectively, comprising: first engagement means formed on an outer peripheral surface of each of said axle sleeves; second engagement means formed on an inside surface of each of said journal boxes and provided to selectively engage said first engagement means when said wheels are positioned to match one of different gauges; wheel gauge changing rails laid between two rails of different gauges and provided to allow said rolling stock bogie to roll thereon; and car support rails provided in parallel with said wheel gauge changing rails to separate the rolling stock bogie from said sleeves and said wheels in a vertical direction to disengage said second engagement means from said first engagement means while said rolling stock bogie rolls on said wheel gauge changing rails so as to change said gauge without stopping the rolling stock bogie;
• each axle is provided with circular grooves in its end portions, respectively
• each journal box has an extension fitted in the circular groove of the axle
• the fastening device has a wedge member held adjacent to the extension so as to be forced into the circular groove of the axle, and wedge biasing members for biasing the wedge member toward the circular groove, the wedge member presses the extension against the side surface of the annular groove by its wedging action when forced into the circular groove of the axle to fasten together the journal box and the axle.
• each car support rail has a wedge guide rail transversely projecting therefrom and capable of retracting the wedging member from the circular groove of the axle against the biasing force of the wedge biasing members to disengage the journal box from the axle.
• the wheel gauge changing track arrangement further comprises guide rails laid so as to extend on both sides of and along the wheel gauge changing rails and to come into contact with the side surfaces of the wheels, and biasing members for biasing the guide rails to bring the guide rails into contact with the side surfaces of the wheels.
• each journal box is provided with shims for thickness adjustment on its lower surface that comes into contact with the car support rail.
• variable-wheel gauge bogie of rolling stock for automatically changing its wheel gauge while travelling on wheel gauge changing rails interconnecting rails of a broad-gauge track of a broad rail gauge and rails of a narrow gauge track of a narrow rail gauge
• said variable-wheel-gauge bogie comprising: journal boxes suspended from side beams of a truck frame by elastic members, respectively; axles vertically movably supported on the journal boxes; an axle sleeve axially slidably fitted on each of the axles for movement between a position for the broad rail gauge and a position for the narrow rail gauge; wheels supported for rotation on the axle sleeves, respectively; drive motors for driving the wheels in rotation supported on the axle sleeves, respectively; on-sleeve locking members formed on the outer circumferences of the axle sleeves, respectively; and an on-box locking means formed on the journal boxes, for engaging with the on-sleeve locking members, respectively, to restrain the axle sleeves from the axial movement when each of the axle sleeves is
• variable-wheel-gauge bogie of rolling stock for automatically changing wheel gauge while a railroad car is travelling on wheel gauge changing rails interconnecting rails of a broad-gauge track of a broad gauge and rails of a narrow-gauge track of a narrow gauge
• said variable-wheel-gauge bogie comprising: pairs of journal boxes suspended from side beams of a truck frame by elastic members, and provided with locking means in their upper walls, respectively; car support units each formed on the lower surface of each journal box to support the body of a railroad car when changing the wheel gauge; axles vertically movably supported on the journal boxes with the opposite ends thereof contained in the journal boxes, respectively; pairs of axle sleeves axially slidably fitted on the axles, respectively, for movement between a position for the broad rail gauge and a position for the narrow rail gauge; pairs of wheels supported for rotation on the pairs of axle sleeves, respectively; pairs of locking blocks attached to the outer circumferences of the pairs of axle sleeves, respectively, and each having an upper
• variable-wheel-gauge bogie is provided with central stoppers each projecting from the middle portion of each axle to restrain the axle sleeve from moving beyond the position for the narrow rail gauge toward the middle of the axle, end stoppers projecting from the oppo- site end portions of each axle to restrain the axle sleeves from moving beyond the positions for the broad rail gauge toward the ends of the axle, sliding members projecting from both sides of each end stopper and each having a taper upper end, guide cavities formed in each journal boxes to guide the sliding members for vertical movement, respectively, and vibration isolating units each disposed in an upper portion of each guide cavity so as to be in elastic contact with the surface of the taper upper end of the sliding member.
