WO2023070416A1 - 一种中继阀 - Google Patents

一种中继阀 Download PDF

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Publication number
WO2023070416A1
WO2023070416A1 PCT/CN2021/126913 CN2021126913W WO2023070416A1 WO 2023070416 A1 WO2023070416 A1 WO 2023070416A1 CN 2021126913 W CN2021126913 W CN 2021126913W WO 2023070416 A1 WO2023070416 A1 WO 2023070416A1
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WO
WIPO (PCT)
Prior art keywords
piston
valve body
main valve
chamber
brake cylinder
Prior art date
Application number
PCT/CN2021/126913
Other languages
English (en)
French (fr)
Inventor
申燕飞
全琼
韦雪丽
邵向兰
李婧
肖晨
欧东方
李巧银
刘保华
肖维远
刘毅
杨建平
宋志勇
王开恩
Original Assignee
眉山中车制动科技股份有限公司
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
Application filed by 眉山中车制动科技股份有限公司 filed Critical 眉山中车制动科技股份有限公司
Priority to EP21961784.2A priority Critical patent/EP4230488A4/en
Priority to PCT/CN2021/126913 priority patent/WO2023070416A1/zh
Publication of WO2023070416A1 publication Critical patent/WO2023070416A1/zh

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
    • B60T15/02—Application and release valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/66—Electrical control in fluid-pressure brake systems
    • B60T13/665—Electrical control in fluid-pressure brake systems the systems being specially adapted for transferring two or more command signals, e.g. railway systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
    • B60T17/18—Safety devices; Monitoring
    • B60T17/22—Devices for monitoring or checking brake systems; Signal devices
    • B60T17/228—Devices for monitoring or checking brake systems; Signal devices for railway vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61H—BRAKES OR OTHER RETARDING DEVICES SPECIALLY ADAPTED FOR RAIL VEHICLES; ARRANGEMENT OR DISPOSITION THEREOF IN RAIL VEHICLES
    • B61H13/00—Actuating rail vehicle brakes
    • B61H13/20—Transmitting mechanisms
    • B61H13/30—Transmitting mechanisms adjustable to take account of variation of vehicle weight
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
    • B60T15/02—Application and release valves
    • B60T15/18—Triple or other relay valves which allow step-wise application or release and which are actuated by brake-pipe pressure variation to connect brake cylinders or equivalent to compressed air or vacuum source or atmosphere
    • B60T15/184—Railway control or brake valves

Definitions

  • the invention relates to the technical field of empty and heavy railway vehicles, in particular to a relay valve.
  • the rail vehicle braking system In order to make the running vehicle stop reliably, the rail vehicle braking system usually needs to distribute the braking force according to the load of the vehicle. Excessive braking force can cause the vehicle to skid, causing the wheels of the vehicle to be scratched. Too little braking force will lead to driving safety.
  • the braking system of domestic railway freight cars usually uses indirect measurement of the vehicle load, and the way of adding the upper pressure valve to distribute the braking force, so as to achieve the purpose of reliable speed regulation and parking of the vehicle.
  • the higher-precision vehicle load measurement is direct weighing, and the air pressure that matches the vehicle load is output after direct weighing.
  • the air pressure participates in controlling the braking force to increase the pressure of the brake cylinder. Control precision, prevent vehicle skidding and insufficient braking force, and ensure railway traffic safety.
  • the object of the present invention is: the present invention provides a relay valve, which solves the problem of poor following performance of the existing relay valve.
  • a relay valve including a valve body, the valve body is equipped with a main valve body, a C piston, a Cv piston, a follower mechanism, a pre-control room, a brake cylinder room and an auxiliary air cylinder room, and a movable main valve body
  • the composition is located at the communication channel between the brake cylinder chamber and the auxiliary air cylinder chamber.
  • the movable C piston is formed to block between the brake cylinder chamber and the pre-control chamber, and the movable Cv piston is formed to be blocked by the pre-control chamber at one end.
  • One end of the piston is in contact with the main valve body, the other end of the C piston is in contact with one end of the balance mechanism, and the other end of the Cv piston is in contact with the other end of the balance structure.
  • main valve body composition and the C piston composition are sleeved and matched, and the sleeve of the main valve body is provided with an air inlet, and the air inlet is connected with the hollow cavity inside the main valve body composition, and the hollow cavity is connected to the valve body.
  • the air channel in the body is communicated, and the air channel is communicated with the exhaust port on the valve body.
  • the pre-control room includes a pre-control room I and a pre-control room II, the pre-control room I and the C piston form an effect, the pre-control room II and the Cv piston form an action, and the brake cylinder room includes a brake cylinder room I and a brake cylinder room II, the brake cylinder chamber I and the main valve body form the function, the brake cylinder chamber II and the C piston form the function, and the brake cylinder chamber I and the brake cylinder chamber II are connected through the piston shrinkage hole.
  • the main valve body consists of an axially movable main valve stem, a valve stem reset member is provided between the left end of the main valve stem and the valve body, and the middle part of the main valve stem is located between the brake cylinder chamber and the auxiliary air cylinder. At the communication channel between the chambers, the right end of the main valve stem is in contact with the C piston.
  • the main valve body comprises a main valve seat, the main valve seat is fixed between the brake cylinder chamber and the auxiliary air cylinder chamber, and the middle part of the main valve stem is located at the through hole of the main valve seat.
  • the main valve seat is provided with a radial inlet, and a filter is arranged at the radial inlet.
  • valve stem return member is a valve stem return spring.
  • valve body is connected with a valve cover, and the valve cover clamps the main valve seat in the valve body.
  • the right end of the main valve rod is provided with an air inlet
  • the right end of the main valve rod is sleeved with the C piston
  • the air inlet is connected with the hollow cavity in the main valve rod
  • the hollow cavity is connected with the atmospheric channel in the valve body
  • the atmospheric channel communicates with the exhaust port on the valve body.
  • the air exhaust port is a spiral air exhaust port.
  • the composition of the C piston includes a release valve rod, the left end of the release valve rod is fixed with a C piston, the right end of the release valve rod is movable with a jumping piston, and the stopper on the right side of the jumping piston is fixed on the release valve rod.
  • Diaphragm I is provided between C piston, jumping piston and the jumping spring seat, and a jumping reset part is provided between the jumping piston and the jumping spring seat to relieve valve stem, C piston, jumping piston, diaphragm I and jumping spring seat
  • a jump chamber is formed between them, and the jump chamber communicates with the pre-control chamber.
  • the left side of the C piston is the brake cylinder chamber, and the jump chamber has a smaller active area for the C piston than the jump piston.
  • the jump chamber communicates with the pre-control chamber through the piston shrinkage cavity.
