CN113815668A - Bogie axle box rubber damping spring and bogie - Google Patents
Bogie axle box rubber damping spring and bogie Download PDFInfo
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- CN113815668A CN113815668A CN202111131521.7A CN202111131521A CN113815668A CN 113815668 A CN113815668 A CN 113815668A CN 202111131521 A CN202111131521 A CN 202111131521A CN 113815668 A CN113815668 A CN 113815668A
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- 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
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Abstract
The invention provides a rubber damping spring of a bogie axle box, which comprises an outer sleeve, a rubber cone and a mandrel, wherein the outer sleeve is sleeved on the mandrel; the core shaft is a hollow shaft with two closed ends, the bottom end of the outer sleeve is closed, the inner wall of the outer sleeve, the rubber cone and the bottom end wall of the core shaft jointly enclose a sealed cavity, damping media are filled in the cavity of the core shaft and the sealed cavity, and a damping valve is arranged on the bottom end wall of the core shaft; the damper valve has a normally open passage communicating the cavity and the seal chamber, and has a high pressure passage that opens when a pressure difference between the cavity and the seal chamber reaches a threshold value and closes when the pressure difference between the cavity and the seal chamber is below the threshold value. The rubber damping spring for the bogie axle box provided by the invention can improve the vibration damping performance of the bogie when a train runs at a high speed in a straight line and the anti-rolling performance of the bogie in the low-speed curve running process. The invention also provides a bogie adopting the bogie axle box rubber damping spring.
Description
Technical Field
The invention belongs to the technical field of railway vehicle bogies, and particularly relates to a bogie axle box rubber damping spring and a bogie.
Background
With the increase of the demand of the international interconnection and intercommunication operation, the running line of the train is more complex, and the requirement on the riding comfort is higher, so that the vibration damping performance of the suspension system of the train bogie needs to be further improved, and the conventional passive suspension system cannot meet the design requirement. Under the condition, the bogie axle box rubber damping spring is generated by the way, and the combined action of the rubber cone spring and the hydraulic damping structure which are vertically overlapped and arranged is utilized, so that the supporting rigidity is improved, but the train can bear high-frequency excitation from a track in the high-speed straight line running process, the supporting rigidity of the bogie needs to be reduced to offset excitation transmission at the moment, and the supporting rigidity of the bogie needs to be improved to improve the anti-rolling performance when the train runs at a low-speed curve, so that the design standard of the rubber damping spring is difficult to control, and the vibration reduction performance of the bogie when the train runs at a high-speed straight line and the anti-rolling performance of the bogie in the low-speed curve running process are considered, so that the problem which needs to be solved at present is solved urgently.
Disclosure of Invention
The embodiment of the invention provides a rubber damping spring of a bogie axle box and a bogie, and aims to improve the vibration damping performance of the bogie when a train runs at a high speed in a straight line and the anti-rolling performance of the bogie in the low-speed curve running process.
In order to achieve the purpose, the invention adopts the technical scheme that: in a first aspect, a rubber damping spring for a bogie axle box is provided, which comprises an outer sleeve, a rubber cone and a mandrel; the core shaft is a hollow shaft with two closed ends, the bottom end of the outer sleeve is closed, the inner wall of the outer sleeve, the rubber cone and the bottom end wall of the core shaft jointly enclose a sealed cavity, damping media are filled in the cavity of the core shaft and the sealed cavity, and a damping valve is arranged on the bottom end wall of the core shaft; the damper valve has a normally open passage communicating the cavity and the seal chamber, and has a high pressure passage that opens when a pressure difference between the cavity and the seal chamber reaches a threshold value and closes when the pressure difference between the cavity and the seal chamber is below the threshold value.
With reference to the first aspect, in one possible implementation, a damping valve includes a valve body and a valve spool; the valve body is arranged on the bottom end wall of the mandrel and is provided with a valve hole extending along the axial direction of the mandrel, the valve body is provided with a normal damping flow channel and a high-pressure damping flow channel which extend downwards from the top end of the valve body and are respectively communicated with the valve hole, and a normal through flow channel which extends upwards from the bottom end of the valve body and is communicated with the valve hole; the valve core is connected in the valve hole in a sealing and sliding manner along the axial direction of the valve body, a central hole extending upwards from the bottom end of the valve core is arranged on the valve core, and a first butt hole and a second butt hole which respectively extend from the side wall of the valve core to be communicated with the central hole are also arranged; the normally-damping flow channel is always communicated with the first butt joint hole and forms a normally-open channel; when the pressure difference between the cavity and the sealing chamber is lower than a threshold value, the peripheral wall of the valve core seals the high-pressure damping flow passage, and when the pressure difference between the cavity and the sealing chamber reaches the threshold value, the valve core slides to the high-pressure damping flow passage under the pushing of pressure to be communicated with the second butt joint hole and form a high-pressure channel.
