EP2783939A1 - Drehgestell für hochgeschwindigkeitsschienenfahrzeuge - Google Patents

Drehgestell für hochgeschwindigkeitsschienenfahrzeuge Download PDF

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Publication number
EP2783939A1
EP2783939A1 EP12716173.5A EP12716173A EP2783939A1 EP 2783939 A1 EP2783939 A1 EP 2783939A1 EP 12716173 A EP12716173 A EP 12716173A EP 2783939 A1 EP2783939 A1 EP 2783939A1
Authority
EP
European Patent Office
Prior art keywords
bogie
axle box
spring
primary
elastic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12716173.5A
Other languages
English (en)
French (fr)
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EP2783939B1 (de
EP2783939A4 (de
Inventor
Yinhua LIU
Jingang Wang
Pengjun ZHAI
Wenpeng YANG
Mingshang LIU
Xiaowei Li
Wensui BAI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
CRRC Shandong Co Ltd
Original Assignee
Jinan Railway Vehicles Equipment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201110438669.5A external-priority patent/CN102490754B/zh
Priority claimed from CN201110437255.0A external-priority patent/CN102490753B/zh
Priority claimed from CN201110440779.5A external-priority patent/CN102490755B/zh
Priority claimed from CN2011104387950A external-priority patent/CN102490745A/zh
Priority claimed from CN2011104407225A external-priority patent/CN102490752A/zh
Application filed by Jinan Railway Vehicles Equipment Co Ltd filed Critical Jinan Railway Vehicles Equipment Co Ltd
Publication of EP2783939A1 publication Critical patent/EP2783939A1/de
Publication of EP2783939A4 publication Critical patent/EP2783939A4/de
Application granted granted Critical
Publication of EP2783939B1 publication Critical patent/EP2783939B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • B61F3/00—Types of bogies
    • B61F3/02—Types of bogies with more than one axle
    • 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
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/04—Bolster supports or mountings
    • B61F5/10—Bolster supports or mountings incorporating fluid springs
    • 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
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/22—Guiding of the vehicle underframes with respect to the bogies
    • B61F5/24—Means for damping or minimising the canting, skewing, pitching, or plunging movements of the underframes
    • 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
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/26—Mounting or securing axle-boxes in vehicle or bogie underframes
    • B61F5/30—Axle-boxes mounted for movement under spring control in vehicle or bogie underframes
    • B61F5/301—Axle-boxes mounted for movement under spring control in vehicle or bogie underframes incorporating metal springs
    • 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
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/26—Mounting or securing axle-boxes in vehicle or bogie underframes
    • B61F5/30—Axle-boxes mounted for movement under spring control in vehicle or bogie underframes
    • B61F5/305—Axle-boxes mounted for movement under spring control in vehicle or bogie underframes incorporating rubber springs
    • 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
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/50—Other details
    • B61F5/52—Bogie frames

Definitions

  • the present invention relates to bogie technology, and more particularly to a bogie for high-speed railway vehicles.
  • the bogie for railway vehicles is generally classified into three-piece type bogie and frame type bogie.
  • the three-piece type bogie has shortcomings such as smaller diamond resistant rigidity, bigger unsprung mass and inability of installing disc brakes as well as the operating speed not exceeding 120km/h; while, the frame type bogie has advantages such as higher diamond resistant rigidity and smaller unsprung mass, so the dynamic performance of the frame type bogie is obviously superior to the three-piece type bogie.
  • the existing frame type bogie includes wheelset, frame, bolster and suspension device, wherein the frame consists of two side beams and two cross beams; the bolster is set transversely on the side beams; a center plate is set on an upper middle part of the bolster, and constant contact elastic side bearings which can carry vertical load of carbody and transfer the longitudinal force, are set on both sides of the upper part of the bolster.
  • the suspension device which is metal liquid rubber composite spring is mounted between the frame and wheelset, and it is located by axle box.
  • the moment of rotational resistance between the bogie and the carbody is provided by the constant contact elastic side bearings when the car is empty, and provided by the center plate and constant contact elastic side bearings when the car is loaded.
  • it's impossible to acquire a proper moment of rotational resistance nor guarantee the linear running stability and curve negotiation performance of railway vehicles during running at high speeds.
  • the poorer linear running stability and curve negotiation performance has restricted the improvement of the critical speed of the railway vehicles.
  • the present invention provides a bogie for high-speed railway vehicles, and particularly a bogie for high-speed railway wagon for solving the technical defects of the prior art, for example, the poorer linear running stability and curve negotiation performance of railway vehicles, particularly the wagons, during running at high speeds.
  • a bogie for high-speed railway vehicles comprising a wheelset, a frame, a primary suspension system and a secondary suspension system;
  • the frame comprises side beams and an intermediate crossbeam, a middle part of each of the side beams is a concave portion, and both ends of the intermediate crossbeam are separately connected with the concave portions of the side beams;
  • the primary suspension system comprises primary axle box suspension devices, one end of each of the primary axle box suspension devices is connected with a wheel axle of the wheelset, and the other end is supported at one end of one of the side beams;
  • the secondary suspension system comprises at least two spring sets, which are arranged at interval on the intermediate crossbeam and located between the side beams, and upper parts of the spring sets are connected with a carbody.