  • a small spring seat is fixed on the relief valve stem
  • a large spring seat is fixed on the jump spring seat
  • a jump reset member is arranged between the small spring seat and the large spring seat.
  • the jump-up reset member is a jump-up spring.
  • the limiting member is a limiting nut, and the limiting nut is connected with the relief valve stem.
  • the relief valve rod is fixedly connected to the C piston rod, and the C piston rod is in contact with the balance mechanism.
  • composition of the Cv piston includes the Cv piston, the left end of the Cv piston is in contact with the diaphragm II, the diaphragm II is arranged on the diaphragm seat, the left side of the diaphragm II blocks the pre-control chamber, the right end of the Cv piston is in contact with the valve There is a Cv reset piece between the bodies.
  • valve body is fixed with a Cv spring seat
  • the Cv piston is mounted on the Cv spring seat
  • a Cv reset member is arranged between the Cv piston and the Cv spring seat.
  • the Cv reset member is a relief spring.
  • the Cv piston is connected with the Cv piston rod, and the Cv piston rod is in contact with the balance mechanism.
  • the balance mechanism includes a balance beam, which relieves the action between the right end of the valve stem and the upper end of the balance beam, the middle part of the balance beam is in contact with the fulcrum of the follower mechanism assembly, and the lower end of the balance beam interacts with the right end of the Cv piston.
  • the upper end of the balance beam is connected to the C piston rod through a torsion spring.
  • valve body is provided with an empty truck signal chamber
  • the weight-dependent mechanism consists of a weight-dependent piston
  • the lower end of the weight-dependent piston blocks the empty-load vehicle signal chamber
  • the weight-dependent piston is connected with the weight-dependent piston rod.
  • a follower reset piece is arranged between the piston and the valve body, and the follower piston rod is connected with a vertically movable adjusting block, and a fulcrum is arranged on the adjusting block.
  • the said deadweight piston rod is connected with the connecting shaft, and the connecting shaft is connected with the adjusting block.
  • weight-carrying piston rod and the adjusting nut are slidably sleeved, and an adjustable spring seat is threadedly connected to the adjusting nut, and a carousel reset member is provided between the adjustable spring seat and the carousel piston.
  • the adjustment block is arranged on a vertically arranged guide chute.
  • the said follow-up reset member is an adjustment spring.
  • the invention has the beneficial effects of better followability and higher sensitivity, and the pressure of the brake cylinder changes proportionally with the change of the load of the vehicle.
  • Fig. 1 is a schematic diagram of the appearance structure of the present invention.
  • Fig. 2 is a structural schematic diagram of the composition of the main valve body of the present invention.
  • Fig. 3 is a structural schematic diagram of the composition of the C-piston of the present invention.
  • Fig. 4 is a structural schematic diagram of the composition of the Cv piston of the present invention.
  • Fig. 5 is a front view of the structure of the follow-the-weight mechanism of the present invention.
  • Fig. 6 is a structural side view of the follow-the-weight mechanism of the present invention.
  • Fig. 7 is a schematic diagram of the structure of the initial bit of the present invention.
  • FIG. 8 is a schematic structural diagram of a jump bit in the present invention.
  • Fig. 9 is a structural schematic diagram of the braking position of the present invention.
  • Fig. 10 is a structural schematic diagram of the holding position of the present invention.
  • Fig. 11 is a schematic structural diagram of the mitigation bit of the present invention.
  • Cv1-Pre-control room I Cv2-Pre-control room II
  • C1-Brake cylinder room I C1-Brake cylinder room I
  • C2-Brake cylinder room II R-Auxiliary air cylinder room
  • T-Empty and heavy vehicle signal room EX1-Atmospheric channel I
  • EX2-atmospheric channel II EX2-atmospheric channel II.
  • 201-piston shrinkage cavity 202-C piston, 203-relief valve stem, 204-small spring seat, 205-diaphragm I, 206-big spring seat, 207-jump spring, 208-limit nut, 209-jump piston , 210-torsion spring, 211-C piston rod, 212-balance beam, 213-jump spring seat, Y-jump chamber.
  • a relay valve includes a valve body.
  • the valve body includes a main valve body 101 and a weighted valve body 407 .
  • the two valve body blocks are fixedly connected by bolts.
  • the main valve body is composed of the main valve body, the pre-control room, the brake cylinder room and the auxiliary air cylinder room R, and the weight-bearing mechanism is arranged in the weight-bearing valve body, and the C piston is clamped between the main valve body and the weight-bearing valve body Composition, Cv piston composition.
  • the pre-control room includes the pre-control room I Cv1 and the pre-control room II Cv2, the pre-control room I Cv1 is composed of the C piston, the pre-control room II Cv2 is composed of the Cv piston, and the brake cylinder room includes the brake cylinder room I C1 and the brake cylinder room II C2, the brake cylinder chamber I C1 is formed with the main valve body, the brake cylinder chamber II C2 is formed with the C piston, and the brake cylinder chamber I C1 and the brake cylinder chamber II C2 are connected through the piston shrinkage hole.
  • the movable main valve body is located in the communication channel between the brake cylinder chamber I and the auxiliary air cylinder chamber R, through the active displacement of the main valve body composition, the communication between the brake cylinder chamber I and the auxiliary air cylinder chamber can be realized or off.
  • the active C piston forms a barrier between the brake cylinder chamber II and the pre-control chamber I. One end of the C piston is in contact with the main valve body, and the other end of the C piston is in contact with one end of the balance mechanism.
  • the active Cv piston is composed of One end is blocked by the pre-control chamber, and the other end composed of the Cv piston is in contact with the other end of the balance structure.
  • the main valve body and the C piston are sleeved and matched.
  • the sleeve of the main valve body is provided with an air inlet.
  • the air inlet communicates with the hollow cavity inside the main valve body.
  • the hollow cavity communicates with the atmospheric passage in the valve body.
  • the air channel communicates with the exhaust port on the valve body.
  • the closing between the brake cylinder chamber 1 and the auxiliary air cylinder chamber can be realized. Then, through the pressure action of the brake cylinder chamber II and the pre-control chamber I on the composition of the C piston, the force of the composition of the C piston acts on the composition of the main valve body. By changing the active displacement of the composition of the main valve body, the brake cylinder chamber I and the Communication between auxiliary air cylinder chambers. As the pressure of the pre-control chamber I rises, the jump action of the C piston component ends, and then the C piston component is affected by the brake cylinder II, so that the C piston component acts on the balance mechanism.
  • the rising pressure of the pre-control chamber II acts on the Cv piston composition, so that the Cv piston composition also acts on the balance mechanism, and overcomes the force of the C piston composition through the balance mechanism, so that the C piston composition acts on the main valve body composition again, and the connection Brake cylinder chamber I and auxiliary air cylinder chamber.
