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CN113661343A - Differential pressure valve - Google Patents

Differential pressure valve Download PDF

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Publication number
CN113661343A
CN113661343A CN202080024059.8A CN202080024059A CN113661343A CN 113661343 A CN113661343 A CN 113661343A CN 202080024059 A CN202080024059 A CN 202080024059A CN 113661343 A CN113661343 A CN 113661343A
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CN
China
Prior art keywords
valve
flange portion
valve chamber
differential pressure
valve body
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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.)
Pending
Application number
CN202080024059.8A
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Chinese (zh)
Inventor
藤谷进
沼仓智也
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Hitachi Astemo Ltd
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Hitachi Astemo Ltd
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Filing date
Publication date
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Publication of CN113661343A publication Critical patent/CN113661343A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
    • F16F9/04—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum in a chamber with a flexible wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3488—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features intended to affect valve bias or pre-stress
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/06—Check valves with guided rigid valve members with guided stems

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Fluid-Damping Devices (AREA)
  • Multiple-Way Valves (AREA)
  • Valve Housings (AREA)

Abstract

该差压阀具有：阀室(141)；设置在阀室(141)内的圆形的阀芯(94)；形成于阀室(141)的底部(142)且供一个空气弹簧的空气流入的流入口(106)；形成于阀室(141)的内周面(138)且使空气向另一个空气弹簧流出的流出口(61、71)；以包围流入口(106)的方式形成于阀室(141)的底部(142)的阀座部(104)；以及对阀芯(94)向朝向阀座部(104)的闭阀方向施力的施力部件(95)。阀芯(94)在底部(142)侧具备第一凸缘部(112)。第一凸缘部(112)具备向径向外方突出的多个第一突出部(118)和在第一突出部(118)的周向相反侧的位置向径向内方凹陷的第一凹部(116)。

Figure 202080024059

The differential pressure valve has: a valve chamber (141); a circular valve core (94) arranged in the valve chamber (141); formed at the bottom (142) of the valve chamber (141) and for the inflow of air from an air spring The inflow port (106) of the valve chamber (141); the outflow port (61, 71) formed on the inner peripheral surface (138) of the valve chamber (141) and allowing the air to flow out to the other air spring; A valve seat portion (104) at the bottom portion (142) of the valve chamber (141); and a biasing member (95) for biasing the valve body (94) in the valve closing direction toward the valve seat portion (104). The valve body (94) is provided with a first flange portion (112) on the bottom portion (142) side. The first flange portion (112) includes a plurality of first protrusions (118) that protrude radially outward, and a first protrusion (118) that is recessed radially inward at a position on the opposite side in the circumferential direction of the first protrusions (118). Recess (116).

Figure 202080024059

Description

Differential pressure valve
Technical Field
The present invention relates to a differential pressure valve.
The present application claims priority based on Japanese patent application No. 2019-118690, filed in Japan on 26.6.2019, the contents of which are incorporated herein by reference.
Background
In a railway vehicle, a differential pressure valve that opens and closes a communication passage connecting two air springs provided between a vehicle body and a bogie according to a pressure difference between the two air springs is provided in the communication passage (see, for example, patent documents 1 and 2).
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2002-120723
Patent document 2: japanese laid-open patent publication No. 2012 and 202520
Disclosure of Invention
Problems to be solved by the invention
In the differential pressure valve, it is required to suppress variation in valve opening pressure.
The invention provides a differential pressure valve capable of suppressing the deviation of valve opening pressure.
Means for solving the problems
According to a first aspect of the present invention, a differential pressure valve has: a valve chamber; a circular valve cartridge disposed within the valve chamber; an inflow port formed at a bottom of the valve chamber, through which air of one of the air springs flows; an outlet port formed in an inner peripheral surface of the valve chamber and configured to allow air to flow out to the other air spring; a valve seat portion that is formed at a bottom portion of the valve chamber so as to surround the inlet port and on which the valve body is seated; and a biasing member that biases the valve body in a valve closing direction toward the valve seat portion. The valve body includes a first flange portion extending radially outward from the valve seat portion on the bottom portion side. The first flange portion includes: a plurality of first protrusions protruding radially outward toward an inner circumferential surface of the valve chamber; and a first recess that is recessed radially inward at a position on the opposite side of the first projection in the circumferential direction.