• the vibration isolating unit for locking pro-jection comprises an outer ring fixedly fitted in the upper section of the locking hole, a rubber vibration isolator fixed to the inside surface of the outer ring, and an inner ring fixed to the inside surface of the rubber vibration isolator, and the inner ring is moved by the conical portion of the conical locking projection to deform the rubber vibration isolator when the conical locking projection is fitted in the locking hole.
• the vibration isolating unit for locking projection has a annular plate spring having a V-shaped section.
• the vibration isolating unit for locking projection comprises a wedge ring fitted in the upper section of the locking hole, a cover covering the upper open end of the upper section of the locking hole, and an elastic member disposed between the upper surface of the wedge ring and the cover to bias the wedge ring downward, the conical portion of the conical locking projection comes into engagement with the inner circumference of the wedge ring when the conical locking projection is fitted in the locking hole.
• the sliding members are outward extensions of the opposite side surfaces of the end stopper, and the guide cavities are sliding grooves formed in the opposite side walls of the journal box.
• the vibration isolating unit for sliding member comprises a box fitted in an opening formed in each side wall of the journal box, detachably attached to the sides wall and having a recess opening into the interior of the journal box, a rubber vibration isolator attached to the surface of the recess of the box, and a liner fixed to the rubber vibration isolator so as to be in contact with the taper upper end of the sliding member.
• the vibration isolating unit for sliding member has a plate spring having a V-shaped cross section and in elastic contact with the end surface of the taper upper end portion and the opposite side surfaces of the sliding member.
• the sliding members are pins projecting upward from brackets projecting from the opposite side surfaces of the end stopper, and the guide cavities are vertical through holes formed in the journal box.
• the vibration isolating unit for sliding member comprises an outer ring fixedly disposed in the upper portion of the guide cavity, a rubber vibration isolator fixed to the inside surface of the outer ring, and an inner ring fixed to the inside surface of the rubber vibration isolator, and the inner ring is moved by the taper upper end of the sliding member so as to deform the rubber vibration isolator when the sliding member is inserted in the guide cavity.
• the wheel gauge can be changed without stopping the railroad car while the railroad car is traveling, and the present invention is applicable to railroad cars for narrow gauges and railroad cars mounted with drive motors. Since the locking members on the journal boxes, for restraining the axle sleeves from axial movement engage with the locking members on the axle sleeves, respectively, when the weight of the railroad car acts thereon, the locking members are engaged securely so that the variable-wheel-gauge bogie for rolling stock functions with high safety and high reliability.
• journal boxes 4 are suspended from the side beams 1 of a truck frame by axle springs 2, i.e., elastic members.
• the axle springs 2 may be coil springs, pneumatic springs or rubber springs.
• the flat lower surfaces of the journal boxes 3 serving as sliding surfaces 3a are at the same level. Fixed axles 4 are supported on the journal boxes 3.
• a positioning projection 5 is formed on each axle 4 at the middle of the axle 4, and positioning circular grooves 6 are formed in each axle 4 at some distance from its opposite ends.
• Two axle sleeves 7 are put on each axle 4 so as to be axially movable on the axle 4.
• Each axle sleeve 7 is supported on the journal box 3 and restrained from rotation by a locking block 13.
• the axle 4 and the axle sleeve 7 are not restrained from rotation relative to each other.
• a wheel 9 is supported for rotation on a taper roller bearing 8 at a substantially middle portion of the axle sleeve 7.
• the wheel 9 is an elastic wheel formed of a composite material that will reduce the unsprung weight of the bogie and vibrational acceleration.
• a stator 10a included in a drive motor 10 is fixedly mounted on the axle sleeve 7 at a position on one side of the wheel 9 nearer to the middle of the axle 4.
• a rotor 10b included in the drive motor 10 has one end supported on a bearing 11 on the axle sleeve 7 and the other end fixed to a side surface of the wheel 9.
• a brake disk 12 is formed on the outer circumference of the rotor 10b.
• the tubular locking block 13 is mounted on a portion of the axle sleeve 7 near the end of the axle 4 and fixedly joined to the axle sleeve 7 by splines 14.
• the locking block 13 extends into the journal box 3, has sliding side walls 13a as shown in Fig. 4 and is able to move vertically relative to the journal box 3.
• the locking block 13 has a pair of upper inclined surfaces 13b, and two axially elongate locking projections 15A and 15B of the same shape are formed on each upper inclined surface 13b as shown in Fig. 5.