In some embodiments, the top end of the valve hole extends to the top wall of the valve body, the extending end is in threaded connection with an adjusting piece, and an elastic piece is arranged between the adjusting piece and the top end of the valve core.
In some embodiments, the hole wall of the valve hole is provided with a concave cavity extending along the axial direction of the valve hole, the normal damping flow passage and the first butt hole are communicated with the concave cavity, and the extending length of the concave cavity is equal to or greater than the sliding stroke of the valve core.
With reference to the first aspect, in another possible implementation manner, the damping valve includes a valve body and a valve core; the valve body is arranged on the bottom end wall of the mandrel and is provided with a valve hole extending along the axial direction of the mandrel, the top end of the valve hole is provided with an elastic element, a through hole extending along the axial direction of the valve hole and forming a normally open channel is arranged on the side of the valve hole on the valve body, the valve body is also provided with a first flow passage extending downwards from the top end of the valve body and communicated with the valve hole, and a second flow passage extending upwards from the bottom end of the valve body and communicated with the valve hole; the valve core is connected in the valve hole in a sealing and sliding mode along the axial direction of the valve body and is abutted against the elastic element, a ring groove extending along the axial direction of the valve core is formed in the peripheral wall of the valve core, when the pressure difference between the cavity and the sealing cavity is lower than a threshold value, the first flow channel and/or the second flow channel are/is blocked by the peripheral wall of the valve core, and when the pressure difference between the cavity and the sealing cavity reaches the threshold value, the valve core slides to the first flow channel and the second flow channel under the pushing of pressure to be communicated with the ring groove and form a high-pressure channel.
Illustratively, the top end of the valve body is screwed with a fastener, and one end of the fastener extends into the valve hole and abuts against the elastic element.
In some embodiments, a plurality of damping valves are distributed on the bottom wall of the mandrel at intervals, and the opening threshold of the high-pressure channel of each damping valve is different.
With reference to the first aspect, in a possible implementation manner, an electromagnetic coil is disposed in the cavity and/or the sealed chamber, and the damping medium is magnetorheological fluid.
Specifically, a ferromagnetic body is arranged in the cavity and/or the sealed cavity and close to the damping valve, and the electromagnetic coil is wound on the ferromagnetic body.
The bogie axle box rubber damping spring provided by the invention has the beneficial effects that: compared with the prior art, the bogie axle box rubber damping spring disclosed by the invention has the advantages that when a train runs at a high speed in a straight line, a bogie bears high-frequency excitation from a track, so that the rubber cone continuously extrudes the volume of the sealed cavity, at the moment, the pressure in the sealed cavity exceeds the pressure in the cavity due to the fact that the circulation speed of a damping medium in the normally open channel cannot reach the degree matched with the excitation frequency, and when the pressure difference between the high-pressure channel and the normally open channel reaches a threshold value, the high-pressure channel on the damping valve is opened, so that the damping medium is circulated by the high-pressure channel and the normally open channel together, the hydraulic damping rigidity is reduced, the integral rigidity of the damping spring is reduced, and the damping performance of the bogie is improved; when a train enters a curve of a curve to run, the running speed is reduced, the excitation frequency of the bogie from the track is reduced into low-frequency excitation, and the damping medium only needs to circulate between the cavity and the sealing chamber through the normally open channel to meet the response requirement of the low-frequency excitation; therefore, the high-pressure channel can be automatically opened or closed through the vibration excitation frequency borne by the bogie, so that the rigidity of the damping spring is automatically reduced to improve the damping performance of the bogie when the train runs at a high speed in a straight line, and the rigidity of the damping spring is automatically increased along with the reduction of the curve running speed of the train, so that the anti-side rolling capability of the bogie is improved.