  • the pressures of the brake cylinder chamber and the pre-control chamber are gradually balanced (the pressures of the two chambers are not necessarily the same, but are balanced between the fulcrums of the balance mechanism through the force of the brake chamber and the pre-control chamber). Then the C piston composition and the Cv piston composition act together on the active force on the balance mechanism to achieve balance.
  • the C piston composition dominates the balance mechanism, and the supporting effect of the C piston composition on the main valve body composition decreases, and finally disappears.
  • the two deviate from each other, and the main valve body composition
  • the brake cylinder is connected to the atmosphere to realize pressure relief.
  • the main valve body consists of a main valve seat 102 , a main valve stem 103 , a filter 104 , an exhaust port 105 , a valve stem return spring 106 , a valve cover 107 and a sealing ring 108 .
  • the main valve body 101 is connected with the valve cover 107, and the valve cover 107 clamps the main valve seat 102 in the main valve body, and a sealing ring 108 is provided between the valve cover and the main valve body to ensure the tightness of the inner chamber.
  • the main valve seat 102 is fixed between the brake cylinder chamber I and the auxiliary air cylinder chamber R, and the middle part of the main valve rod 103 is located at the through hole of the main valve seat 102, that is, between the brake cylinder chamber I and the auxiliary air cylinder chamber R At the communication channel of the main valve stem 103, a sealing ring 108 is provided in the middle of the main valve stem. Closure or communication between cylinder chambers.
  • the main valve seat 102 is provided with a radial inlet, and a filter 104 is arranged at the radial inlet, through which the air entering the auxiliary air cylinder chamber is filtered.
  • a sealing ring is arranged between the main valve seat and the main valve body to realize the sealing between the brake cylinder chamber I and the auxiliary air cylinder chamber R.
  • a valve stem return spring 106 is arranged between the left end of the main valve stem 103 and the bonnet as a valve stem return member, through the elastic force of the valve stem return spring, the main valve stem can be automatically reset to close the passage.
  • a sealing ring is arranged between the left end of the main valve stem and the valve cover to ensure the sealing of the auxiliary air cylinder chamber when the main valve stem is displaced.
  • the right end of the main valve rod 103 is inserted into the release valve rod, and by releasing the support of the valve rod, the main valve rod can overcome the elastic force and communicate with the channel.
  • the right end of the main valve stem 103 is provided with an air inlet, the air inlet communicates with the hollow cavity in the main valve stem 103, the hollow cavity communicates with the atmospheric channel I EX1 on the valve cover, and the atmospheric channel I communicates with the atmospheric channel II EX2 on the main valve body Connected, the atmospheric channel II communicates with the air exhaust port on the main valve body, and the air exhaust port 105 is a spiral air exhaust port.
  • the right end of the main valve stem is provided with a sealing ring. When the main valve stem and the relief valve stem are sleeved, the seal ring will block the gap between the main valve stem and the relief valve stem. When the main valve stem and the relief valve stem are sleeved When disengaging, the brake cylinder 1 realizes communication with the atmosphere and performs a mitigation effect.
  • the pressure in the pre-control room drops, and the C piston leaves the main valve stem.
  • the pressure air of the brake cylinder passes through the air inlet at the right end of the main valve stem, enters the hole in the middle of the double rubber valve stem, passes through the radial hole of the valve cover, and passes through the exhaust air. Exhaust to atmosphere.
  • the pressure air in the brake cylinder chamber II and C2 chamber is exhausted along the relief passage of the brake cylinder chamber I through the throttling shrinkage hole.
  • the function of the shrinkage hole is to prevent the C piston from closing the relief valve port too quickly, resulting in pressure relief in the brake cylinder. Not thorough.
  • C piston composition comprises piston shrinkage hole 201, C piston 202, relief valve rod 203, small spring seat 204, template I 205, large spring seat 206, jump spring 207, limit nut 208, jump piston 209 , C piston rod 211, jump spring seat 213 jump chamber Y.
  • the left end of relief valve stem 203 is fixed with C piston 202, and the movable sleeve at the right end of relief valve stem 203 is provided with jumping piston 209, and the limit nut 208 on the right side of relief valve stem 203 is fixed on the right side of jumping piston 209 as a stopper, and C piston Diaphragm 1 205 is provided between 202, jumping up piston 209 and jumping up spring seat 213.
  • the C piston, the jumping piston and diaphragm I are used for bearing pressure. Through the pressure difference on both sides, the action position of the relief valve stem is changed.
  • the limit nut is used to limit the movement position of the jumping piston, that is, the jumping piston moves to the right. Sliding to the stop nut is blocked.
  • a small spring seat 204 and a large spring seat 206 are installed on the jump piston 209, and a jump spring 207 is arranged between the small spring seat 204 and the large spring seat 206 as a jumping reset member.
  • the jumping piston can relatively relieve the axial slippage of the valve rod, and the jumping spring 207 provides an elastic obstacle for relieving the relative slippage between the valve rod 203 and the jumping piston.
  • the left end of the relief valve stem is sleeved and matched with the right end of the main valve stem, which can realize actions such as support, sleeve separation and the like.
  • a sealing ring is provided between the left end of the relief valve stem and the main valve body, which is used to ensure the sealing of the brake cylinder chamber 1 when the relief valve stem shifts.
  • the right end of the relief valve rod 203 is fixedly connected with the C piston rod 211, and the C piston rod 211 is in contact with the upper end of the balance beam, and the C piston rod extends the relief valve rod so that the force of the relief valve rod acts on the balance beam.
  • Relief valve rod 203, C piston 202, jumping piston 209, diaphragm I 205 and jumping spring seat 213 form a jumping chamber Y, and the effect area of the jumping chamber Y on C piston 202 is smaller than that of the jumping piston 209, that is, the jumping chamber
  • the pressure on the jumper piston is greater than that on the C piston.
  • the jump spring seat is fixed between the main valve body and the follower valve body, the jump chamber Y communicates with the pre-control chamber I through the piston shrinkage hole 201 on the jump spring seat 213, and the left side of the C piston 202 is the brake cylinder chamber II.
  • the pressure in the pre-control chamber I can be transmitted to the jump chamber, and the action position of the relief valve stem can be changed through the different forces exerted by the jump chamber on the C piston and the jump piston.
  • the pressure of the brake cylinder chamber II acts on the left side of the C piston, which can also change the action position of the release valve stem.
  • Jump function When the pressure in the pre-control chamber rises, it enters the jump chamber through the shrinkage hole, pushes the C piston, and drives the release valve seat to lift the main valve stem in the main valve body, and the pressure of the auxiliary air cylinder enters the brake cylinder, forming an initial jump. At this time, the balance beam moves away from the fulcrum of the knife edge of the adjustment block, that is, the pressure of the brake cylinder is not controlled by the follow-the-weight mechanism.