• the locking projections 15A and 15B has a trapezoidal longitudinal section.
• Locking groove 16 having a shape complementary to that of the locking projections 15A and 15B are formed in the inside surface of the journal box 3 facing the upper inclined surfaces 13b of the locking block 13.
• the positional relation between the locking projections 15A and 15b and the corresponding locking recess 16 is determined so as to meet the following conditions.
• the distance between the pair of wheels 9 on each axle 4 corresponds to the narrow rail gauge as shown in Fig. 2 when the locking projection 15A is fitted in the locking recess 16, and the distance between the pair of wheels 9 corresponds to the broad rail gauge as shown in Fig. 3 when the locking projection 15B is fitted in the locking recess 16 as shown in Fig. 5.
• the locking projections 15 and the locking recess 16 are locking part of the axle sleeve 7 and that of the journal box 3, respectively, may be formed in any suitable shape other than the trapezoidal shape, provided that the locking projections 15 and the locking recess 16 are able to restrain the axle sleeve 7 from axial movement when engaged.
• the locking block may be provided with one locking projection 15 and the journal box 3 may be provided with two locking recesses 16.
• the journal box 3 may be provided with a locking projection or two locking projections and the locking block 13 may be provided with two locking recesses or one locking recess.
• the journal box 3 has a sliding guide extension 17 having vertical guide legs.
• the guide legs extend vertically on the opposite sides of a reduced part of the axle 4 defined by the circular groove 6 formed in the end portion of the axle 4.
• the guide legs of the guide extension 17 receiving the reduced portion of the axle 4 therebetween guides the journal box 3 when the journal box 3 move vertically relative to the axle 4 and the axle sleeve 7.
• the guide extension 17 serves also as a stopper for limiting the outward axial movement of the axle sleeve 7.
• a bifurcate fastening member 18 is inserted in the circular groove 6 of the axle 4.
• the fastening member 18 has two wedging legs 18a and 18b.
• a pair of rods 19 are joined to the fastening member 18, and coil springs 20 are extended between the lower ends of the rods 19 and the journal box 3, respectively, to bias the rods 19 downward.
• the fastening member 18 is biased downward through the rods 19 by the coil springs 20 so that the wedging legs 18a are inserted in the circular groove 6.
• the working surfaces of the guide extension 17 or the fastening member 18 are longitudinally tapered.
• Figs. 7A and 7B showing part of a narrow track of a narrow gauge having narrow-track rails 21, part of a standard track of the standard rail gauge having standard-track rails 22, the narrow-track rails 21 and the standard-track rails 22 are interconnected by a wheel gauge changing track having wheel gauge changing rails 23.
• the rail gauge of the wheel gauge changing track having the wheel gauge changing rails 23 increases gradually from one end thereof joined to the narrow track having the narrow-track rails 21 toward the other end thereof joined to the standard track having the standard-track rails 22.
• Portions of the narrow-track rails 21 and the standard-track rails 22 in sloping sections L of a predetermined length continuous with the wheel gauge changing track are declined toward the joints of the narrow-track rails 21 and the wheel gauge changing rails 23, and those of the standard-track rails 22 and the wheel gauge changing rails 23, respectively, so that the joints are sunk by a predetermined height H from the level of the narrow track and the standard track.
• Guide rails 24 are laid on both sides of each wheel gauge changing rails 23 along the entire length of the wheel gauge changing rails 23 and portions of the narrow-track rails 21 and the standard-track rails 22 continuous with the wheel gauge changing rails 23.
• the opposite guide rails 24 are biased toward each other by springs 25 so that the guide rails 24 are pressed against the side surfaces of the wheels 4, respectively.
• a pair of car support rails 26 are laid on the outer side of two sets each of the rails 21, 22 and 23, respectively, so as to extend in a substantially horizontal plane at a predetermined height from the ground.
• the car support rails 26 are laid so as to extend right under the sliding surfaces 3a of the journal boxes 3 so that the sliding surfaces 3a of the journal boxes 3 come into sliding contact with the car support rails 26.
• fastening member raising rails 27 are supported on the car support rails 26 so as to extend on the outer side of the car support rails 26 and right under the rods 19 joined to the fastening members 18.