In a second aspect, an embodiment of the present invention further provides a bogie, including the bogie axle box rubber damping spring, having the same beneficial effects as the bogie axle box rubber damping spring, and therefore, the details are not repeated herein.
Drawings
FIG. 1 is a schematic structural diagram of a rubber damping spring of a bogie axle box according to an embodiment of the invention;
FIG. 2 is a schematic structural diagram of a damping valve used in an embodiment of the present invention;
FIG. 3 is a schematic structural diagram of a damping valve used in another embodiment of the present invention;
fig. 4 is a schematic structural diagram of a rubber damping spring of a bogie axle box according to another embodiment of the invention.
In the figure: 10. a jacket; 11. sealing the chamber; 20. a rubber cone; 30. a mandrel; 31. a cavity; 40. a damping medium; 50. a damping valve; 51. a valve body; 511. a valve bore; 5111. a concave cavity; 512. a constant damping flow channel; 513. a high pressure damping flow channel; 514. a normally open flow passage; 515. a through hole; 516. a first flow passage; 517. a second flow passage; 52. a valve core; 521. a central bore; 522. a first mating hole; 523. a second docking hole; 524. an adjustment member; 525. an elastic member; 526. a ring groove; 527. an elastic element; 528. a fastener; 60. an electromagnetic coil; 61. a ferromagnetic body.
Detailed Description
In order to make the technical problems, technical solutions and advantageous effects to be solved by the present invention more clearly apparent, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
It should be noted that the rubber damper spring of the bogie axle box of the present invention is also referred to as a rubber damper spring, hereinafter simply referred to as a tie spring, because it is called an axle box suspension, also referred to as a primary suspension, installed between the bogie axle box or equalizer beam and the frame; the invention relates to a method for improving the rigidity of a conical rubber spring, which is characterized in that the conical rubber spring is adopted as a train spring of a railway vehicle, the rigidity of the conical rubber spring is determined by the taper of a rubber body and the number of conical layers of the conical rubber spring, and the conical rubber spring is a structural part processed according to a designed size, so that the conical rubber spring does not have the rigidity adjusting capacity in the actual use process.
Referring to fig. 1 to 3 together, the rubber damping spring of the bogie axle box according to the present invention will now be described. The rubber damping spring of the bogie axle box comprises an outer sleeve 10, a rubber cone 20 and a mandrel 30; the mandrel 30 is a hollow shaft with two closed ends, the bottom end of the outer sleeve 10 is closed, the inner wall of the outer sleeve 10, the rubber cone 20 and the bottom end wall of the mandrel 30 enclose a sealed chamber 11 together, a damping medium 40 is filled in the cavity 31 of the mandrel 30 and the sealed chamber 11, and a damping valve 50 is arranged on the bottom end wall of the mandrel 30; the damping valve 50 has a normally open passage communicating the cavity 31 and the seal chamber 11, and has a high pressure passage that opens when the pressure difference between the cavity 31 and the seal chamber 11 reaches a threshold value and closes when the pressure difference between the cavity 31 and the seal chamber 11 is below the threshold value.
The rubber damping spring for bogie axle box provided by this embodiment adopts the main structure of the conventional conical rubber spring, that is, the rubber cone 20 is embedded on the inner conical wall of the outer sleeve 10, the outer conical wall of the mandrel 30 is embedded on the inner hole of the rubber cone 20, and different from the conventional conical rubber spring, the mandrel 30 is provided with the cavity 31, and the bottom end of the outer sleeve 10 is closed to form the sealed chamber 11, the cavity 31 is communicated with the sealed chamber 11 by installing the damping valve 50 on the bottom wall of the mandrel 30 (and the lower cavity wall of the cavity 31), the damping medium 40 such as damping oil and hydraulic oil, even the gas medium is circulated between the cavity 31 and the sealed chamber 11 through the damping valve 50, so that the pressure in the two chambers tends to be balanced, the damping valve 50 may specifically be a flow regulating valve or throttle valve arranged on the normally open channel to regulate the normal circulation speed of the medium (or may not be provided with a flow regulating valve or throttle valve, a normally open channel is directly arranged according to the design flow requirement), and meanwhile, a pressure regulating valve is arranged on the high-pressure channel of the normally open channel to control the opening and closing threshold of the high-pressure channel, when the high-pressure channel is opened, the circulation speed of the damping medium 40 between the sealed chamber 11 and the cavity 31 is increased, and the damping supporting rigidity is reduced, otherwise, when the high-pressure channel is closed, the damping medium 40 can only circulate through the normally open channel, so that the circulation speed between the sealed chamber 11 and the cavity 31 is reduced, and the damping rigidity is increased, and because the elastic supporting rigidity of the rubber cone 20 is unchanged, the change of the damping rigidity represents the change of the integral supporting rigidity of the series spring.