According to a second aspect of the present invention, a differential pressure valve has: a valve chamber; a circular valve cartridge disposed within the valve chamber; an inflow port formed at a bottom of the valve chamber, through which air of one of the air springs flows; an outlet port formed in an inner peripheral surface of the valve chamber and configured to allow air to flow out to the other air spring; a valve seat portion that is formed at a bottom portion of the valve chamber so as to surround the inlet port and on which the valve body is seated; and a biasing member that biases the valve body in a valve closing direction toward the valve seat portion. The valve body includes a first flange portion extending radially outward from the valve seat portion on the bottom portion side, and a second flange portion extending radially outward toward the inner peripheral surface of the valve chamber on a side opposite to the bottom portion. The first flange portion includes a plurality of first protruding portions that protrude radially outward toward the inner peripheral surface of the valve chamber. The second flange portion includes a plurality of second protruding portions protruding radially outward toward the inner peripheral surface of the valve chamber at positions circumferentially offset from the first protruding portions.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the differential pressure valve, variations in valve opening pressure can be suppressed.
Drawings
Fig. 1 is a sectional view showing a differential pressure valve according to a first embodiment of the present invention.
Fig. 2 is a front view showing a valve body of the differential pressure valve according to the first embodiment of the present invention.
Fig. 3 is a bottom view showing a valve body of the differential pressure valve according to the first embodiment of the present invention.
Fig. 4 is a schematic diagram showing a differential pressure valve according to a first embodiment of the present invention and a vehicle connected thereto.
Fig. 5 is a sectional view showing a differential pressure valve according to a second embodiment of the present invention.
Fig. 6 is a plan view showing a valve body of a differential pressure valve according to a second embodiment of the present invention.
Fig. 7 is a front view showing a valve body of a differential pressure valve according to a second embodiment of the present invention.
Fig. 8 is a sectional view showing a differential pressure valve according to a third embodiment of the present invention.
Fig. 9 is a front view showing a valve body of a differential pressure valve according to a third embodiment of the present invention.
Fig. 10 is a bottom view showing a valve body of a differential pressure valve according to a third embodiment of the present invention.
Detailed Description
Embodiments of the present invention are explained based on the drawings.
[ first embodiment ]
A first embodiment will be described with reference to fig. 1 to 4.
As shown in fig. 1, a differential pressure valve 11 of the first embodiment includes a metal casing 12. A first seat 15 and a second seat 16 are provided in two places in parallel on the outer surface of the housing 12. The outer seat surfaces of the first seat 15 and the second seat 16 are disposed on the same plane. The housing 12 is provided with a first valve hole 21 and a second valve hole 22. The first valve hole 21 is provided to penetrate from the first seat 15 to an intermediate predetermined position in the housing 12, and is perpendicular to the seat surface of the first seat 15. The second valve hole 22 is provided to penetrate from the second seat 16 to an intermediate predetermined position in the housing 12, and is provided perpendicular to the seat surface of the second seat 16. The first valve hole 21 is parallel to the second valve hole 22. The first valve hole 21 and the second valve hole 22 have the same shape and the axial positions thereof are aligned.
The first valve hole 21 includes, in order from the innermost side, a first bottom hole portion 31, a first mounting hole portion 32, a first main hole portion 33, and a first threaded hole portion 34. The first bottom hole portion 31, the first mounting hole portion 32, the first main hole portion 33, and the first screw hole portion 34 are arranged coaxially with their center axes aligned. The inner diameter of the first mounting hole portion 32 is larger than the inner diameter of the first bottomed hole portion 31. The inner diameter of the first main hole portion 33 is larger than the inner diameter of the first mounting hole portion 32. The minimum inner diameter of the first threaded hole portion 34 is larger than the inner diameter of the first main hole portion 33. The first threaded hole portion 34 of the first valve hole 21 opens to the outside of the housing 12 at the position of the first seat portion 15.