• Each fastening member raising rail 27 has a sloping section 1 corresponding to a section of the narrow-track rail 21 continuous with the sloping section L, and sloping up toward a horizontal section corresponding to the the sloping section L continuous with the narrow-track rail 21, the horizontal section of the wheel gauge changing rail 23 and the sloping section L continuous with the standard-track rail 22, and a sloping section 1 corresponding to a section of the standard-track rail 22 continuous with the other sloping section L, and sloping down from the horizontal section.
• variable-wheel-gauge bogie is in the geometry shown in Fig. 2 while the railroad car is traveling on the narrow-track rails 21 and the locking projections 15A are fitted in the locking recesses 16, respectively.
• the rotors 10b of the drive motors 10 rotate together with the wheels 9, respectively.
• Reactive torques corresponding to the driving torques of the wheels 9 are transmitted through the axle sleeves 7, the sliding side walls 13a of the locking blocks 13, the journal boxes 3 and the axle springs 2 to the side beams 1 of the truck frame to drive the railroad car for traveling.
• variable-wheel-gauge bogie When the variable-wheel-gauge bogie enters a section of the narrow-track rails 21 corresponding to the up sloping section 1 of the raising rails 27, the raising rails 27 raises the rods 19 against the force of the springs 20 to raise the fastening members 18 by a predetermined distance. Consequently, the wedging effects of the fastening members 18 are removed, whereby the journal boxes 3 are able to move vertically relative to the axles 4. Subsequently, the variable-wheel-gauge bogie enters the down sloping section L of the narrow-track rails 21 and starts traveling downward.
• the sliding surfaces 3a of the journal boxes 3 come into contact with the car support rails 26, and then the journal boxes 3 are kept in a substantially horizontal plane while the axles 4 and the axle sleeves 7 move downward relative to the journal boxes 3 according to the inclination of the down sloping section L. Consequently, the locking projections 15A come off the corresponding locking recesses 16 to allow the axle sleeves 7 to move axially.
• the axle sleeves 7 are allowed to move axially before the variable-wheel-gauge bogie reaches the terminal end of the down sloping section L at the latest.
• variable-wheel-gauge bogie starts traveling on the wheel gauge changing rails 23 of the wheel gauge changing track gradually widening toward the standard track. Then, the wheels 9 are guided by the guide rails 24 biased toward the wheels 9 by the springs 25 as the wheels roll on the wheel gauge changing rails 23, so that the wheels 9 are shifted gradually outward together with the associated axle sleeves 7 on the axles 4.
• the variable-wheel-gauge bogie arrives at the terminal end of the wheel gauge changing rails 23, the outer ends of the sleeves 7 come into contact with the extensions 17 of the corresponding journal boxes 3 as shown in Fig. 3, and the axle sleeves 7 are stopped.
• the distance between the pair of wheels 9 on each axle 4 is equal to the standard rail gauge, and the locking projections 15B are located opposite to the locking recesses 16, respectively. Since the truck frame of the variable-wheel-gauge bogie is supported through the journal boxes 3 on the car support rails 26 while the variable-wheel-gauge bogie is traveling on the wheel gauge changing rails 23 or on sections of the narrow-track rails 21 or the standard-track rails 22 near the ends of the wheel gauge changing rails 23, the wheels 9 and the axle sleeves 7 are lightly loaded, and hence the axle sleeves 7 are able to slide lightly according to the variation of the rail gauge of the wheel gauge changing track.
• variable-wheel-gauge bogie moves from the wheel gauge changing rails 23 to the standard-track rails 22.
• the axles 4 and the axle sleeves 7 move upward relative to the journal boxes 3, the locking projections 15B approach the corresponding locking recesses 16 of the journal boxes and, finally, the locking projections 15B are fitted in the corresponding locking recesses 16. Consequently, the axle sleeves 7 is locked in place and the wheels 9 are fixed at positions for the standard rail gauge.
• variable-wheel-gauge bogie travels in a section of the standard track corresponding to the down sloping section 1 of the guide rails 27, the fastening members 18 are lowered through the rods 19 by the springs 20, and press the guide extensions 17 against the axles 4 by their wedging effect to fasten the axle sleeves 7 firmly to the axles 4.
• the variable-wheel-gauge bogie is provided with the fastening members 18 for the following purposes.