  • the jumping piston drives the small spring seat to compress the jumping spring until the jumping piston is blocked by the stop nut, and the jumping action ends.
  • the jumping piston and the C piston form a rigid connection, only the pressure of the brake cylinder on the left side of the C piston acts on the piston rod, and the pressure of the pre-control chamber II is balanced through the balance beam.
  • Cv piston composition comprises Cv piston 301, relief spring 302, Cv spring seat 303, Cv piston rod 304, diaphragm II 305 and diaphragm seat 306.
  • the left end of the Cv piston 301 is in contact with the diaphragm II 305, and the diaphragm II 305 is located on the diaphragm seat 306, and the diaphragm seat is fixed between the main valve body and the valve body with the weight.
  • the left side of the diaphragm II 305 blocks the pre-control chamber II, the pressure of the pre-control chamber II acts on the diaphragm II, and then transmits it to the Cv piston.
  • the right end Cv piston rod 304 of the Cv piston 301 is fixedly connected, and the Cv piston rod 304 acts on the balance beam.
  • a Cv spring seat 303 is fixed on the valve body with weight, and a Cv piston 301 is mounted on the Cv spring seat 303.
  • a relief spring 302 is arranged between the right end of the Cv piston 301 and the Cv spring seat 303 as a Cv reset member. The relief valve is used to maintain the automatic reset of the Cv piston and provide an elastic obstacle for the movement of the Cv piston.
  • Balance mechanism comprises torsion spring 210 and balance beam 212, and C piston rod is connected with the upper end of balance beam by torsion spring.
  • the right end of the C piston rod is in contact with the upper end of the balance beam 212
  • the middle part of the balance beam 212 is in contact with the fulcrum of the follower mechanism assembly
  • the lower end of the balance beam 212 is in contact with the right end of the Cv piston rod 304.
  • the follower mechanism includes a follower piston rod 401, a connecting shaft 402, an adjustment block 403, and an adjustable spring Seat 404, adjusting nut 405, guide chute 406, valve body 407 with weight, adjustment spring 408, piston 409 with weight and valve cover 410 with weight.
  • the bottom of the load-bearing valve body 407 is connected with the load-bearing valve cover 410, and an empty-load truck signal chamber is opened on the load-load valve cover. Acts on the weighted piston.
  • the heavy piston 409 is connected with the heavy piston rod 401, the heavy piston rod 401 is connected with the connecting shaft 402, and the heavy piston rod 401 is connected with the vertically movable adjustment block 403, so that the heavy piston, the heavy piston rod and the adjustment The blocks are connected as a whole, enabling synchronous movement.
  • An adjustable spring seat 404 is threaded on the adjustable nut 405, and an adjustable spring 408 is arranged between the adjustable spring seat 404 and the accompanying heavy piston 409 as an accompanying repeater positioner.
  • the adjustable spring seat can adjust the position on the heavy piston rod by rotating relative to the adjusting nut, thereby adjusting the degree of tightness of the adjusting spring.
  • the adjusting block 403 can move vertically, and the pressure acting on the heavy piston can be transformed into different positions of the adjusting block, changing the balance beam position of the lever fulcrum.
  • the working principle of the present invention is as follows.
  • the intake valve is closed under the action of the compression spring, cutting off the passage between the auxiliary air cylinder and the brake cylinder I.
  • the balance beam is mechanically connected to the C piston rod, and under the action of the torsion spring, it is kept apart from the knife edge fulcrum of the adjustment block.
  • the pressure from the auxiliary air cylinder enters the left auxiliary air cylinder chamber R, the load-related control pressure is applied to the follower piston, all working parts are at the initial position, and the fulcrum position of the follower mechanism is proportional to the vehicle mass.
  • the pressure entering the brake cylinder must overcome the friction force of the brake cylinder piston cylinder wall, the piston return spring and the inertia of the brake device, and then be applied to the brake shoe to generate braking force.
  • the jump device allows the pressure in the brake cylinder to increase rapidly.
  • the pre-control pressure flows to the pre-control chamber I Cv1 through the throttle hole, and then reaches the jump chamber Y through the throttle shrinkage hole, pushes the C piston to move left, overcomes the resistance of the main valve stem spring, pushes the main valve stem open, and comes from the auxiliary air cylinder chamber R
  • the compressed air quickly flows into the brake cylinder chamber I C1, and slowly flows to the brake cylinder chamber II C2 on the left side of the C piston through the main valve shrinkage hole. Since the load-carrying device is inactive at this stage, the intake valve opens independently of the load.
  • the jump piston moves to the right and contacts the limit nut, and the jump action ends.
  • the rising pressure of the brake cylinder chamber I enters the brake cylinder chamber II through the shrinkage hole, that is, the left side of the C piston, and pushes the C piston, the relief valve rod, and the C piston rod to move to the right, and drives the balance beam to contact the knife-edge fulcrum of the adjustment block to form a fulcrum, and then
  • the heavy device works, and at the same time, the Cv piston moves to the right under the pressure of the pre-control chamber II to resist the force generated by the brake cylinder.
  • the rising pressure of the pre-control chamber makes the Cv piston move to the right, and the balance beam rotates around the knife-edge fulcrum of the adjustment block, resisting the action of the brake cylinder chamber II pressure on the C piston.
  • the balance beam drives the C piston rod, relief valve rod, and main valve rod to open the intake valve, and the compressed air from the auxiliary air cylinder chamber R flows into the brake cylinder chamber I again, and reaches the brake cylinder chamber II through the throttle shrinkage hole , the pressure in the brake cylinder chamber II increases.
  • the intake valve turns to the hold position.
  • the pressure flowing into chamber II of the brake cylinder also increases at the C piston.
  • the pressure in the brake cylinder chamber reaches a value at the same time, which keeps the balance beam in a balanced state corresponding to the pressure holding position, and the intake valve and exhaust valve are closed.
  • the torque generated by the C-piston dominates the balance beam due to the reduced pressure in the pilot chamber.
  • the C piston pushes the balance beam to rotate towards the blade of the adjustment block, and at the same time pushes the release valve rod, and the C piston rod moves to the right.