The second valve hole 22 includes a second bottom hole portion 41, a second mounting hole portion 42, a second main hole portion 43, and a second threaded hole portion 44 in this order from the innermost side. The second bottom hole portion 41, the second mounting hole portion 42, the second main hole portion 43, and the second screw hole portion 44 are arranged coaxially with their center axes aligned. The inner diameter of the second mounting hole portion 42 is larger than the inner diameter of the second bottom hole portion 41. The inner diameter of the second main hole portion 43 is larger than the inner diameter of the second mounting hole portion 42. The minimum inner diameter of the second threaded hole portion 44 is larger than the inner diameter of the first main hole portion 33. The second threaded bore portion 44 of the second valve bore 22 opens out of the housing 12 at the location of the second seat 16.
The housing 12 is formed with a first internal passage 51, a second internal passage 52, a first inflow passage 53, and a second inflow passage 54. The first internal passage 51 has one end opening to the first main hole portion 33 and the other end opening to the second bottom hole portion 41. The second inner passage 52 has one end opening to the second main hole portion 43 and the other end opening to the first bottom hole portion 31. The first inflow passage 53 opens the first bottom hole portion 31 to the outside of the housing 12. The second inflow passage 54 opens the second bottom hole portion 41 to the outside of the housing 12.
The first internal passage 51 includes a first outflow port 61 (outflow port) opening in the first main hole portion 33, a first communication port 62 opening in the second bottom hole portion 41, and a first intermediate passage portion 63 connecting the first outflow port 61 and the first communication port 62. The first outlet 61 is open at a predetermined position at an intermediate position in the axial direction of the first main hole portion 33, and extends in the radial direction of the first main hole portion 33. The first communication port 62 extends in the radial direction of the second bottom hole portion 41. The first intermediate passage portion 63 extends in the axial direction of the first valve hole 21.
The second internal passage 52 includes a second outlet 71 (outlet port) that opens to the second main hole portion 43, a second communication port 72 that opens to the first bottom hole portion 31, and a second intermediate passage portion 73 that connects the second outlet 71 and the second communication port 72. The second outlet port 71 opens at a predetermined position at an intermediate position in the axial direction of the second main hole portion 43, and extends in the radial direction of the second main hole portion 43. The second communication port 72 extends in the radial direction of the first bottomed hole portion 31. The second intermediate passage portion 73 extends in the axial direction of the second valve bore 22.
The differential pressure valve 11 has a first valve structure portion 81 fitted to the first valve hole 21 and a second valve structure portion 82 fitted to the second valve hole 22. The first valve hole 21 and the first valve structure portion 81 constitute a first valve mechanism 83. The second valve hole 22 and the second valve structure portion 82 constitute a second valve mechanism 84. The first valve structure portion 81 and the second valve structure portion 82 have the same configuration. Since the first valve hole 21 and the second valve hole 22 have the same shape, the first valve mechanism 83 and the second valve mechanism 84 have the same configuration.
Here, the first valve structure 81 of the first valve structure 81 and the second valve structure 82 having the same configuration will be described as an example.
The first valve structure portion 81 includes a valve seat member 91, a cover member 92, a gasket 93, and a biasing member 95. The valve seat member 91 is fitted in the first mounting hole portion 32 of the first valve hole 21. The cover member 92 is screwed to the first threaded hole portion 34 of the first valve hole 21. The gasket 93 is interposed between the cover member 92 and the first seat portion 15. The spool 94 is movably disposed in the first main hole portion 33. The biasing member 95 biases the valve body 94 in the direction of the valve seat member 91.
A passage hole 101 extending in the axial direction is formed through the center of the valve seat member 91 in the radial direction. The valve seat member 91 includes an annular base portion 103 and an annular valve seat portion 104 having an outer diameter smaller than the outer diameter of the base portion 103 and projecting outward in the axial direction from one end in the axial direction of the base portion 103. The base portion 103 and the valve seat portion 104 are arranged coaxially with their central axes aligned. The base portion 103 of the valve seat member 91 is fitted in the first mounting hole portion 32 and fixed to the housing 12. The orientation of the seat member 91 at this time is such that the seat portion 104 is disposed on the first main hole portion 33 side of the first valve hole 21. The valve seat portion 104 surrounds the passage hole 101 over the entire circumference. In this way, the valve seat portion 104 is formed in the valve seat member 91 that is separate from the housing 12.