• the locking projection 15B of each axle sleeve 7 is fitted in the locking recess 16 of the journal box 3 as the journal box 3 is lowered by the weight of the truck frame when the variable-wheel-gauge bogie travels on the standard-track rails 22 in the up sloping section L. Therefore, even if the variable-wheel-gauge bogie bounces, the locking projection 15B will not come off the locking recess 16 because a vertical acceleration is in the range of about 0.3g to 0.5g and far less than the gravitational acceleration of lg.
• axle springs 2 can be transversely slightly displaced due to their rigidity, there is the possibility that the wheels 9 move relative to the axle 4 and the components of the variable-wheel-gauge bogie chatters and are abraded if the play of the extensions 17 of the journal boxes 3 in the corresponding circular grooves 6 of the axles 4 is permitted. Therefore, the play of the extensions 17 in the corresponding circular grooves 6 is inhibited perfectly by the wedging action of the fastening members 18 to solve the aforesaid problems.
• the railroad car may be provided with a sensor for detecting the wheel gauge changing arrangement and supply of power to the drive motors 10 may be stopped upon the detection of the wheel gauge changing arrangement by the sensor.
• a stack of a plurality of height adjusting shims 50 are fastened to the sliding surface 3a of the journal box 3 with screws as shown in Figs. 2, 3, 4 and 6.
• the diameter of each wheel 9 decreases as the wheel 9 is abraded and the distance between the sliding surface 3a of each journal box 3 and the car support rail 26 decreases. Therefore, some of the shims 50 are removed according to the reduction of the diameter of the wheel 9 to compensate a reduction in the distance between the sliding surface 3a of the journal box 3 and the car support rail 26.
• the respective rails 21, 22 and 23 of the narrow-gauge track, the standard-gauge track and the wheel gauge changing track may be extended in a horizontal plane and sloping sections may be formed in the car support rails 26.
• the wheels 9 are guided by the guide rails 24 biased by the springs 25 so as to be in contact with the side surfaces of the wheels 9, the wheels 9 can be very smoothly shifted according to the variation of the rail gauge of the wheel gauge changing track for wheel gauge adjustment.
• variable-wheel-gauge bogie in a second embodiment of the present invention will be described hereinafter with reference to Figs. 8 to 24.
• the variable-wheel-gauge bogie in the second embodiment is similar in construction to the variable-wheel-gauge bogie in the first embodiment and hence only components and arrangements of the variable-wheel-gauge bogie different from those of the variable-wheel-gauge bogie in the first embodiment will be described.
• a tubular locking block 13 is fixedly united to on end of an axle sleeve 7 on the side of the end of an axle 4.
• male splines are formed in a portion of the axle sleeve 7, and female splines mating with the male splines are formed on the locking block 13 to inhibit the rotation of the axle sleeve 7 and the locking block 13 relative to each other. Since the locking block 13 is supported on the journal box 3 so that the locking block 13 is unable to rotate, which will be described later, the axle sleeve 7 is unable to rotate.
• the locking block 13 is fastened to the axle sleeve 7 with a nut 28 as shown in Fig. 8 so that the locking block 13 is unable to move axially relative to the axle sleeve 7.
• the locking block 13 is contained in the journal box 3. As shown in Fig. 11, the locking block 13 has a horizontal, load bearing upper surface 13a in contact with the upper wall of the journal box 3 to take the weight of a truck frame through the journal box 3, and sliding side surfaces 13b in contact with a sliding side guide surfaces formed in the journal box 3.
• a pair of conical locking projections 15A and 15B project from the upper surface 13a of the locking block 13.
• the conical locking projections 15A and 15B are spaced apart by a predetermined distance.
• a locking hole 32 and an escape hole 33 are formed in the upper wall of the journal box 3.
• the distance along the axis of an axle 4 between the locking hole 32 and the escape hole 33, i.e., the center distance, is equal to the center distance between the conical locking projections 15A and 15B.
• the axle sleeve 7 is unable to move axially.
• the positional relation between the conical locking projections 15A and 15B and the locking hole 32 is determined so as to meet the following conditions.
• the wheel 9 is at a position indicated by continuous lines in Fig.