  • the secondary suspension system further comprises secondary vertical dampers, secondary transverse dampers and yaw dampers;
  • each of the secondary vertical dampers is connected with the frame, and the other end is connected with the carbody; one end of each of the secondary transverse dampers is connected with the frame, and the other end is connected with the carbody; and one end of each of the yaw dampers is connected with an outer side of the side beam, and the other end is connected with the carbody.
  • the spring sets are rubber spring sets; outer sides of the spring sets are provided with secondary transverse stoppers and secondary vertical stoppers ; and the secondary vertical dampers and yaw dampers are set at outer sides of the respective secondary vertical stoppers.
  • the primary suspension system further comprises primary vertical dampers; one end of each of the primary vertical dampers is connected with one of the primary axle box suspension devices, and the other end is connected with one of the side beams.
  • the primary axle box suspension device comprises an axle box positioning rotary arm and a primary suspension spring, and a lower end of the axle box positioning rotary arm is connected with the wheel axle; and the primary suspension spring is mounted onto an upper end of the axle box positioning rotary arm, and both ends of each of the side beams are separately provided with a spring mounting hole, into which the primary suspension spring is mounted.
  • the axle box positioning rotary arm is of a split structure that comprises an upper axle box, a lower axle box and a rotary arm elastic joint coupled together; one end of the upper axle box is of a semi-bushing structure, and the other end is provided with a rotary arm elastic joint mounting hole; the lower axle box is of a semi-bushing structure; and the upper and lower axle boxes are butt-jointed to form a bushing for installation of the wheel axle; both ends of the rotary arm elastic joint are of a semicolumn structure, which is mated with a mounting seat on the side beam in half arc pattern; and the primary suspension spring comprises a spring mounting brace, an elastic stopping column, an inner ring spring and an outer ring spring; the elastic stopping column is mounted vertically onto the spring mounting brace, which is then mounted onto an upper end surface of the upper axle box; the inner ring spring is sleeved onto the elastic stopping column, and the outer ring spring is sleeved onto the inner ring spring.
  • the rotary arm elastic joint is a rotary arm rubber joint.
  • the above bogie further comprises an axle temperature detector for detecting the temperature of the wheel axle, wherein the axle temperature detector is set on the lower axle box.
  • the above bogie further comprises a traction rod device, wherein one end of the traction rod device is connected with the intermediate crossbeam, the other end is connected with the carbody, and the traction rod device is configured to provide tractive force for the intermediate crossbeam.
  • the traction rod device comprises a traction rod, elastic joints and a fixed seat; both ends of the traction rod are opened with mounting holes, and the elastic joints are mounted into the mounting holes; both ends of each of the elastic joints are of a semicolumn structure; the fixed seat is opened with semicolumn holes; the semicolumn structure at both ends of one of the elastic joints is mated with the semicolumn holes on the fixed seat, and the semicolumn structure at both ends of the other elastic joint is configured to mate with semicolumn mounting holes of the carbody.
  • the elastic joints is rubber joints.
  • the frame further comprises two auxiliary crossbeams, both ends of which are separately connected with the side beams and distributed evenly at both sides of the intermediate crossbeam;
  • the bogie further comprises a braking device, which comprises a brake disc, a brake cylinder, a brake pad and a clamp, the brake pad is mounted onto the clamp, the clamp is mounted onto the auxiliary crossbeam, and the brake disc is fixed on the wheel axle; frictional force generated between the brake pad and the brake disc is configured to provide braking force for the high-speed railway vehicles.
  • the above bogie further comprises at least one elastic safety chains; one end of each of the elastic safety chains is connected with the intermediate crossbeam, and the other end is connected with the carbody.
  • the wheel axle is a hollow or solid axle; optionally, both ends of the wheel axle are provided with an antiskid device.
  • the above bogie further comprises at least one weighing valves, wherein one end of each weighing valve is connected with the primary axle box suspension device, and the other end is connected with one of the side beams and located at outer side of the side beam; optionally, the primary vertical dampers, secondary transverse dampers and secondary vertical dampers are oil dampers.
  • the present invention further provides a secondary suspension system of a bogie for high-speed railway vehicles, comprising at least two spring sets; wherein a lower end of each of the spring sets is connected with the bogie, and an upper end there of is connected with a carbody.
  • the present invention also provides a frame of a bogie for high-speed railway vehicles, comprising side beams and intermediate crossbeam, wherein a middle part of each of the side beams is a concave portion, and both ends of the intermediate crossbeam are separately connected with the concave portions of the side beams.
  • the present invention also provides a primary suspension system of a bogie for high-speed railway vehicles, comprising an axle box positioning rotary arm and a primary suspension spring, wherein a lower end of the axle box positioning rotary arm is connected with a wheel axle, the primary suspension spring is mounted onto an upper end of the axle box positioning rotary arm, and the primary suspension spring is mounted into spring mounting holes at both ends of a side beam of the bogie.