  • Channel I EX1, atmospheric channel II EX2 on the main valve body, and spiral exhaust port are exhausted to the atmosphere.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

本发明公开了一种中继阀，包括阀体，阀体内设有主阀体组成、C活塞组成、Cv活塞组成、预控室、制动缸室和副风缸室，活动的主阀体组成位于制动缸室与副风缸室之间的连通通道处，活动的C活塞组成隔挡在制动缸室与预控室之间，活动的Cv活塞组成一端被预控室进行隔挡，C活塞组成的一端与主阀体组成接触，C活塞组成的另一端与平衡机构的一端接触，Cv活塞组成的另一端与平衡结构的另一端接触。本发明的有益效果：跟随性更好，灵敏度更高，随着车辆载重的变化，制动缸压力成比例变化。

Description

一种中继阀 技术领域
本发明涉及铁道车辆空重车技术领域，具体为一种中继阀。
背景技术
轨道车辆制动系统为了使运行的车辆可靠停车，通常需要根据车辆的载重来分配制动力。制动力过大会引起车辆滑行，导致车辆轮对擦伤。制动力过小更会导致行车安全。
目前国内铁道货车制动系统通常采用间接测量车辆载重，加上限压阀方式来分配制动力，达到车辆可靠调速、停车的目的。
由于间接测量车辆载重精度相对较差，更高精度的车辆载重测量是直接称重，直接称重后输出与车辆载重相匹配的空气压力，该空气压力参与控制制动力，以提高制动缸压力控制精度，防止车辆滑行和制动力不足，保障铁路行车安全。
发明内容
本发明的目的在于：本发明提供了一种中继阀，解决了现有中继阀跟随性能差的问题。
本发明目的通过下述技术方案来实现：
一种中继阀，包括阀体，阀体内设有主阀体组成、C活塞组成、Cv活塞组成、随重机构组成、预控室、制动缸室和副风缸室，活动的主阀体组成位于制动缸室与副风缸室之间的连通通道处，活动的C活塞组成隔挡在制动缸室与预控室之间，活动的Cv活塞组成一端被预控室进行隔挡，C活塞组成的一端与主阀体组成接触，C活塞组成的另一端与平衡机构的一端接触，Cv活塞组成的另一端与平衡结构的另一端接触。
进一步的，所述的主阀体组成与C活塞组成之间套设配合，主阀体组成的套设处设有进风口，进风口与主阀体组成内部的中空腔连通，中空腔与阀体内的大气通道连通，大气通道与阀体上的排风口连通。
进一步的，所述的预控室包括预控室I和预控室II，预控室I与C活塞组成作用，预控室II与Cv活塞组成作用，制动缸室包括制动缸室I和制动缸室II，制动缸室I与主阀体组成作用，制动缸室II与C活塞组成作用，制动缸室I与制动缸室II之间通过活塞缩孔连通。
进一步的，所述的主阀体组成包括轴向活动的主阀杆，主阀杆的左端与阀体之间设有阀杆复位件，主阀杆的中部位于制动缸室与副风缸室之间的连通通道处，主阀杆的右端与C活塞组成接触。
进一步的，所述的主阀体组成包括主阀座，主阀座固定在制动缸室与副风缸室之间，主阀杆的中部位于主阀座的通孔处。
进一步的，所述的主阀座上设有径向进口，径向进口处设有过滤器。
进一步的，所述的阀杆复位件为阀杆复位簧。
进一步的，所述的阀体与阀盖连接，阀盖将主阀座卡设在阀体内。
进一步的，所述的主阀杆的右端设有进风口，主阀杆的右端与C活塞组成套设配合，进风口与主阀杆内的中空腔连通，中空腔与阀体内的大气通道连通，大气通道与阀体上的排风口连通。
进一步的，所述的排风口为螺旋排风口。
进一步的，所述的C活塞组成包括缓解阀杆，缓解阀杆的左端固定有C活塞，缓解阀杆的右端活动套设有跃升活塞，缓解阀杆上固定位于跃升活塞右侧的限位件，C活塞、跃升活塞均与跃升簧座之间设有膜板I，跃升活塞与跃升簧座之间设有跃升复位件，缓解阀杆、C活塞、跃升活塞、膜板I和跃升簧座之间形成跃升室，跃升室与预控室连通，C活塞的左侧为制动缸室，跃升室对C活塞与跃升活塞相比作用面积较小。
进一步的，所述的跃升室通过活塞缩孔与预控室连通。
进一步的，所述的缓解阀杆上固定有小弹簧座，跃升簧座上固定有大弹簧座，小弹簧座与大弹簧座之间设有跃升复位件。
进一步的，所述的跃升复位件为跃升簧。
进一步的，所述的限位件为限位螺母，限位螺母与缓解阀杆连接。
进一步的，所述的缓解阀杆与C活塞杆固定连接，C活塞杆与平衡机构接触。
进一步的，所述的Cv活塞组成包括Cv活塞，Cv活塞的左端与膜板II接触，膜板II设在膜板座上，膜板II的左侧隔挡预控室，Cv活塞的右端与阀体之间设有Cv复位件。
进一步的，所述的阀体上固定有Cv弹簧座，Cv活塞穿设在Cv弹簧座上，Cv活塞与Cv弹簧座之间设有Cv复位件。
进一步的，所述的Cv复位件为缓解簧。
进一步的，所述的Cv活塞与Cv活塞杆连接，Cv活塞杆与平衡机构接触。
进一步的，所述的平衡机构包括平衡梁，缓解阀杆的右端与平衡梁的上端作用，平衡梁的中部与随重机构组件的支点接触，平衡梁的下端与Cv活塞的右端作用。
进一步的，所述的平衡梁的上端通过扭簧与C活塞杆连接。
进一步的，所述的阀体内设有空重车信号室，随重机构组成包括随重活塞，随重活塞的下端隔挡空重车信号室，随重活塞与随重活塞杆连接，随重活塞与阀体之间设有随重复位件，随重活塞杆与竖向活动的调节块连接，调节块上设有支点。
进一步的，所述的随重活塞杆与连接轴连接，连接轴与调节块连接。
进一步的，所述的随重活塞杆与调节螺母滑动套设，调节螺母上螺纹连接有可调弹簧座，可调弹簧座与随重活塞之间设有随重复位件。
进一步的，所述的调节块设在竖向布置的导向滑槽上。
进一步的，所述的随重复位件为调节弹簧。
本发明的有益效果：跟随性更好，灵敏度更高，随着车辆载重的变化，制动缸压力成比例变化。
前述本发明主方案及其各进一步选择方案可以自由组合以形成多个方案，均为本发明可采用并要求保护的方案；且本发明，(各非冲突选择)选择之间以及和其他选择之间也可以自由组合。本领域技术人员在了解本发明方案后根据 现有技术和公知常识可明了有多种组合，均为本发明所要保护的技术方案，在此不做穷举。