• each of the conical locking projections 15 (the reference numeral 15 will be used to indicate both the conical locking projections 15A and 15B inclusively) has a cylindrical lower portion 15a and a conical head portion 15b.
• the cylindrical lower portion 15a has a height h and a uniform diameter through the height h.
• the conical head portion 15b is tapered upward.
• the locking hole 32 of the journal box 3 has a lower section 32a of a height h and an upper section 32b.
• the diameter of the lower section 32a is slightly greater than that of the cylindrical lower portion 15a, and the diameter of the upper section 32b is far greater than that of the lower section 32a.
• a vibration isolating unit 34 for the conical locking projection 15 is fitted in the upper section 32b of the locking hole 32.
• the vibration isolating unit 34 comprises an outer ring 35 detachably fixed to the circumference of the upper section 32b, an annular rubber vibration isolator 35 fixed to the inner circumference of the outer ring 35, and an inner ring 36 fixed to the inner circumference of the rubber vibration isolator 37.
• the outer ring 35 is provided with an inner flange 35a serving as a retainer for retaining the inner ring 36 or the rubber vibration isolator 37, and an outer flange 35b.
• the outer flange 35b is fastened detachably to the journal box 3 with screws 39.
• the vibration isolating unit 34 in a natural state, when none of the conical locking projections 15 is fitted in the locking hole 32, a predetermined clearance is formed between the inner ring 36 or the rubber vibration isolator 37, and the inner flange 35a as shown in Fig. 13.
• an end stopper 40 projects from each end of an axle 4, and sliding members 41 extend perpendicularly to the axis of the axle 4 from the opposite sides of the end stopper 40.
• Each sliding member 41 has a taper upper end portion 41a.
• An opening 42 (Fig. 16) is formed in a side wall 3a of a journal box 3, and a vibration isolating unit 43 for the sliding member 41 is fitted in the opening 42.
• the vibration isolating unit 43 comprises a box 44 detachably fitted in the opening 42, a rubber vibration isolator 45 and a liner 46 fixed to the rubber vibration isolator 45.
• the box 44 is provided with a recess opening into the journal box 3, and the rubber vibration isolator 45 is fastened to three surfaces defining the recess of the box 44.
• a sliding groove 47 is formed in the side wall 3a of the journal box 3 so as to extend into the recess of the box 44.
• the upper end of the sliding groove 47 opens into the recess of the box 44.
• the sliding member 41 is fitted slidably in the sliding groove 47 so that the taper upper end portion 41a of the sliding member 41 is in contact with the liner 46 of the vibration isolating unit 43.
• the upper surface 42a and the lower surface 42b of the opening 42 serve as an upper stopping surface and a lower stopping surface for the vibration isolating unit 43.
• variable-wheel-gauge bogie is in the geometry shown in Figs. 8, 12, 14 and 15 while the railroad car is traveling on the narrow-track rails 21 and the conical locking projections 15A are fitted in the locking holes 16, respectively.
• Drive motors not shown, drive the wheels 9 to drive the railroad car for traveling.
• the sliding surfaces 3a of the journal boxes 3 come into contact with the car support rails 26, and then the journal boxes 3 are kept in a substantially horizontal plane by the car support rails 26 while the axles 4 and the axle sleeves 7 move downward relative to the journal boxes 3 according to the inclination of the down sloping section L. Consequently, the sliding members 41 shown in Figs. 14 to 16 move downward along the sliding grooves 47, and the conical locking projections 15A shown in Figs. 8 and 12 come off the corresponding locking holes 32 to allow the axle sleeves 7 to move axially.
• the axle sleeves 7 are allowed to move axially before the variable-wheel-gauge bogie reaches the terminal end of the down sloping section L at the latest. Then, the variable-wheel-gauge bogie starts traveling on the wheel gauge changing rails 23 of the wheel gauge changing track gradually widening toward the standard track. Then, the wheels 9 are guided by the guide rails 24 biased toward the wheels 9 by the springs 25 as the wheels roll on the wheel gauge changing rails 23, so that the wheels 9 are shifted gradually outward together with the associated axle sleeves 7 on the axles 4.
• the variable-wheel-gauge bogie arrives at the terminal end of the wheel gauge chang-ing rails 23, the outer ends of the sleeves 7 come into contact with the corresponding stoppers 40, and the axle sleeves 7 are stopped.