  • the axle box positioning rotary arm is of a split structure that comprises an upper axle box, a lower axle box and a rotary arm elastic joint coupled together; one end of the upper axle box is of a semi-bushing structure, and the other end is provided with a rotary arm elastic joint mounting hole; the lower axle box is of a semi-bushing structure; the upper and lower axle boxes are butt-jointed to form a bushing for installation of the wheel axle; both ends of each of the rotary arm elastic joint are of a semicolumn structure, the semicolumn structure of the rotary arm elastic joint is mated with a mounting seat on the side beam of the bogie in half arc pattern; the primary suspension spring comprises a spring mounting brace, an elastic stopping column, an inner ring spring and an outer ring spring; the elastic stopping column is mounted vertically onto the spring mounting brace, which is then mounted onto an upper end surface of the upper axle box; the inner ring spring is sleeved onto the elastic stopping column, and the outer
  • the present invention also provides a traction rod device of a bogie for high-speed railway vehicles, comprising a traction rod, elastic joints and a fixed seat; both ends of the traction rod are opened with mounting holes, and the elastic joints are mounted into the mounting holes; both ends of each of the elastic joints are of a semicolumn structure; the fixed seat is opened with semicolumn holes; the semicolumn structure at both ends of one of the elastic joints is mated with the semicolumn holes on the fixed seat, and the semicolumn structure at both ends of the other elastic joint is configured to mate with semicolumn mounting holes of the carbody.
  • the spring sets of the secondary suspension system are set between the side beams to bear the vertical load of the carbody and also provide a proper moment of rotational resistance between the frame and the carbody, thus increasing the linear running stability, curve negotiation performance and critical speed of the railway vehicles.
  • FIG. 1 is a structural view of a bogie for high-speed railway vehicles provided in a preferred embodiment of the present invention
  • FIG. 2 is a structural view of a frame of the bogie for high-speed railway vehicles shown in FIG. 1 .
  • the primary suspension system 3 is located between the frame 2 and wheelset 1 and the secondary suspension system 4 is located between the frame 2 and the carbody.
  • the wheelset 1 comprises wheels 11 and wheel axle 12 connected with the wheels 11.
  • the frame 2 comprises two side beams 21 and one intermediate crossbeam 22.
  • a middle part of each side beam 21 has a concave portion 211 and both ends of the intermediate crossbeam 22 are connected with the concave portions 211 of the side beams 21, respectively.
  • the intermediate crossbeam 22 and the side beams 21 can be connected by means of plugging fit; specifically, an upper cover plate is mounted onto the upper end surface of the concave portion 211 of the side beam 21; a lower cover plate is mounted onto the lower end surface of the concave portion 211; the upper and lower cover plates run parallel and protrude out toward the inner side of the side beam 21.
  • the frame 2 can be assembled by means of the above plugging fit to enhance its structural strength, or it can also be connected by other known means.
  • the intermediate crossbeam 22 and side beams 21 are formed integrally.
  • the primary suspension system 3 comprises a primary axle box suspension device 31; one end of the primary axle box suspension device 31 is connected with the wheel axle 12 of the wheelset 1, and the other end supports on one end of the side beam 21.
  • the spring of the primary axle box suspension device 31 can be a metal spring or metal liquid rubber composite spring.
  • One primary axle box suspension device 31 can be provided for each wheel.
  • the secondary suspension system 4 comprises at least two spring sets 41, which are arranged at intervals on the intermediate crossbeam 22 and located between the side beams 21.
  • the transverse spacing between two spring sets 41 is 500-700mm, and the upper part of the spring set 41 is configured to connect with the carbody.
  • Two mounting seats for the spring sets 41 can be arranged on the intermediate crossbeam 22.
  • These two spring sets 41 can be made of rubber springs or other types of springs, e.g., metal or air springs. Two bulges are set on the upper part of each of the spring sets 41 for facilitating connection with the carbody.
  • the spring sets 41 can bear a vertical load of the carbody and also provide a proper moment of rotational resistance between the frame 2 and the carbody.
  • the spring sets 41 of the secondary suspension system 4 are mounted between two side beams 21 to bear the vertical load of the carbody and provide the proper moment of rotational resistance between the frame 2 and carbody, thus increasing the linear running stability and curve negotiation performance of railway vehicles, and thus critical speed of the railway vehicles.
  • the secondary suspension system 4 also can comprise secondary vertical damper 42, secondary transverse damper 43 and yaw damper 44.
  • One end of each of the secondary vertical dampers 42 is connected with the frame 2, and the other end is connected with the carbody.
  • One end of each of the secondary transverse dampers 43 is connected with the frame 2, and the other end is connected with the carbody.
  • One end of each of the yaw dampers 44 is connected with an outer side of the side beam 21, and the other end is connected with the carbody.
  • the secondary vertical damper 42 can be a hydraulic damper comprising an oil cylinder and a piston rod. Hydraulic damping force can be formed by stretching and compressing the piston rod, so as to realize a satisfactory vibration damping effect and flexible damping effect.
  • a mounting seat for the secondary vertical damper 42 can be set on each side beam 21. The lower end of the secondary vertical damper 42 is connected with the mounting seat for the secondary vertical damper, and the upper end is connected with the carbody.