附图说明
图1是本发明的外观结构示意图。
图2是本发明的主阀体组成的结构示意图。
图3是本发明的C活塞组成的结构示意图。
图4是本发明的Cv活塞组成的结构示意图。
图5是本发明的随重机构组成的结构主视图。
图6是本发明的随重机构组成的结构侧视图。
图7是本发明的初始位的结构示意图。
图8是本发明的跃升位的结构示意图。
图9是本发明的制动位的结构示意图。
图10是本发明的保压位的结构示意图。
图11是本发明的缓解位的结构示意图。
图中：Cv1-预控室I，Cv2-预控室II，C1-制动缸室I，C2-制动缸室II，R-副风缸室，T-空重车信号室，EX1-大气通道I，EX2-大气通道II。
101-主阀体，102-主阀座，103-主阀杆，104-过滤器，105-排风口，106-阀杆复位簧，107-阀盖，108-密封圈。
201-活塞缩孔，202-C活塞，203-缓解阀杆，204-小弹簧座，205-膜板I，206-大弹簧座，207-跃升簧，208-限位螺母，209-跃升活塞，210-扭簧，211-C活塞杆，212-平衡梁，213-跃升簧座，Y-跃升室。
301-Cv活塞，302-缓解簧，303-Cv弹簧座，304-Cv活塞杆，305-膜板II，306-膜板座。
401-随重活塞杆，402-连接轴，403-调节块，404-可调弹簧座，405-调节螺母，406-导向滑槽，407-随重阀体，408-调节弹簧，409-随重活塞，410-随重阀盖，411-支点。
具体实施方式
下列非限制性实施例用于说明本发明。
实施例1：
参考图1所示，一种中继阀，包括阀体，阀体包括主阀体101和随重阀体407，两个阀体分块之间通过螺栓固定连接。主阀体内设有主阀体组成、预控室、制动缸室和副风缸室R，随重阀体内设有随重机构组成，主阀体与随重阀体之间夹持有C活塞组成、Cv活塞组成。
预控室包括预控室I Cv1和预控室II Cv2，预控室I Cv1与C活塞组成作用，预控室II Cv2与Cv活塞组成作用，制动缸室包括制动缸室I C1和制动缸室II C2，制动缸室I C1与主阀体组成作用，制动缸室II C2与C活塞组成作用，制动缸室I C1与制动缸室II C2之间通过活塞缩孔连通。
活动的主阀体组成位于制动缸室I与副风缸室R之间的连通通道处，通过主阀体组成的活动位移，能够实现制动缸室I与副风缸室之间的连通或关闭。活动的C活塞组成隔挡在制动缸室II与预控室I之间，C活塞组成的一端与主阀体组成接触，C活塞组成的另一端与平衡机构的一端接触，活动的Cv活塞组成一端被预控室进行隔挡，Cv活塞组成的另一端与平衡结构的另一端接触。
主阀体组成与C活塞组成之间套设配合，主阀体组成的套设处设有进风口，进风口与主阀体组成内部的中空腔连通，中空腔与阀体内的大气通道连通，大气通道与阀体上的排风口连通。
通过主阀体组成的自身作用，能够实现制动缸室I与副风缸室之间的关闭。然后通过制动缸室II与预控室I对C活塞组成的压力作用，C活塞组成的作用力作用在主阀体组成上，通过改变主阀体组成的活动位移，实现制动缸室I与副风缸室之间的连通。随着预控室I压力的上升，C活塞组成的跃升作用结束，然后C活塞组成受制动缸II作用，使得C活塞组成作用在平衡机构上。上升的预控室II压力作用在Cv活塞组成上，使得Cv活塞组成也作用在平衡机构上，并通过平衡机构克服C活塞组成的作用力，使得C活塞组成重新作用在主阀体组成上，连通制动缸室I与副风缸室。
在制动完成后，制动缸室和预控室的压力逐渐平衡(两腔室压力不一定相 同，而是通过制动室力、预控室力在平衡机构支点之间平衡)。则C活塞组成和Cv活塞组成共同作用在平衡机构上的作用力实现平衡。在缓解时，由于预控室压力下降，C活塞组成在平衡机构上占主导地位，C活塞组成对主阀体组成的顶撑作用减小，最后才消失，同时两者相互背离，主阀体组成与C活塞组成之间的套设作用消失，则将制动缸连通大气，实现缓解泄压。
参考图2所示，主阀体组成包括主阀座102、主阀杆103、过滤器104、排风口105、阀杆复位簧106、阀盖107和密封圈108。
主阀体101与阀盖107连接，阀盖107将主阀座102卡设在主阀体内，阀盖与主阀体之间设有密封圈108，用于保证内部腔室的密封性。主阀座102固定在制动缸室I与副风缸室R之间，主阀杆103的中部位于主阀座102的通孔处，即制动缸室I与副风缸室R之间的连通通道处，主阀杆103的中部设有密封圈108，主阀杆能够轴向活动，通过主阀杆中部的密封圈与主阀座接触或脱离，实现制动缸室I与副风缸室之间的关闭或连通。
主阀座102上设有径向进口，径向进口处设有过滤器104，通过过滤器对进入副风缸室的空气进行过滤。主阀座与主阀体之间设有密封圈，用于实现制动缸室I与副风缸室R之间的密封。
主阀杆103的左端与阀盖之间设有阀杆复位簧106作为阀杆复位件，通过阀杆复位簧的弹力作用，保证主阀杆能够自动复位封闭通道。主阀杆的左端与阀盖之间设有密封圈，保证主阀杆在位移时，副风缸室的密封性。主阀杆103的右端套入缓解阀杆内，通过缓解阀杆的顶撑，主阀杆能够克服弹力将通道连通。
主阀杆103的右端设有进风口，进风口与主阀杆103内的中空腔连通，中空腔与阀盖上的大气通道I EX1连通，大气通道I与主阀体上的大气通道II EX2连通，大气通道II与主阀体上的排风口连通，排风口105为螺旋排风口。主阀杆的右端设有密封圈，当主阀杆与缓解阀杆套设作用的时候，密封圈对主阀杆与缓解阀杆之间的间隙进行封堵，当主阀杆与缓解阀杆套设脱离时，制动缸I实现与大气连通，进行缓解作用。
制动时，预控室I压力上升，推动C活塞组成顶开主阀杆103，副风缸的压力空气经过粉末冶金过滤器后到达副风缸室R，再经过开放的阀口到达制动缸室I C1室后进入制动缸，形成制动。同时制动缸室I C1室中的压力空气通过节流缩孔到达制动缸室II C2，与增加的预控室II Cv2压力通过平衡梁形成比例关系。