Compared with the prior art, when a train runs at a high speed in a straight line, the bogie bears high-frequency excitation from a track, so that the rubber cone 20 continuously extrudes the volume of the sealed chamber 11, at the moment, the flow speed of the damping medium 40 in the normally open channel cannot reach the degree matched with the excitation frequency, so that the pressure in the sealed chamber 11 exceeds the pressure in the cavity 31, when the pressure difference between the high pressure and the pressure reaches a threshold value, the high pressure channel on the damping valve 50 is opened, so that the high pressure channel and the normally open channel perform the flow of the damping medium 40 together, the hydraulic damping rigidity is reduced, the integral rigidity of the series of springs is reduced, and the vibration damping performance of the bogie is improved; when a train enters a curve of a curve to run, the running speed is reduced, the excitation frequency of the bogie from the track is reduced to low-frequency excitation, the damping medium 40 only needs to circulate between the cavity 31 and the sealing chamber 11 through a normally open channel, and the response requirement of the low-frequency excitation can be met, so that the pressure difference between the cavity 31 and the sealing chamber 11 is reduced to be lower than a threshold value, the high-pressure channel is closed, the hydraulic damping rigidity is increased, the integral rigidity of a series of springs is increased, and the anti-side-rolling capacity of the bogie can be improved; therefore, the high-pressure channel can be automatically opened or closed through the vibration excitation frequency borne by the bogie, so that the rigidity of the series spring is automatically reduced when the train runs at high speed in a straight line to improve the vibration absorption performance of the bogie, and the rigidity of the series spring is automatically increased when the curve running speed of the train is reduced, so that the anti-side rolling capability of the bogie is improved.
As an embodiment of the damping valve 50, referring to fig. 1 and fig. 2, the damping valve 50 includes a valve body 51 and a valve core 52; the valve body 51 is arranged on the bottom end wall of the mandrel 30 and is provided with a valve hole 511 extending along the axial direction of the mandrel, the valve body 51 is provided with a normal damping flow passage 512 and a high-pressure damping flow passage 513 extending downwards from the top end of the valve body and respectively communicated with the valve hole 511, and a normal through flow passage 514 extending upwards from the bottom end of the valve body and communicated with the valve hole 511; the valve core 52 is connected in the valve hole 511 in a sealing and sliding manner along the axial direction of the valve body 51, the valve core 52 is provided with a central hole 521 extending upwards from the bottom end thereof, and is also provided with a first connecting hole 522 and a second connecting hole 523 which respectively extend from the side wall thereof to be communicated with the central hole 521; the normally-open damping flow passage 512 is always communicated with the first connection hole 522 to form a normally-open passage; when the pressure difference between the cavity 31 and the sealing chamber 11 is lower than a threshold value, the peripheral wall of the valve core 52 seals the high-pressure damping flow passage 513, and when the pressure difference between the cavity 31 and the sealing chamber 11 reaches the threshold value, the valve core 52 slides under the pushing of pressure until the high-pressure damping flow passage 513 is communicated with the second butt hole 523 and forms a high-pressure channel.
Specifically, referring to fig. 2, the top end of the valve hole 511 extends to the top wall of the valve body 51, the extending end is in threaded connection with an adjusting member 524, and an elastic member 525 is disposed between the adjusting member 524 and the top end of the valve core 52.