  • the secondary vertical dampers 42 can be separately set at outer sides of two side beams 21 and provide a lateral rolling damping for the carbody to limit the maximum lateral rolling displacement of the carbody and improve the lateral rolling stability of vehicles.
  • the secondary transverse dampers 43 and yaw dampers 44 can also be hydraulic dampers.
  • Two secondary transverse dampers 43 can be provided and separately set at inner sides of two side beams 21. One end of each of the secondary transverse dampers 43 is connected with a mounting seat at inner side of the side beam 21, and the other end is connected with the carbody.
  • the secondary transverse dampers 43 can provide the transverse vibration damping for the railway vehicles in high-speed running, and further improve the linear running stability of the railway vehicles.
  • the yaw dampers 44 are mounted at outer sides of the side beams 21 substantially along a longitudinal and horizontal direction, thus avoiding the occurrence of hunting instability at high-speed and improving the running stability of railway vehicles.
  • the bogie for high-speed railway vehicles according to the above technical solution can adopt one or more of the secondary vertical damper 42, the secondary transverse damper 43 and the yaw damper 44.
  • secondary transverse stoppers 45 and secondary vertical stoppers 46 can be further set at outer sides of the respective spring sets 41, specifically at the middle parts on the upper end surfaces of the concave portions 211 of the side beams 21.
  • the secondary vertical dampers 42 and yaw dampers 44 can be set at outer sides of the respective secondary vertical stoppers 46.
  • the secondary transverse stoppers 45 can limit the maximum transverse displacement of the carbody in relation to the bogie, and prevent the damage from excessive transverse shear deformation generated by the spring sets 41.
  • the secondary vertical stoppers 46 can limit the maximum lateral rolling displacement of the carbody, and prevent rollover of the railway vehicles arising from excessive lateral rolling displacement during curved running. In the event of failure of the spring sets 41, the secondary vertical stoppers 46 can bear the vertical load of the carbody.
  • the primary suspension system 3 also comprises primary vertical dampers 32.
  • One end of each of the primary vertical dampers 32 is connected with the primary axle box suspension device 31, and the other end is connected with the side beam 21.
  • the primary vertical dampers 32 can also be a hydraulic damper, and four primary vertical dampers 32 can be mounted, wherein each of the primary vertical dampers 32 is mounted onto one primary axle box suspension device 31.
  • a lower end of the primary vertical damper 32 is connected with a mounting seat on the primary axle box suspension device 31, and an upper end is connected with a mounting seat on the end surface of the side beam 21.
  • the primary vertical dampers 32 can provide vertical vibration damping between the wheelset 1 and frame 2, thus improving the running stability of railway vehicles.
  • FIG. 3 is a structural view of a primary axle box suspension device provided in a second embodiment of the present invention
  • FIG. 4 is a perspective view of the primary axle box suspension device shown in FIG. 3
  • FIG. 5 is a perspective view of an upper axle box shown in FIG. 3
  • FIG. 6 is a perspective view of a lower axle box shown in FIG. 3
  • FIG. 7 is a perspective view of a rotary arm elastic joint shown in FIG. 3 .
  • a primary axle box suspension device 31 of the present embodiment comprises an axle box positioning rotary arm 311 and a primary suspension spring 312.
  • a lower end of the axle box positioning rotary arm 311 is connected with the wheel axle 12.
  • the primary suspension spring 312 is mounted onto an upper end of the axle box positioning rotary arm 311, and both ends of the side beam 21 are provided separately with a spring mounting hole, into which the primary suspension spring 312 is mounted.
  • axle box positioning rotary arm 311 is of a split structure that comprises an upper axle box 3111, a lower axle box 3112 and a rotary arm elastic joint 3113 coupled together.
  • One end of the upper axle box 3111 is of a semi-bushing structure, and the other end is provided with a rotary arm elastic joint mounting hole 3114.
  • the lower axle box 3112 is of a semi-bushing structure, and the upper axle box 3111 and the lower axle box 3112 are butt-jointed to form a bushing 3115.
  • a bearing can be mounted onto the wheel axle 12, and the bushing 3115 is sleeved onto the bearing, realizing the connection of the axle box positioning rotary arm 311 and the wheel axle 12.
  • the axle box positioning rotary arm 311 is of the split structure composed of the upper axle box 3111 and the lower axle box 3112, the wheelset 1 can be easily replaced during repair and maintenance.
  • Both ends of the rotary arm elastic joint 3113 are of a semicolumn structure that may adopt rubber joint for the rotary arm.
  • the semicolumn structure of the rotary arm elastic joint 3113 is mated with a mounting seat on the side beam 21 in half arc pattern, so that the rotary arm elastic joint 3113 can withstand a higher longitudinal load, and abnormal abrasion between the rotary arm elastic joint 3113 and the mounting seat of the side beam 21 can also be avoided to increase the service life and reliability of the rotary arm elastic joint 3113.
  • the primary suspension spring 312 comprises a spring mounting brace 3121, an elastic stopping column 3122, an inner ring spring 3123 and an outer ring spring 3124.
  • the elastic stopping column 3122 is mounted vertically onto the spring mounting brace 3121, which is then mounted onto the upper end surface of the upper axle box 3111.