The passage hole 101 of the valve seat member 91 fixed to the first mounting hole portion 32 of the housing 12 communicates with the first bottom hole portion 31, and the first bottom hole portion 31 constitutes an inlet port 106. The valve seat portion 104 is formed so as to surround the inlet port 106. The inlet port 106 of the first valve structure portion 81 including the passage hole 101 of the valve seat member 91 is always communicated with the first inlet passage 53. The seat member 91 of the second valve structure portion 82 is also fixed to the housing 12 in the second mounting hole portion 42. An inlet port 106 formed by the passage hole 101 of the seat member 91 and the second bottom hole 41 is always in communication with the second inlet passage 54.
As shown in fig. 2 and 3, the valve body 94 is circular. Specifically, the valve body 94 has a stepped cylindrical shape. The valve body 94 includes a solid cylindrical shaft portion 111 and a disk-shaped flange portion 112 (first flange portion) extending radially outward from one axial end side of the shaft portion 111. The shaft portion 111 and the flange portion 112 are disposed coaxially with their central axes aligned. A plurality of recesses 116 (first recesses) having the same shape are formed in the outer peripheral portion of the flange portion 112 so as to be recessed radially inward from the cylindrical outermost peripheral surface 114. The recess 116 is formed with an odd number of portions at equal intervals in the circumferential direction of the flange portion 112. Specifically, the recess 116 is formed at three locations at 120 ° intervals in the circumferential direction of the flange 112.
Thus, a projection 118 (first projection) is formed between the recesses 116 adjacent in the circumferential direction on the outer peripheral portion of the flange portion 112 and the recesses 116. The projecting portion 118 (first projecting portion) projects outward in the radial direction of the flange portion 112 from the most recessed position of the recessed portion 116. The projections 118 of the flange portion 112 are all of the same shape. The length of the protruding portion 118 in the circumferential direction of the flange portion 112 is longer than the length in the same direction of the recess portion 116. The protruding portion 118 is formed with an odd number of portions at equal intervals in the circumferential direction of the flange portion 112. Specifically, the protruding portion 118 is formed at three locations at 120 ° intervals in the circumferential direction of the flange portion 112.
An annular flange base end portion 121 is formed between the plurality of projections 118 of the flange portion 112 and the shaft portion 111. The plurality of projections 118 project radially outward from the flange base end portion 121. As shown in fig. 1, the flange base end portion 121 has an outer diameter larger than the outer diameter of the valve seat portion 104 of the valve seat member 91. In other words, the minimum outer diameter of the flange portion 112 is larger than the outer diameter of the valve seat portion 104. Therefore, the maximum outer diameter of the flange portion 112, that is, the maximum outer diameter of the valve body 94 is also larger than the outer diameter of the seat portion 104. The maximum outer diameter of the flange portion 112 is slightly smaller than the inner diameter of the first main hole portion 33.
The valve body 94 is inserted into the first main hole portion 33 in such a direction that the flange portion 112 is on the seat portion 104 side. In this state, the valve body 94 can be seated on the seat portion 104. The valve body 94 has a disc-shaped seating body 123 at the radial center of the end of the flange portion 112 on the side opposite to the side from which the shaft portion 111 projects. The portion of the valve body 94 seated on the seat portion 104 is constituted by the seating body 123. In other words, the seating body 123 constitutes the flange base end portion 121. The valve body 124 is formed by a portion of the valve body 94 other than the seating body 123. The valve main body 124 is made of a material different from that of the seating body 123. For example, the seating body 123 is made of synthetic resin, and the valve body 124 is made of metal. The valve main body 124 constitutes the entire portion of the shaft portion 111 on the side protruding from the flange portion 112, the portion of the shaft portion 111 that overlaps the flange portion 112 in the axial direction, the portion of the flange portion 112 on the side protruding from the shaft portion 111, and the portion on the radially outer side of the flange portion 112. The valve body 124 is integrally formed.