When a train runs linearly at a high speed, the pressure in the sealed chamber 11 is far higher than the pressure in the cavity 31 due to the high-frequency excitation of the track borne by the bogie, and when the pressure difference between the two chambers is enough to overcome the elastic force of the elastic member 525 (that is, the threshold value is reached), the valve core 52 can be pushed to move upwards to communicate the high-pressure damping flow channel 513 with the second butt hole 523, so that the damping medium 40 in the sealed chamber 11 can flow into the cavity 31 through the high-pressure channel and the normally-open channel together, that is, the flow speed of the damping medium 40 is increased, so that the support stiffness of a series spring is reduced along with the reduction of the damping stiffness, and the vibration damping performance of the bogie is improved; on the contrary, when the train enters a curve of a curve, the speed of the train is reduced, so that the excitation frequency of the track transmitted to the bogie is low, at the moment, the pressure area between the sealed chamber 11 and the cavity 31 can be balanced only by the circulation speed of the damping medium 40 of the normally-open channel, so that the pressure difference basically disappears, the valve core 52 slides downwards under the action of the elastic element 525 to the second butt hole 523 to be staggered with the high-pressure damping flow channel 513, the peripheral wall of the valve core 52 blocks the high-pressure damping flow channel 513, the damping rigidity is increased, and the integral supporting rigidity of the spring is increased, so that the anti-rolling capacity of the bogie is improved; of course, since the elastic force of the spring determines the sliding time of the valve core 52 in the valve hole 511 under the pushing of the pressure difference, that is, the magnitude of the elastic acting force of the spring on the valve core 52 is the threshold value for opening and closing the high-pressure channel, the elastic force of the spring is adjusted by screwing in or screwing out the adjusting member 524, and the magnitude of the threshold value can be adjusted, so that one series of springs can meet the requirements of trains with different operating speeds (mainly the speed specified for linear high-speed operation).
In some embodiments, referring to fig. 2, a cavity 5111 is formed on a hole wall of the valve hole 511 and extends along an axial direction thereof, the constant damping flow passage 512 and the first connection hole 522 are both communicated with the cavity 5111, and an extension length of the cavity 5111 is equal to or greater than a sliding stroke of the valve element 52. Through setting up cavity 5111 structure can guarantee that first butt joint hole 522 can communicate with normal damping runner 512 through cavity 5111 all the time in the process that case 52 slided from top to bottom to guarantee the connected state of normally opening the passageway.
As a modified embodiment of the damping valve 50, please refer to fig. 1 and 3, the damping valve 50 includes a valve body 51 and a valve core 52; wherein, the valve body 51 is set on the bottom end wall of the mandrel 30, there is a valve hole 511 extending along its axial direction, the top of the valve hole 511 has an elastic element 527, the side of the valve hole 511 on the valve body 51 has a through hole 515 extending along its axial direction and forming a normally open channel, the valve body 51 is also set with a first flow channel 516 extending from its top end downwards and communicating with the valve hole 511, and a second flow channel 517 extending from its bottom end upwards and communicating with the valve hole 511; the valve core 52 is connected in the valve hole 511 in a sealing and sliding manner along the axial direction of the valve body 51 and is abutted against the elastic element 527, a circular groove 526 extending along the axial direction of the valve core 52 is formed in the peripheral wall of the valve core 52, when the pressure difference between the cavity 31 and the sealing chamber 11 is lower than a threshold value, the first flow passage 516 and/or the second flow passage 517 are/is sealed by the peripheral wall of the valve core 52, and when the pressure difference between the cavity 31 and the sealing chamber 11 reaches the threshold value, the valve core 52 slides under the pushing of pressure until the first flow passage 516 and the second flow passage 517 are communicated with the circular groove 526 and form a high-pressure passage.
When a train runs linearly at a high speed, the pressure in the sealed chamber 11 is far higher than the pressure in the cavity 31 due to the high-frequency excitation of the track, and when the pressure difference between the two chambers is enough to overcome the elastic force of the elastic element 527 (that is, a threshold value is reached), the valve core 52 can be pushed to move upwards until the annular groove 526 is communicated with the first flow channel 516 and the second flow channel 517 at the same time, so that the damping medium 40 in the sealed chamber 11 can flow into the cavity 31 through the high-pressure channel and the normally-open channel together, that is, the flow speed of the damping medium 40 is increased, so that the support stiffness of a series of springs is reduced along with the reduction of the damping stiffness, and the vibration damping performance of the bogie is improved; on the contrary, when the train enters a curve of a curve, the excitation frequency transmitted to the bogie by the track is low due to the reduction of the speed of the train, and at the moment, the pressure area between the sealed chamber 11 and the cavity 31 can be balanced only through the circulation speed of the damping medium 40 of the normally open channel, so that the pressure difference basically disappears, the valve core 52 slides downwards under the action of the elastic element 527 until the annular groove 526 is staggered with the first flow channel 516 or the second flow channel 517 or both, the peripheral wall of the valve core 52 seals and closes the high-pressure channel, the damping rigidity is increased along with the sealing, and the overall supporting rigidity of the spring is increased, so that the anti-rolling capacity of the bogie is improved.