  • the inner ring spring 3123 is sleeved onto the elastic stopping column 3122, and the outer ring spring 3124 is sleeved onto the inner ring spring 3123.
  • the primary axle box suspension device 31 of the present embodiment allows to adjust the longitudinal and lateral rigidity of the rotary arm elastic joint 3113, so as to acquire the longitudinal and lateral rigidity value required for the bogie in high-speed running, and improve the dynamic performance of railway vehicles in high-speed running.
  • the outer ring spring 3124 and inner ring spring 3123 are set at upper part of the upper axle box 3111, the rotary arm elastic joint 3113 is free of additional moment generated by the spring force, hence, this can increase the service life and reliability of the rotary arm elastic joint 3113, and realize abrasion-free or low-abrasion design of the primary axle box suspension device.
  • the aforementioned bogie for high-speed railway vehicles also can comprise an axle temperature detector (not shown), which can be a temperature sensor and mounted onto the lower axle box 3112 of the axle box positioning rotary arm 311 for detecting the temperature of the wheel axle 12 and thus guaranteeing the running safety of railway vehicles.
  • the axle temperature detector can also be set on the upper axle box 3111.
  • the aforementioned bogie for high-speed railway vehicles is also provided with a traction rod device 6.
  • One end of the traction rod device 6 is connected with the intermediate crossbeam 22, and the other end is connected with the carbody.
  • the traction rod device 6 is set longitudinally to provide tractive force for the intermediate crossbeam 22.
  • the traction rod device 6 can be designed with different kinds of structures.
  • FIG. 8 depicts a perspective view of a traction rod device in a third embodiment of the present invention.
  • the traction rod device 6 comprises a traction rod 61, elastic joints 62 and a fixed seat 63.
  • the elastic joints 62 can be designed into rubber joints, and mounted into the mounting holes of the traction rod 61.
  • the elastic joints 62 can be mated with the mounting holes by interference fit, in order to improve the fit tightness.
  • Both ends of each of the elastic joints 62 are of a protruding semicolumn structure.
  • Semicolumn holes are opened on the fixed seat 63, and the semicolumn structure at both ends of one of the elastic joints 62 is mated with the semicolumn holes on the fixed seat 63, and the semicolumn structure at both ends of the other elastic joint 62 is used to mate with the semicolumn mounting holes of the carbody.
  • the fixed seat 63 is connected with the intermediate crossbeam 22 in a way that the fixed seat 63 can be welded onto the intermediate crossbeam 22.
  • the elastic joint 62 at the other end of the traction rod 61 is connected with a semicolumn mounting seat of the carbody.
  • the elastic joint 62 is mated with the mounting holes of the fixed seat 63 in half arc pattern, this can eliminate the rotational wear of the elastic joint 62, and obtain a larger mating area, thus transferring a larger longitudinal force with reliable performance. Both ends of the elastic joint 62 are of a protruding structure, and the elastic joint 62 can be mated with the mounting holes of the fixed seat 63 in other proper patterns.
  • the aforementioned bogie for high-speed railway vehicles also comprises some elastic safety chains 7, e.g., 4 elastic safety chains 7.
  • One end of the elastic safety chain 7 is connected with the intermediate crossbeam 22, and the other end is connected with the carbody.
  • the elastic safety chain 7 can transfer a certain longitudinal force in the case of failure of the traction rod device 6, and also prevent excessive vertical jumping displacement generated by the carbody in relation to the frame 2, thus improving the running safety of railway vehicles.
  • the frame 2 also comprises two auxiliary crossbeams 23, both ends of which are separately connected with the side beams 21 and distributed evenly at both sides of the intermediate crossbeam 22.
  • the structural strength of the frame 2 can be improved with the setting of the auxiliary crossbeams 23.
  • the aforementioned bogie for high-speed railway vehicles also comprises a braking device 8, which comprises a brake disc 81, a brake cylinder, a brake pad and a clamp.
  • the brake pad is mounted onto the clamp, and the clamp is mounted onto the auxiliary crossbeam 23.
  • the brake disc 81 is fixed on the wheel axle 12.
  • the frictional force generated between the brake pad and the brake disc 81 is used to provide braking force for the railway vehicles.
  • a brake hanger 231 is set on the auxiliary crossbeam 23, the brake cylinder and clamp of the braking device 8 can be suspended on the brake hanger 231 by bolts.
  • both ends of the wheel axle 12 are provided with an antiskid device 9, which is designed into either mechanical or electronic types.
  • the antiskid device 9 can control indirectly the braking force of the braking device 8. When the braking device 8 is actuated, the antiskid device 9 can increase the sticking coefficient between the wheels 11 and the track, thus avoiding skidding of the wheels 11 in the braking process.
  • the aforementioned bogie for high-speed railway vehicles also comprises at least one weighing valves 10, wherein one end of each weighing valve is connected with the mounting seat on the primary axle box suspension device 31, and the other end is connected with one of the side beams 21 and located at outer side of the side beam 21.
  • the weighing valve 10 can control the braking force of railway vehicles in idle or loaded state, thus meeting the requirements of railway vehicles for different braking forces under varied load conditions.
  • the wheel axle 12 can be designed into a solid axle.