• the distance between the pair of wheels 9 on each axle 4 is equal to the standard rail gauge, and the locking projections 15B are located opposite to the locking holes 32, respectively. Since the truck frame of the variable-wheel-gauge bogie is supported through the journal boxes 3 on the car support rails 26 while the variable-wheel-gauge bogie is traveling on the wheel gauge changing rails 23 or on sections of the narrow-track rails 21 or the standard track rails 22 near the ends of the wheel gauge changing rails 23, the wheels 9 and the axle sleeves 7 are lightly loaded, and hence the axle sleeves 7 are able to slide lightly along the axles 4 according to the variation of the rail gauge of the wheel gauge changing track.
• variable-wheel-gauge bogie moves from the wheel gauge changing rails 23 to the standard-track rails 22.
• the axles 4 and the axle sleeves 7 move upward relative to the journal boxes 3, the sliding members 41 shown in Figs. 14 to 16 slide upward along the sliding grooves 47, the conical head portions 15b of the conical locking projections 15B enter the vibration isolating units 43, respectively, the conical locking projections 15B are fitted in the locking holes 32 of the journal boxes 3, respectively, and the conical locking projections 15A enter the escape holes 33.
• the mode of engagement of the taper upper end portion 41a of the sliding member 41 with the vibration isolating unit 43 is similar to that of engagement of the conical head portion 15b of the conical locking projection 15B with the vibration isolating unit 34; the taper upper end portion 41a pushes the liner 46 up as the same moves up to compress the rubber vibration isolator 45.
• the conical locking projection 15B has the conical head portion 15b, the conical locking projection 15B can be surely fitted in the locking hole 32 even if the conical locking projection 15B and the locking hole 32 are dislocated slightly relative to each other.
• the axle sleeve 7 is restrained from axial sliding movement and the distance between the pair of wheels 9 on each axle 4 is fixed at the standard gauge. Since the conical locking projection 15B is fitted in the locking hole 32 by the weigh of the truck frame, the conical locking projection 15B will never come off the locking hole 32 accidentally. Since dynamic shocks due to the play of the conical locking projection 15B in the locking hole 32 during traveling are absorbed by the rubber vibration isolator 37, the abrasion of the component parts can be effectively prevented and high traveling stability can be secured.
• the rubber vibration isolator 37 is deformed elastically beforehand when the conical locking projection 15B is fitted in the locking hole 32, the dynamic shocks that occur during travel due to the play can be very effectively absorbed, and the relative movement of the journal box 3 and the axle sleeve 7 can be effectively suppressed.
• the cylindrical lower portion 15a of the conical locking projection 15B is received in the lower section 32a of the locking hole 32 having a diameter substantially equal to that of the cylindrical lower portion 15a when the conical locking projection 15B is fitted in the locking hole 32, the area of contact between the surface of the cylindrical lower portion 15a and the side surface of the lower section 32a is comparatively large, which is advantageous in strength.
• journal box 3 and the axle 4 are maintained in a fixed positional relation and hence the positional relation between the locking hole 32 of the journal box 3 and the axle 4 is fixed. Accordingly, the conical locking projection 15 fixed to the axle sleeve 7 can be surely fitted in the locking hole 32.
• the respective rails 21, 22 and 23 of the narrow-gauge track, the standard-gauge track and the wheel gauge changing track may be extended in a horizontal plane and sloping sections may be formed in the car support rails 26.
• the wheels 9 are guided by the guide rails 24 biased by the springs 25 so as to be in contact with the side surfaces of the wheels 9, the wheels 9 can be very smoothly shifted according to the variation of the rail gauge of the wheel gauge changing track for wheel gauge adjustment.
• Fig. 18 shows vibration isolating unit 34 for conical locking projection, in a modification.
• the vibration isolating unit 34 shown in Fig. 18 has an annular plate spring 51 having a V-shaped section and set along the circumference of the locking hole 32.
• the plate spring 51 has a flange 51a detachably fastened to the journal box 3 with screws 52.
• Longitudinal slits 53 are formed in the annular plate spring 51, and a recess 54 is formed in the circumference of the locking hole 32 to allow the elastic deformation of the annular plate spring 51.