In the present embodiment, in order to adjust the opening threshold of the high-pressure passage, referring to fig. 3, a fastening member 528 is screwed to the top end of the valve body 51, and one end of the fastening member 528 extends into the valve hole 511 and abuts against the elastic element 527. Because the elastic force of the elastic element 527 determines the sliding time of the valve core 52 in the valve hole 511 under the pushing of the pressure difference, that is, the magnitude of the elastic acting force of the elastic element 527 on the valve core 52 is the threshold value for opening and closing the high-pressure channel, the elastic force of the elastic element 527 on the valve core 52 can be adjusted by screwing in or out the fastening piece 528, and the magnitude of the threshold value can be adjusted, so that one series of springs can meet the train requirements of different running speeds (mainly the speed specified for the linear high-speed running).
In some embodiments, referring to fig. 1, a plurality of damping valves 50 are spaced apart from the bottom wall of the mandrel 30, and the opening threshold of the high-pressure channel of each damping valve 50 is different. The running speed of the train determines that the difference of the excitation frequency of the bogie from the guide rail is different, so that different pressure difference values are formed between the sealed chamber 11 and the cavity 31, generally, the higher the speed is, the higher the excitation frequency is, the pressure difference is increased, and here, by arranging the plurality of damping valves 50, the corresponding one or more damping valves 50 can be correspondingly opened along with the change of the pressure difference value, so that the circulation speed of the damping medium 40 between the sealed chamber 11 and the cavity 31 is adjusted, the self-adjustment of the support rigidity of a spring system is realized, and the high-speed vibration damping performance and the bend anti-rolling capacity of the bogie in the running process of the train are considered.
In some possible implementations, referring to fig. 4, the electromagnetic coil 60 is disposed in the cavity 31 and/or the sealed chamber 11, and the damping medium 40 is a magnetorheological fluid. Specifically, a ferromagnetic body 61 is provided in the cavity 31 and/or the sealed chamber 11 at a position close to the damper valve 50, and the electromagnetic coil 60 is wound around the ferromagnetic body 61.
The magnetorheological fluid is a special suspension system formed by uniformly dispersing micron-sized magnetizable particles in specific carrier mother liquor and additives, shows the characteristic of non-Newtonian fluid under the action of an applied magnetic field, and is converted from free-flowing liquid into semisolid or even solid within millisecond time, thereby showing strong controllable rheological property.
The electromagnetic coil 60 is arranged close to the damping valve 50 in the sealed chamber 11 or the cavity 31 or both of the two, when the current value introduced into the electromagnetic coil 60 is changed, the magnetic field force near the electromagnetic coil 60 can be changed, so that the mobility of the magnetorheological fluid close to the damping valve 50 is changed along with the change of the viscosity of the magnetorheological fluid, specifically, when the current is increased, the magnetic field is increased, the viscosity of the magnetorheological fluid is increased, so that the speed of the magnetorheological fluid flowing through the damping valve 50 is reduced, the damping rigidity is improved, otherwise, the viscosity of the magnetorheological fluid is reduced, the mobility is enhanced, the speed of the magnetorheological fluid flowing through the damping valve 50 is accelerated, the damping rigidity is reduced, and as the response speed of the magnetorheological fluid to the change of the magnetic field is high (millisecond level), the controller has excellent timeliness when the electromagnetic coil 60 is matched, when the speed sensor and the acceleration sensor which are arranged on the bogie detect the running speed and the excited vibration frequency of the bogie, a series of springs can respond instantly and self-adjust to the supporting rigidity matched with the running road condition, so that the anti-rolling capability of the bogie required by the reliable running of the train can be ensured, the vibration damping performance of the bogie can be improved, the riding comfort of the train is improved, and the bogie has good adaptability to the complex road condition in the high-speed and low-speed cross-line operation process of the train.