  • the wheel axle 12 can be a hollow axle, helping to reduce the mass of the wheel axle 12 and further the unsprung mass of the bogie. So, this allows to conduct easily ultrasonic flaw detection test for the wheel axle 12 and lower down its maintenance cost.
  • the wheels 11 can be designed into straight web wheels or other web types, thus reducing the mass of the wheels 11 and unsprung mass of the bogie, cut down the wheel-rail force and improve the dynamic performance of railway vehicles.
  • the aforementioned bogie for high-speed railway vehicles can enhance the linear running stability, safety and curve negotiation performance of the high-speed railway vehicles, especially for wagons whose running speed can reach or exceed 200Km/h.
  • the embodiments of the present invention also provide the secondary suspension system that can be applied to the above bogie for the high-speed railway vehicles.
  • the secondary suspension system 4 comprises at least two spring sets 41, which are arranged at interval on the intermediate crossbeam 22 and located between the side beams 21.
  • the transverse spacing of two spring sets 41 is 500-700mm, and the upper parts of the spring sets 41 are configured to connect with the carbody.
  • Two mounting seats for the spring sets can be arranged on the intermediate crossbeam 22.
  • These two spring sets 41 can be made of rubber springs or other types of springs, e.g., metal or air springs. Two bulges are set on the upper part of each of the spring sets 41 for facilitating connection with the carbody.
  • the spring sets 41 can bear a vertical load of the carbody and also provide a proper moment of rotational resistance between the frame 2 and the carbody.
  • the secondary suspension system 4 also comprises secondary vertical dampers 42, secondary transverse dampers 43 and yaw dampers 44.
  • One end of each of the secondary vertical dampers 42 is connected with the frame 2, and the other end is connected with the carbody.
  • One end of each of the secondary transverse dampers 43 is connected with the frame 2, and the other end is connected with the carbody.
  • One end of each of the yaw dampers 44 is connected with the outer side of the side beam 21, and the other end is connected with the carbody.
  • each of the secondary vertical damper 42 can be designed into an oil damper comprising an oil cylinder and a piston rod. Hydraulic damping force can be formed by stretching and compressing the piston rod, so as to realize a satisfactory vibration damping effect and flexible damping effect.
  • a mounting seat for the secondary vertical damper 42 can be set on each side beam 21. A lower end of the secondary vertical damper 42 is connected with the mounting seat for the secondary vertical damper, and an upper end is connected with the carbody.
  • the secondary vertical dampers 42 can be separately set at outer sides of two side beams 21 and provide a lateral rolling damping for the carbody to limit the maximum lateral rolling displacement of the carbody and improve the lateral rolling stability of vehicles.
  • the secondary transverse dampers 43 and yaw dampers 44 can also be designed into oil dampers.
  • Two secondary transverse dampers 43 can be separately set at inner sides of two side beams 21. One end of each of the secondary transverse dampers 43 is connected with a mounting seat at inner side of the side beam 21, and the other end is connected with the carbody.
  • the secondary transverse damper 43 can provide transverse vibration damping for the railway vehicles in high-speed running, thus further increasing the linear running stability of the railway vehicles.
  • the yaw dampers 44 are mounted at outer sides of the side beams 21 in longitudinal and horizontal pattern, thus avoiding the occurrence of hunting instability at high-speed and improving the running stability of railway vehicles.
  • the embodiments of the present invention also provide a frame for a bogie for the high-speed railway vehicles, which is applied to the aforementioned bogie for the high-speed railway vehicles.
  • the frame 2 comprises two side beams 21 and an intermediate crossbeam 22.
  • a middle part of each of the side beams 21 has provided with a concave portion 211, and both ends of the intermediate crossbeam 22 are connected with the concave portions 211 of the side beams 21, respectively.
  • the intermediate crossbeam 22 and the side beams 21 can be connected by means of plugging fit; in detail, an upper cover plate is mounted onto upper end surface of the concave portion 211 of the side beam 21, and a lower cover plate is mounted onto the lower end surface of the concave portion 211; the upper and lower cover plates run parallel and protrude out toward the inner side of the side beam 21.
  • the frame 2 can be assembled by means of the aforementioned plugging fit to enhance its structural strength, or connected by other known means.
  • the intermediate crossbeam 22 and side beams 21 are formed integrally.
  • the embodiments of the present invention also provide a primary suspension system for a bogie for the high-speed railway vehicles, which is applied to the aforementioned bogie for the high-speed railway vehicles.
  • a primary axle box suspension device 31 comprises an axle box positioning rotary arm 311 and a primary suspension spring 312.
  • a lower end of the axle box positioning rotary arm 311 is connected with the wheel axle 12, and an upper end is connected with the side beam 21.
  • the primary suspension spring 312 is mounted onto an upper end of the axle box positioning rotary arm 311, and both ends of the side beam 21 are separately provided with a spring mounting hole, into which the primary suspension spring 312 is mounted.
  • axle box positioning rotary arm 311 is of a split structure that comprises an upper axle box 3111, a lower axle box 3112 and a rotary arm elastic joint 3113 coupled together.
  • the upper axle box 3111 is of a semi-bushing structure, and the other end is provided with a rotary arm elastic joint mounting hole 3114.