As shown in fig. 3, an odd number of portions are formed in the outer peripheral portion of the flange portion 112 at the recess 116 and the projection 118, respectively. Therefore, the recessed portion 116 is provided at a position opposite to 180 degrees in the circumferential direction of each flange portion 112 with respect to all the protruding portions 118. In other words, the flange portion 112 includes a plurality of protruding portions 118 protruding radially outward and a recess portion 116 recessed radially inward at a position on the opposite side of each of the plurality of protruding portions 118 in the circumferential direction of the flange portion 112.
As shown in fig. 1, the cover member 92 includes, in order from the axial side, a head portion 131, a disk portion 132, a threaded shaft portion 133, and a protruding shaft portion 134. The head 131 is a portion to be engaged with a fastening tool such as a wrench. The head 131 has a hexagonal shape. The disc portion 132 has an outer diameter larger than the maximum outer diameter of the head portion 131. The maximum outer diameter of the threaded shaft portion 133 is smaller than the outer diameter of the disc portion 132. The protruding shaft portion 134 has a cylindrical shape. The diameter of the protruding shaft portion 134 is smaller than the minimum outer diameter of the threaded shaft portion 133. The head portion 131, the circular plate portion 132, the threaded shaft portion 133, and the protruding shaft portion 134 are disposed coaxially with their central axes aligned.
The cover member 92 of the first valve structure 81 is inserted into the first valve hole 21 with the protruding shaft 134 as the leading end. At this time, the threaded shaft 133 is screwed into the first threaded hole 34. At this time, the annular gasket 93 is interposed between the circular plate portion 132 and the first seat portion 15. In the state where the lid member 92 is screwed into the first valve hole 21, the protruding shaft 134 and the shaft 111 of the valve body 94 of the first valve structure 81 face each other in the axial direction with their center axes substantially aligned with each other. In the valve body 94, a predetermined gap is provided in the axial direction between the shaft portion 111 and the protruding shaft portion 134 of the cap member 92 in a state of abutting against the valve seat portion 104. The spool 94 moves axially within the range of the clearance. At this time, the outermost peripheral surface 114 of the flange portion 112 is guided by the inner peripheral surface 138, which is the cylindrical surface of the first main hole portion 33. Even if the valve body 94 moves within the above range, the flange portion 112 is always positioned between the inlet port 106 and the first outlet port 61.
The urging member 95 is a coil spring. The protruding shaft 134 of the cap member 92 is inserted into one axial end of the biasing member 95, and the shaft 111 of the valve body 94 is inserted into the other axial end. One end in the axial direction of the biasing member 95 abuts against an end surface of the cap member 92 on the side of the protruding shaft portion 134 of the threaded shaft portion 133, and the other end in the axial direction abuts against an end surface of the valve body 94 on the side of the shaft portion 111 of the flange portion 112. The biasing member 95 biases the valve body 94 in a valve closing direction toward the valve seat portion 104.
In a state where the differential pressure in the valve opening direction received by the valve body 94 is smaller than a predetermined value, the valve body 94 abuts against the valve seat portion 104 by the urging force of the urging member 95 to close the inlet 106. When the differential pressure in the valve opening direction received by the valve body 94 is greater than a predetermined value, the valve body 94 separates from the valve seat portion 104 against the biasing force of the biasing member 95 to open the inlet 106. At this time, the outermost peripheral surface 114 of the flange portion 112 of the valve body 94 is guided by the inner peripheral surface 138 of the first main hole portion 33 and moves in the axial direction.
The valve chamber 141 is formed by being surrounded by the first main hole portion 33 of the housing 12, the cap member 92, and the valve seat member 91. The spool 94 is axially movably disposed in the valve chamber 141. The valve seat member 91 constitutes the bottom 142 of the valve chamber 141. Therefore, a seat portion 104 on which the valve body 94 is seated is provided in the bottom portion 142 of the valve chamber 141. An inlet port 106 including the passage hole 101 of the valve seat member 91 is formed in the bottom 142 of the valve chamber 141. An inner peripheral surface 138 of the first main hole portion 33 is also an inner peripheral surface 138 of the valve chamber 141.
The first outlet port 61, which opens at the first main hole portion 33, is formed in the inner peripheral surface 138 of the valve chamber 141 of the first valve mechanism 83. Similarly, the second outlet port 71 that opens to the second main hole portion 43 is formed in the inner peripheral surface 138 of the valve chamber 141 of the second valve mechanism 84.