In addition, the viscosity change of the magnetorheological fluid is realized by controlling the current change of the electromagnetic coil 60, so that the damping rigidity is adjusted, and the curve passing capacity of the bogie can be greatly improved: because the tying springs are symmetrically arranged on the two sides of the bogie, when the bogie runs through a curve of a curve, the current of the electromagnetic coil 60 in the outer tying spring is adjusted and increased in an active control mode, so that the viscosity of magnetorheological fluid in the outer tying spring is increased, the rigidity of the outer tying spring is increased, and meanwhile, the current of the electromagnetic coil 60 in the inner tying spring is adjusted and decreased, so that the viscosity of the magnetorheological fluid in the inner tying spring is reduced, the rigidity of the inner tying spring is reduced, namely, the tying springs on the two sides of the bogie have rigidity of high outside and low inside when a train passes through the curve, and the anti-side rolling capability of the bogie is greatly improved.
Based on the same inventive concept, please refer to fig. 1 to 4, the embodiment of the present application further provides a bogie, including the above bogie axle box rubber damping spring.
Compared with the prior art, the bogie provided by the embodiment adopts the series spring, when a train runs at a high speed in a straight line, the bogie bears high-frequency excitation from a track, so that the rubber cone 20 continuously extrudes the volume of the sealed chamber 11, at the moment, the flow speed of the damping medium 40 in the normally open channel cannot reach the degree matched with the excitation frequency, so that the pressure in the sealed chamber 11 exceeds the pressure in the cavity 31, when the pressure difference between the two reaches a threshold value, the high-pressure channel on the damping valve 50 is opened, so that the damping medium 40 flows through the high-pressure channel and the normally open channel together, the hydraulic damping rigidity is reduced, the integral rigidity of the series spring is reduced, and the vibration damping performance of the bogie is improved; when a train enters a curve of a curve to run, the running speed is reduced, the excitation frequency of the bogie from the track is reduced to low-frequency excitation, the damping medium 40 only needs to circulate between the cavity 31 and the sealing chamber 11 through a normally open channel, and the response requirement of the low-frequency excitation can be met, so that the pressure difference between the cavity 31 and the sealing chamber 11 is reduced to be lower than a threshold value, the high-pressure channel is closed, the hydraulic damping rigidity is increased, the integral rigidity of a series of springs is increased, and the anti-side-rolling capacity of the bogie can be improved; therefore, the high-pressure channel can be automatically opened or closed through the vibration excitation frequency borne by the bogie, so that the rigidity of the series spring is automatically reduced when the train runs at high speed in a straight line to improve the vibration absorption performance of the bogie, and the rigidity of the series spring is automatically increased when the curve running speed of the train is reduced, so that the anti-side rolling capability of the bogie is improved.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.
Claims (10)
1. The rubber damping spring for bogie shaft box includes outer sleeve, rubber cone and core shaft,
the core shaft is a hollow shaft with two closed ends, the bottom end of the outer sleeve is closed, the inner wall of the outer sleeve, the rubber cone and the bottom end wall of the core shaft jointly enclose a sealed cavity, damping media are filled in the cavity of the core shaft and the sealed cavity, and a damping valve is arranged on the bottom end wall of the core shaft;
wherein the damping valve is provided with a normally open channel communicating the cavity and the sealing chamber, and is also provided with a high-pressure channel which is opened when the pressure difference between the cavity and the sealing chamber reaches a threshold value and is closed when the pressure difference between the cavity and the sealing chamber is lower than the threshold value.
2. The bogie axle box rubber damping spring according to claim 1, wherein the damping valve comprises:
the valve body is arranged on the bottom end wall of the mandrel and is provided with a valve hole extending along the axial direction of the mandrel, the valve body is provided with a normal damping flow channel and a high-pressure damping flow channel which extend downwards from the top end of the valve body and are respectively communicated with the valve hole, and the valve body is also provided with a normal through flow channel which extends upwards from the bottom end of the valve body and is communicated with the valve hole;
the valve core is connected in the valve hole in a sealing and sliding manner along the axial direction of the valve body, a central hole extending upwards from the bottom end of the valve core is arranged on the valve core, and a first butt hole and a second butt hole which respectively extend from the side wall of the valve core to be communicated with the central hole are also formed in the valve core;
the normally-open channel is formed by the normally-open damping flow channel and the first butt hole; when the pressure difference between the cavity and the sealing chamber is lower than a threshold value, the peripheral wall of the valve core seals the high-pressure damping flow passage, and when the pressure difference between the cavity and the sealing chamber reaches the threshold value, the valve core slides to the high-pressure damping flow passage under the pushing of pressure to be communicated with the second butt joint hole and form the high-pressure channel.