缓解时，预控室压力下降，C活塞组成离开主阀杆，制动缸压力空气经过主阀杆右端的进风口，进入双胶阀杆中间的孔，并经过阀盖径向孔，经排风口排向大气。同时制动缸室II C2室的压力空气经节流缩孔沿制动缸室I缓解通路排大气，缩孔的作用是防止C活塞组成过快关闭缓解阀口，导致制动缸中压力缓解不彻底。
参考图3所示，C活塞组成包括活塞缩孔201、C活塞202、缓解阀杆203、小弹簧座204、模板I 205、大弹簧座206、跃升簧207、限位螺母208、跃升活塞209、C活塞杆211、跃升簧座213跃升室Y。
缓解阀杆203的左端固定有C活塞202，缓解阀杆203的右端活动套设有跃升活塞209，缓解阀杆203上固定位于跃升活塞209右侧的限位螺母208作为限位件，C活塞202、跃升活塞209均与跃升簧座213之间设有膜板I 205。C活塞、跃升活塞和膜板I用于承压，通过两侧的压差作用，改变缓解阀杆的作用位置，限位螺母用于对跃升活塞的运动位置进行限位，即跃升活塞向右滑移至限位螺母处被阻挡。
跃升活塞209上安装有小弹簧座204和大弹簧座206，小弹簧座204与大弹簧座206之间设有跃升簧207作为跃升复位件。跃升活塞能够相对缓解阀杆轴向滑移，跃升簧207为缓解阀杆203和跃升活塞之间的相对滑移提供弹力障碍。
缓解阀杆的左端与主阀杆的右端套设配合，能够实现顶撑、套设脱离等动作。缓解阀杆的左端与主阀体之间设有密封圈，用于在缓解阀杆移位的时候，保证制动缸室I的密封性。缓解阀杆203的右端与C活塞杆211固定连接，C活塞杆211与平衡梁的上端接触，C活塞杆对缓解阀杆进行延长，使得缓解阀杆的力作用在平衡梁上。
缓解阀杆203、C活塞202、跃升活塞209、膜板I 205和跃升簧座213之间 形成跃升室Y，跃升室Y对C活塞202与跃升活塞209相比作用面积较小，即跃升室内的压力作用在跃升活塞比作用在C活塞上的大。
跃升簧座固定在主阀体与随重阀体之间，跃升室Y通过跃升簧座213上的活塞缩孔201与预控室I连通，C活塞202的左侧为制动缸室II。预控室I内的压力能够传递至跃升室，通过跃升室对C活塞和跃升活塞的不同作用力，改变缓解阀杆的作用位置。制动缸室II的压力作用在C活塞的左侧，同样能够改变缓解阀杆的作用位置。
缓解阀杆传递作用在C活塞左侧的制动缸室II压力，并通过C活塞杆传递到平衡梁，去平衡预控室II对Cv活塞组成的压力。
跃升功能：当预控室压力上升，通过缩孔进入跃升室，推动C活塞，带动缓解阀座顶开主阀体组成中的主阀杆，副风缸压力进入制动缸，形成初跃升。此时，平衡梁向远离调节块刀口支点的方向运动，也即制动缸压力不受随重机构控制。
随着预控室压力的增加，作用在跃升活塞的力增大到能克服跃升簧的作用力时，跃升活塞带动小弹簧座压缩跃升簧，直到跃升活塞被限位螺母挡住，跃升作用结束。此时跃升活塞与C活塞组成形成一个刚性连接，只有C活塞左侧的制动缸压力作用在活塞杆上，通过平衡梁平衡预控室II的压力。
参考图4所示，Cv活塞组成包括Cv活塞301、缓解簧302、Cv弹簧座303、Cv活塞杆304、膜板II 305和膜板座306。Cv活塞301的左端与膜板II 305接触，膜板II 305设在膜板座306上，膜板座固定在主阀体与随重阀体之间。膜板II 305的左侧隔挡预控室II，预控室II的压力作用在膜板II上，然后传递给Cv活塞。Cv活塞301的右端Cv活塞杆304固定连接，Cv活塞杆304作用在平衡梁上。
随重阀体上固定有Cv弹簧座303，Cv活塞301穿设在Cv弹簧座303上，Cv活塞301的右端与Cv弹簧座303之间设有缓解簧302作为Cv复位件。缓解阀用于保持Cv活塞的自动复位，为Cv活塞的移动提供弹力障碍。
平衡机构包括扭簧210和平衡梁212，C活塞杆通过扭簧与平衡梁的上端连 接。C活塞杆的右端与平衡梁212的上端接触，平衡梁212的中部与随重机构组件的支点接触，平衡梁212的下端与Cv活塞杆304的右端接触。通过平衡两端的作用力，实现Cv活塞与C活塞之间的平衡传力。
参考图5和6所示，主阀体与随重阀体407之间设有空重车信号室T，随重机构组成包括随重活塞杆401、连接轴402、调节块403、可调弹簧座404、调节螺母405、导向滑槽406、随重阀体407、调节弹簧408、随重活塞409和随重阀盖410。
随重阀体407的底部与随重阀盖410连接，随重阀盖上开设有空重车信号室，随重活塞409的下端隔挡空重车信号室T，空重车信号室内的压力作用在随重活塞上。随重活塞409与随重活塞杆401连接，随重活塞杆401与连接轴402连接，随重活塞杆401与竖向活动的调节块403连接，实现将随重活塞、随重活塞杆和调节块连接为一个整体，能够实现同步运动。
随重活塞杆401与调节螺母405滑动套设，调节螺母405上螺纹连接有可调弹簧座404，可调弹簧座404与随重活塞409之间设有调节弹簧408作为随重复位件。可调弹簧座能够通过相对调节螺母旋转，实现在随重活塞杆上的位置调整，从而调整调节弹簧的松紧程度。
调节块403上设有支点，调节块403设在竖向布置的导向滑槽406上，调节块能够竖向活动，作用在随重活塞上的压力，转变为调节块不同的位置，改变平衡梁的杠杆支点位置。
空车时，来自传感阀的压力经过随重阀盖进入随重活塞下方，但不足以推动随重活塞运动，支点不变化，输出为空车压力。当信号压力足以推动随重活塞运动，支点位置发生变化，制动缸压力也随之变化。
本发明的工作原理如下。
参考图7所示，初始位(缓解位)：
所有的工作部件都在起始位置。进气阀在压缩弹簧的作用下关闭，切断副风缸和制动缸I之间的通路。平衡梁机械地连接到C活塞杆上，并在扭簧的作用下，保持与调节块的刀口支点分开。
来自副风缸的压力到左边的副风缸室R中，负载相关的控制压力施加到随重活塞上，所有工作零件都在起始位置，随重机构的支点位置与车辆质量成比例。
参考图8所示，跃升位：
当制动开始时，进入到制动缸压力必须克服制动缸活塞缸壁摩擦力、活塞复原弹簧和制动装置的惯性，然后施加到闸瓦，并产生制动力。
跃升装置可使制动缸内的压力迅速增加。