The valve body 94 includes a flange portion 112 on the bottom portion 142 side of the valve chamber 141. The flange portion 112 extends radially outward from the valve seat portion 104. The plurality of projections 118 of the flange portion 112 project radially outward from the flange base end portion 121 toward the inner circumferential surface 138 of the valve chamber 141. The plurality of recesses 116 of the flange portion 112 are recessed inward in the radial direction of the flange portion 112 at positions on the opposite side in the circumferential direction of the protruding portions 118. The flange portion 112 includes a plurality of projections 118 and recesses 116. The plurality of projections 118 project radially outward from the flange base end portion 121 toward the inner circumferential surface 138 of the valve chamber 141. The recess 116 is recessed radially inward at a position circumferentially opposite the projection 118.
As schematically shown in fig. 4, the differential pressure valve 11 is disposed in communication passages 158 and 159 that connect two air springs 155 and 156 provided between the vehicle body 152 and the bogie 153 of the vehicle 151. The differential pressure valve 11 opens and closes the communication passages 158 and 159 in accordance with the pressure difference between the two air springs 155 and 156.
One air spring 155 communicates with the first inflow passage 53 via a passage portion 161. The other air spring 156 and the second inflow passage 54 communicate via a passage portion 162. The passage portion 161 extending from one air spring 155, the first inflow passage 53, the inlet port 106 of the first valve mechanism 83, the valve chamber 141 of the first valve mechanism 83, the first internal passage 51, the inlet port 106 of the second valve mechanism 84, the second inflow passage 54, and the passage portion 162 constitute a communication passage 158 connecting the two air springs 155, 156. The passage portion 162 extending from the other air spring 156, the second inflow passage 54, the inflow port 106 of the second valve mechanism 84, the valve chamber 141 of the second valve mechanism 84, the second internal passage 52, the inflow port 106 of the first valve mechanism 83, the first inflow passage 53, and the passage portion 161 constitute a communication passage 159 that connects the two air springs 155, 156.
The first valve mechanism 83 is disposed in the communication passage 158, and opens and closes the communication passage 158 in accordance with a pressure difference between the two air springs 155 and 156. That is, when the pressure of the air spring 155 is higher than the pressure of the air spring 156, the valve body 94 is separated from the valve seat portion 104 against the urging force of the urging member 95 to open the inlet port 106. Then, the communication passage 158 communicates, and the air of the air spring 155 flows to the air spring 156 through the communication passage 158, that is, the passage portion 161, the first inflow passage 53, the inlet port 106 of the first valve mechanism 83, the valve chamber 141 of the first valve mechanism 83, the first internal passage 51 including the first outlet port 61, the inlet port 106 of the second valve mechanism 84, the second inflow passage 54, and the passage portion 162. Thereby, the pressure of the air spring 155 decreases to approach the pressure of the air spring 156.
Air from one air spring 155 flows into the inflow port 106 formed in the bottom 142 of the valve chamber 141. The first outlet 61 of the first internal passage 51 is formed in the inner peripheral surface 138 of the valve chamber 141 of the first valve mechanism 83, and discharges air to the other air spring 156.
The first outlet 61 intersects the axial direction of the first valve hole 21, which is the direction connecting the inlet 106 and the valve chamber 141. Specifically, the first outlet port 61 is orthogonal to the axial direction of the first valve hole 21. Therefore, when air flows from the inlet port 106 to the first outlet port 61 through the valve chamber 141, the air flowing from the inlet port 106 into the valve chamber 141 mainly passes through between the recess 116 of the flange portion 112 of the spool 94 and the inner circumferential surface 138 of the valve chamber 141 in the axial direction of the spool 94, and then changes its direction in the radial direction of the spool 94 and flows out from the first outlet port 61.