3. The rubber damping spring for a bogie axle box according to claim 2 wherein the top end of the valve hole extends to the top wall of the valve body, and the extending end is threadedly connected with an adjusting member, and an elastic member is provided between the adjusting member and the top end of the valve core.
4. The rubber damping spring for bogie shaft box as recited in claim 2, wherein the hole wall of said valve hole is provided with a concave cavity extending along the axial direction thereof, said normal damping flow passage and said first connection hole are both communicated with said concave cavity, and the extension length of said concave cavity is equal to or greater than the sliding stroke of said spool.
5. The bogie axle box rubber damping spring according to claim 1, wherein the damping valve comprises:
the valve body is arranged on the bottom end wall of the mandrel and is provided with a valve hole extending along the axial direction of the mandrel, the top end of the valve hole is provided with an elastic element, a through hole extending along the axial direction of the valve hole and forming the normally open channel is arranged on the side of the valve hole on the valve body, the valve body is also provided with a first flow passage extending downwards from the top end of the valve body and communicated with the valve hole, and a second flow passage extending upwards from the bottom end of the valve body and communicated with the valve hole;
the valve core, follow the axial seal sliding connection of valve body in the valve hole, and with elastic element butt, set up along its axially extended annular on the perisporium of valve core the cavity with when the pressure differential between the sealed cavity is less than the threshold value, the perisporium of valve core will first runner and/or the shutoff of second runner the cavity with when the pressure differential between the sealed cavity reaches the threshold value, the valve core slides under the pressure promotes to first runner with the second runner all with the annular intercommunication and formation high pressure channel.
6. The bogie axle box rubber damping spring of claim 5, wherein a fastener is threaded into the top end of the valve body, one end of the fastener extending into the valve bore and abutting the resilient element.
7. The rubber damping spring for bogie axle boxes according to claim 1, wherein said damping valves are spaced apart from each other on the bottom wall of said spindle, and the opening threshold of the high pressure passage of each damping valve is different.
8. The bogie axle box rubber damping spring as claimed in any one of claims 1 to 7, wherein an electromagnetic coil is provided in the cavity and/or the sealed chamber and the damping medium is a magnetorheological fluid.
9. The bogie axle box rubber damping spring according to claim 8, wherein a ferromagnetic body is provided in the cavity and/or the sealed cavity adjacent to the damping valve, the electromagnetic coil being wound around the ferromagnetic body.
10. Bogie, characterized in that it comprises a bogie axle box rubber damping spring according to any of claims 1-9.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111131521.7A CN113815668B (en) | 2021-09-26 | 2021-09-26 | Bogie axle box rubber damping spring and bogie |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111131521.7A CN113815668B (en) | 2021-09-26 | 2021-09-26 | Bogie axle box rubber damping spring and bogie |
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| CN113815668A true CN113815668A (en) | 2021-12-21 |
| CN113815668B CN113815668B (en) | 2022-09-27 |
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| CN110594342A (en) * | 2019-09-06 | 2019-12-20 | 株洲时代新材料科技股份有限公司 | Liquid composite spring |
| CN110735881A (en) * | 2019-09-06 | 2020-01-31 | 株洲时代新材料科技股份有限公司 | Rigidity adjusting method of liquid composite spring |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3706362A (en) * | 1969-05-08 | 1972-12-19 | Chrysler France | Telescopic hydraulic damper |
| CN102644693A (en) * | 2012-05-11 | 2012-08-22 | 株洲时代新材料科技股份有限公司 | Adjustment method for dynamic stiffness of rubber joint with liquid damping, and rubber joint |
| CN202531730U (en) * | 2012-05-11 | 2012-11-14 | 株洲时代新材料科技股份有限公司 | Rubber joint with liquid automatic damping stiffness adjusting device |
| JP2014189114A (en) * | 2013-03-27 | 2014-10-06 | Kayaba Ind Co Ltd | Stopper |
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| CN113815668B (en) | 2022-09-27 |
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