预控制压力通过节流孔流向预控室I Cv1，再经过节流缩孔到达跃升室Y，推动C活塞左移，克服主阀杆弹簧的阻力，顶开主阀杆，来自副风缸室R的压缩空气快速流入制动缸室I C1，并通过主阀缩孔缓慢流向C活塞左边的制动缸室II C2。由于随重装置在此阶段无效，所以进气阀打开时与负载无关。
当预控室压力上升到足以压缩跃升簧时，跃升活塞向右移动与限位螺母接触后，跃升作用结束。上升的制动缸室I压力通过缩孔进入制动缸室II，即C活塞左侧，推动C活塞、缓解阀杆、C活塞杆右移，带动平衡梁接触调节块刀口支点形成支点，随重装置起作用，同时Cv活塞在预控室II压力作用下右移，以抵抗制动缸产生的作用力。
参考图9所示，制动位：
上升的预控室压力使Cv活塞右移，平衡梁绕调节块的刀口支点转动，抵抗制动缸室II压力对C活塞的作用。平衡梁驱动C活塞杆、缓解阀杆、主阀杆，从而打开进气阀，来自副风缸室R的压缩空气再次流入制动缸室I，并通过节流缩孔到达制动缸室II，制动缸室II压力升高。
参考图10所示，保压位：
在每个制动过程完成后，进气阀会转到保压位置。流入制动缸室II的压力也在C活塞处增大。一旦预控室压力上升完成，制动缸室压力同时达到一个值，该值使平衡梁保持在与保压位置相对应的平衡状态，进气阀和排气阀关闭。
参考图11所示，缓解位：
通过降低预控制压力来启动中继阀缓解。
由于预控室压力降低，由C活塞产生的扭矩在平衡梁上占主导地位。C活塞推动平衡梁向调节块的刀刃转动，同时推动缓解阀杆、C活塞杆右移，制动缸室I压力经主阀杆中心孔流到主阀盖，并通过主阀盖上的大气通道I EX1、主阀体上的大气通道II EX2、螺旋排风口，排到大气。
当预控室压力完成下降时，一旦制动缸已经充分排气，使得制动缸室压力达到一个值，在该值下，随重装置的平衡得到恢复，排气阀就再次回到保压位置。一旦中继阀完全缓解，预控制压力完全缓解至零，制动缸以这种方式完全排气。所有工作部件都恢复到图7所示的位置。
前述本发明基本例及其各进一步选择例可以自由组合以形成多个实施例，均为本发明可采用并要求保护的实施例。本发明方案中，各选择例，与其他任何基本例和选择例都可以进行任意组合。
以上所述仅为本发明的较佳实施例而已，并不用以限制本发明，凡在本发明的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本发明的保护范围之内。

Claims (10)

  1. 一种中继阀，包括阀体，其特征在于：所述的阀体内设有主阀体组成、C活塞组成、Cv活塞组成、随重机构组成、预控室、制动缸室和副风缸室(R)，活动的主阀体组成位于制动缸室与副风缸室(R)之间的连通通道处，活动的C活塞组成隔挡在制动缸室与预控室之间，活动的Cv活塞组成一端被预控室进行隔挡，C活塞组成的一端与主阀体组成接触，C活塞组成的另一端与平衡机构的一端接触，Cv活塞组成的另一端与平衡结构的另一端接触。
  2. 根据权利要求1所述的中继阀，其特征在于：所述的主阀体组成与C活塞组成之间套设配合，主阀体组成的套设处设有进风口，进风口与主阀体组成内部的中空腔连通，中空腔与阀体内的大气通道连通，大气通道与阀体上的排风口连通。
  3. 根据权利要求1或2所述的中继阀，其特征在于：所述的主阀体组成包括轴向活动的主阀杆(103)，主阀杆(103)的左端与阀体之间设有阀杆复位件，主阀杆(103)的中部位于制动缸室与副风缸室(R)之间的连通通道处，主阀杆(103)的右端与C活塞组成接触。
  4. 根据权利要求3所述的中继阀，其特征在于：所述的主阀杆(103)的右端设有进风口，主阀杆(103)的右端与C活塞组成套设配合，进风口与主阀杆(103)内的中空腔连通，中空腔与阀体内的大气通道连通，大气通道与阀体上的排风口(105)连通。
  5. 根据权利要求1所述的中继阀，其特征在于：所述的C活塞组成包括缓解阀杆(203)，缓解阀杆(203)的左端固定有C活塞(202)，缓解阀杆(203)的右端活动套设有跃升活塞(209)，缓解阀杆(203)上固定位于跃升活塞(209)右侧的限位件，C活塞(202)、跃升活塞(209)均与跃升簧座(213)之间设有膜板I(205)，跃升活塞(209)与跃升簧座(213)之间设有跃升复位件，缓解阀杆(203)、C活塞(202)、跃升活塞(209)、膜板I(205)和跃升簧座(213)之间形成跃升室(Y)，跃升室(Y)与预控室连通，C活塞(202)的左侧为制动缸室，跃升室(Y)对C活塞(202)与跃升活塞 (209)相比作用面积较小。
  6. 根据权利要求1所述的中继阀，其特征在于：所述的Cv活塞组成包括Cv活塞(301)，Cv活塞(301)的左端与膜板II(305)接触，膜板II(305)设在膜板座(306)上，膜板II(305)的左侧隔挡预控室，Cv活塞(301)的右端与阀体之间设有Cv复位件。
  7. 根据权利要求1所述的中继阀，其特征在于：所述的平衡机构包括平衡梁(212)，缓解阀杆(203)的右端与平衡梁(212)的上端作用，平衡梁(212)的中部与随重机构组件的支点接触，平衡梁(212)的下端与Cv活塞(301)的右端作用。
  8. 根据权利要求7所述的中继阀，其特征在于：所述的平衡梁(212)的上端通过扭簧(210)与缓解阀杆(203)连接。
  9. 根据权利要求1所述的中继阀，其特征在于：所述的阀体内设有空重车信号室(T)，随重机构组成包括随重活塞(409)，随重活塞(409)的下端隔挡空重车信号室(T)，随重活塞(409)与随重活塞杆(401)连接，随重活塞(409)与阀体之间设有随重复位件，随重活塞杆(401)与竖向活动的调节块(403)连接，调节块(403)上设有支点。
  10. 根据权利要求9所述的中继阀，其特征在于：所述的随重活塞杆(401)与调节螺母(405)滑动套设，调节螺母(405)上螺纹连接有可调弹簧座(404)，可调弹簧座(404)与随重活塞(409)之间设有随重复位件。
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