  • the lower axle box 3112 is of a semi-bushing structure, and the upper axle box 3111 and the lower axle box 3112 are butt-jointed to form a bushing 3115 for installation of the wheel axle 12.
  • a bearing can be mounted onto the wheel axle 12, and the bushing 3115 is sleeved onto the bearing, realizing the connection of the axle box positioning rotary arm 311 and the wheel axle 12.
  • the axle box positioning rotary arm 311 is of the split structure composed of the upper axle box 3111 and the lower axle box 3112, the wheelset 1 can be easily replaced during repair and maintenance.
  • Both ends of the rotary arm elastic joint 3113 are of a semicolumn structure that may adopt rubber joint for the rotary arm.
  • the semicolumn structure of the rotary arm elastic joint 3113 is mated with a mounting seat on the side beam 21 in half arc pattern, so that the rotary arm elastic joint 3113 can withstand higher longitudinal load, and abnormal abrasion between the rotary arm elastic joint 3113 and the mounting seat of the side beam 21 can also be avoided to increase the service life and reliability of the rotary arm elastic joint 3113.
  • the primary suspension spring 312 comprises a spring mounting brace 3121, an elastic stopping column 3122, an inner ring spring 3123 and an outer ring spring 3124.
  • the elastic stopping column 3122 is mounted vertically onto the spring mounting brace 3121, which is then mounted onto the upper end surface of the upper axle box 3111.
  • the inner ring spring 3123 is sleeved onto the elastic stopping column 3122, and the outer ring spring 3124 sleeved onto the inner ring spring 3123.
  • the primary axle box suspension device 31 of the present embodiment allows to adjust the longitudinal and lateral rigidity of the rotary arm elastic joint 3113, so as to acquire the longitudinal and lateral rigidity value required for the bogie in high-speed running, and improve the dynamic performance of railway vehicles in high-speed running.
  • the outer ring spring 3124 and inner ring spring 3123 are set at upper part of the upper axle box 3111, the rotary arm elastic joint 3113 is free of additional moment generated by the spring force, hence, this can increase the service life and reliability of the rotary arm elastic joint 3113, and realize abrasion-free or low-abrasion design of the primary axle box suspension device.
  • the embodiments of the present invention also provide a traction rod device for a bogie for high-speed railway vehicles, which is applied to the aforementioned bogie for high-speed railway vehicles.
  • the traction rod device 6 comprises a traction rod 61, elastic joints 62 and a fixed seat 63.
  • the elastic joints 62 can be designed into rubber joints, and mounted into the mounting holes of the traction rod 61.
  • the elastic joints 62 can be mated with the mounting holes by interference fit, in order to improve the fit tightness.
  • Both ends of each of the elastic joints 62 are of a protruding semicolumn structure.
  • Semicolumn holes are opened on the fixed seat 63, and the semicolumn structure at both ends of one of the elastic joints 62 is mated with the semicolumn holes on the fixed seat 63, and the semicolumn structure at both ends of the other elastic joint 62 is used to mate with the semicolumn mounting holes of the carbody.
  • the fixed seat 63 is connected with the intermediate crossbeam 22 in a way that the fixed seat 63 can be welded onto the intermediate crossbeam 22.
  • the elastic joint 62 at the other end of the traction rod 61 is connected with a semicolumn mounting seat of the carbody.
  • both ends of the elastic joint 62 are of a protruding structure, and the mounting holes of the fixed seat 63 can be mated with the mounting holes of the intermediate crossbeam 22 in other proper patterns.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
EP12716173.5A 2011-12-23 2012-04-06 Drehgestell für hochgeschwindigkeitsschienenfahrzeuge Active EP2783939B1 (de)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
CN201110438669.5A CN102490754B (zh) 2011-12-23 2011-12-23 高速铁路货车转向架构架
CN201110437255.0A CN102490753B (zh) 2011-12-23 2011-12-23 铁路货车转向架的牵引拉杆装置