• the annular plate spring 51 similarly to the rubber vibration isolator 37 shown in Fig. 12, is elastically deformed by the conical locking projection 15 and applies its resilience to the conical locking projection 15.
• the vibration isolating unit 34 employing the annular plate spring 51 is simpler in construction than the vibration isolating unit 34 shown in Fig. 12, can be easily fabricated and assembled, and is superior in durability to the vibration isolating unit 34 shown in Fig. 12.
• Fig. 19 shows a vibration isolating unit 34 for conical locking projection, in another modification.
• the vibration isolating unit shown in Fig. 19 comprises a wedge ring 57 fixedly fitted in the upper section of the locking hole 32, a cover 55 detachably fastened to the journal box 3 with screws 56 so as to cover the upper open end of the upper section of the locking hole 32, and a Belleville spring 58 disposed between the upper surface of the wedge ring 57 and the cover 55 to bias the wedge ring 57 downward. Since the Belleville spring 58 is a means simply for biasing the wedge ring 57 downward, the same may be substituted by an elastic rubber ring.
• the conical portion of the conical locking projection 15 comes into engagement with the inner circumference of the wedge ring 57 when the conical locking projection 15 is fitted in the locking hole, and the wedge ring 57 biased downward by the Belleville spring 58 comes into close contact with the conical locking projection 15 by its own wedging action.
• the conical locking projection 15 can be held in the locking hole 32 substantially without any play.
• the wedge ring 57 is provided with a slit 59 as shown in Fig. 20 in order that the wedge ring 57 can be elastically distorted and easily fitted in the locking hole 32.
• Figs. 21 and 22 show vibration isolating unit 43 for sliding member, in a modification.
• This vibration isolating unit 43 comprises a cover 61 detachably attached to the side surface of the journal box 3 so as to cover an opening 60 formed in the side wall of the journal box 3, and a U-shaped spring plate 62 having a V-shaped cross section as shown in Fig. 22 and fitted in the opening 60. A recess 63 similar to the recess 54 (Fig. 18) is formed in the opening 60.
• the operation of the vibration isolating unit 43 for sliding member, employing the plate spring 62 is substantially the same as that of the vibration isolating unit 34 for conical locking projection.
• Figs. 23 and 24 show modifications of the sliding member 41 and the guide cavity.
• Brackets 65 projects from the opposite ends of the end stopper 40, respectively, a sliding pin 66 is set in an upright position on each bracket 65.
• the upper end portion of the sliding pin 66 is tapered in a conical shape.
• Guiding through holes 67 are formed in the journal box 3 to guide the sliding pins 66 for vertical movement.
• a vibration isolating unit 68 for sliding member is disposed in an upper portion of the through hole 67.
• the vibration isolating unit 68 is entirely the same in construction as the vibration isolating unit 43 for conical locking projection, shown in Fig. 12; the vibration isolating unit 68 comprises an outer ring, a rubber vibration isolator and an inner ring.
• the vibration isolating unit 68 for sliding member may employ a plate spring having a V-shaped cross section similar to the plate spring 51 shown in Fig. 18.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Handcart (AREA)
• Train Traffic Observation, Control, And Security (AREA)
• Platform Screen Doors And Railroad Systems (AREA)
• Vibration Prevention Devices (AREA)
• Vehicle Body Suspensions (AREA)

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• 1996
  • 1996-06-04 KR KR1019960019726A patent/KR100221715B1/ko not_active IP Right Cessation
  • 1996-06-04 CA CA 2178177 patent/CA2178177C/en not_active Expired - Fee Related
  • 1996-06-05 DE DE1996607518 patent/DE69607518T2/de not_active Expired - Fee Related
  • 1996-06-05 RU RU96111017/28A patent/RU2127684C1/ru not_active IP Right Cessation
  • 1996-06-05 AU AU54730/96A patent/AU719847B2/en not_active Ceased
  • 1996-06-05 ES ES96304135T patent/ES2145384T3/es not_active Expired - Lifetime
  • 1996-06-05 EP EP96304135A patent/EP0747278B1/en not_active Expired - Lifetime
  • 1996-06-06 CN CN96110093A patent/CN1071221C/zh not_active Expired - Fee Related
  • 1996-09-03 TW TW085110745A patent/TW355170B/zh active

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