CN201110440779.5A CN102490755B (zh) 2011-12-23 2011-12-23 高速铁路货车转向架
CN2011104387950A CN102490745A (zh) 2011-12-23 2011-12-23 高速铁路货车转向架二系悬挂装置
CN2011104407225A CN102490752A (zh) 2011-12-23 2011-12-23 高速铁路货车转向架一系悬挂装置
PCT/CN2012/073579 WO2013091319A1 (zh) 2011-12-23 2012-04-06 高速铁路车辆转向架

Publications (3)

Publication Number Publication Date
EP2783939A1 true EP2783939A1 (de) 2014-10-01
EP2783939A4 EP2783939A4 (de) 2015-11-18
EP2783939B1 EP2783939B1 (de) 2017-03-29

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WO (1) WO2013091319A1 (de)

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WO2016030281A1 (de) * 2014-08-26 2016-03-03 Siemens Aktiengesellschaft Fahrwerk für ein schienenfahrzeug
WO2016083010A1 (de) * 2014-11-27 2016-06-02 Siemens Ag Österreich Federtopf für eine primärfederung eines schienenfahrzeugs
EP3135553A1 (de) * 2015-08-28 2017-03-01 Zhuzhou Times New Material Technology Co., Ltd. Verfahren zur verhinderung des bruchs von stahlfedern
JPWO2016189854A1 (ja) * 2015-05-25 2017-12-14 川崎重工業株式会社 軌条車両用台車及びそれを備えた軌条車両
RU2678797C1 (ru) * 2017-09-19 2019-02-01 СиАрАрСи ЧАНЧУНЬ РЭЙЛВЭЙ ВИИКЛЗ КО., ЛТД. Рама тележки прицепного вагона и тележка прицепного вагона, имеющая такую раму
US10532752B2 (en) 2015-03-03 2020-01-14 Siemens Mobility GmbH Chassis frame for a rail vehicle
WO2020053608A1 (en) * 2018-09-12 2020-03-19 Ganz Motor Kft. Two-axle modular bogie assembly for railway vehicles
JP2021000937A (ja) * 2019-06-24 2021-01-07 東海旅客鉄道株式会社 台車回転治具及び台車の回転方法
EP4063226A4 (de) * 2019-12-20 2023-01-18 CRRC Meishan Co., Ltd. Hochgeschwindigkeitswagendrehgestell für die unabhängige stromerzeugung

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AT516364A1 (de) * 2014-09-22 2016-04-15 Siemens Ag Oesterreich Fahrwerksrahmen mit Federtopf
JP6936572B2 (ja) * 2016-11-21 2021-09-15 三菱重工エンジニアリング株式会社 軌道式車両
CN207225373U (zh) * 2017-09-19 2018-04-13 中车长春轨道客车股份有限公司 一种动车构架及具有该动车构架的动车转向架
EP3620345A4 (de) * 2017-09-19 2021-01-20 CRRC Changchun Railway Vehicles Co., Ltd. Drehgestellrahmen und drehgestell damit
CN107901939B (zh) * 2017-12-14 2024-03-26 中车齐齐哈尔车辆有限公司 转向架及其自适应转臂定位装置
DE102018210880A1 (de) * 2018-07-03 2020-01-09 Siemens Aktiengesellschaft Radsatzzwischenrahmen für ein Schienenfahrzeug
CN110254461B (zh) * 2019-07-02 2024-04-05 株洲时代新材料科技股份有限公司 抗侧滚扭杆上的刚度可调的横向弹性止档及刚度调节方法
CN111661095B (zh) * 2020-07-17 2024-08-20 中车资阳机车有限公司 一种悬挂式货运空铁的一系悬挂装置
CN113696924B (zh) * 2021-09-08 2023-05-23 中车唐山机车车辆有限公司 一系悬挂装置、定位弹簧、转向架及轨道列车
CN113978504B (zh) * 2021-11-18 2023-07-25 中车长春轨道客车股份有限公司 具有轮对调整功能的线性感应电机转向架
CN114248815A (zh) * 2022-01-17 2022-03-29 西南交通大学 一种采用双轴箱悬挂和永磁直驱电机的轨道车辆转向架

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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016030281A1 (de) * 2014-08-26 2016-03-03 Siemens Aktiengesellschaft Fahrwerk für ein schienenfahrzeug
WO2016083010A1 (de) * 2014-11-27 2016-06-02 Siemens Ag Österreich Federtopf für eine primärfederung eines schienenfahrzeugs
US10421466B2 (en) 2014-11-27 2019-09-24 Siemens Mobility GmbH Spring cup for a primary suspension of a rail vehicle
US10532752B2 (en) 2015-03-03 2020-01-14 Siemens Mobility GmbH Chassis frame for a rail vehicle
JPWO2016189854A1 (ja) * 2015-05-25 2017-12-14 川崎重工業株式会社 軌条車両用台車及びそれを備えた軌条車両
US10793167B2 (en) 2015-05-25 2020-10-06 Kawasaki Jukogyo Kabushiki Kaisha Railcar bogie and railcar including same
EP3135553A1 (de) * 2015-08-28 2017-03-01 Zhuzhou Times New Material Technology Co., Ltd. Verfahren zur verhinderung des bruchs von stahlfedern
RU2678797C1 (ru) * 2017-09-19 2019-02-01 СиАрАрСи ЧАНЧУНЬ РЭЙЛВЭЙ ВИИКЛЗ КО., ЛТД. Рама тележки прицепного вагона и тележка прицепного вагона, имеющая такую раму
EP3623249A4 (de) * 2017-09-19 2021-02-24 CRRC Changchun Railway Vehicles Co., Ltd. Anhängerrahmen und anhängerdrehgestell damit
WO2020053608A1 (en) * 2018-09-12 2020-03-19 Ganz Motor Kft. Two-axle modular bogie assembly for railway vehicles
JP2021000937A (ja) * 2019-06-24 2021-01-07 東海旅客鉄道株式会社 台車回転治具及び台車の回転方法
EP4063226A4 (de) * 2019-12-20 2023-01-18 CRRC Meishan Co., Ltd. Hochgeschwindigkeitswagendrehgestell für die unabhängige stromerzeugung

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WO2013091319A1 (zh) 2013-06-27
EP2783939A4 (de) 2015-11-18

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