The second valve mechanism 84 is disposed in the communication passage 159, and opens and closes the communication passage 159 according to a pressure difference between the two air springs 155 and 156. That is, when the pressure of the air spring 156 is higher than the pressure of the air spring 155, the valve body 94 is separated from the valve seat portion 104 against the urging force of the urging member 95 to open the inlet port 106. Then, the communication passage 159 communicates with each other, and the air in the air spring 156 flows into the air spring 155 through the communication passage 159, that is, the passage portion 162, the second inflow passage 54, the inlet port 106 of the second valve mechanism 84, the valve chamber 141 of the second valve mechanism 84, the second internal passage 52 including the second outlet port 71, the inlet port 106 of the first valve mechanism 83, the first inflow passage 53, and the passage portion 161. Thereby, the pressure of the air spring 156 is reduced to approach the pressure of the air spring 155.
The air of the other air spring 156 flows into the inflow port 106 formed in the bottom 142 of the valve chamber 141. The second outlet 71 of the second internal passage 52 is formed in the inner peripheral surface 138 of the valve chamber 141 of the second valve mechanism 84, and discharges air to one air spring 155.
The second outlet 71 intersects the direction connecting the inlet 106 and the valve chamber 141, i.e., the axial direction of the second valve hole 22. Specifically, the second outlet 71 is orthogonal to the axial direction of the second valve bore 22. Therefore, when air flows from the inlet port 106 to the second outlet port 71 through the valve chamber 141, the air flowing from the inlet port 106 into the valve chamber 141 mainly passes through between the recess 116 of the flange portion 112 of the spool 94 and the inner circumferential surface 138 of the valve chamber 141 in the axial direction of the spool 94, and then changes its direction in the radial direction of the spool 94 and flows out from the second outlet port 71.
Patent document 1 discloses that a differential pressure valve that opens and closes a communication passage according to a pressure difference between two air springs is provided in a communication passage that connects the two air springs provided between a vehicle body and a bogie in a railway vehicle. In such a differential pressure valve, it is required to suppress variation in valve opening pressure.
In the differential pressure valve 11 according to the first embodiment, in the first valve mechanism 83, the inlet port 106 through which air flows into one air spring 155 is formed in the bottom portion 142 of the valve chamber 141, and the first outlet port 61 through which air flows out to the other air spring 156 is formed in the inner peripheral surface 138 of the valve chamber 141. With such a configuration, the first outlet 61 intersects the direction connecting the inlet 106 and the valve chamber 141. Therefore, when air flows from the inlet port 106 to the first outlet port 61 through the valve chamber 141, the air flowing from the inlet port 106 into the valve chamber 141 mainly passes through between the recess 116 of the flange portion 112 of the spool 94 and the inner circumferential surface 138 of the valve chamber 141 in the axial direction of the spool 94, and then changes its direction in the radial direction of the spool 94 and flows out from the first outlet port 61. At this time, when the recess 116 is located on the opposite side of the first outlet port 61 in the circumferential direction of the valve body 94, a large radial force acts on the valve body 94 toward the first outlet port 61 due to the flow of air toward the first outlet port 61 through the recess 116. Accordingly, the valve body 94 may be inclined in the valve chamber 141 such that the end portion of the flange portion 112 on the side opposite to the seat portion 104 is closer to the first outlet 61 than the end portion on the side of the seat portion 104.
In contrast, the first valve mechanism 83 is provided with an arc-shaped protruding portion 118 at a position on the flange portion 112 of the valve body 94 on the opposite side in the circumferential direction from the recess portion 116. Therefore, even if the spool 94 is inclined as described above, the protrusion 118 comes into line contact with the inner peripheral surface 138 of the valve chamber 141, and the contact surface pressure decreases. Therefore, the axial movement of the spool 94 becomes smooth. Therefore, variation in valve opening pressure can be suppressed. That is, if the recessed portion 116 is formed at a position on the opposite side in the circumferential direction of the recessed portion 116, the valve body 94 contacts the inner peripheral surface 138 of the valve chamber 141 at the corner portions of both ends of the recessed portion 116 in the circumferential direction of the flange portion 112 in a point contact manner when tilted as described above. Then, the contact surface pressure increases, and seizure or the like occurs, and the valve body 94 may not be smoothly moved in the axial direction. The first valve mechanism 83 can reduce such a possibility.
In addition, in the valve body 94, the projections 118 are formed at intervals of 120 ° in the circumferential direction. Therefore, the area of the outermost peripheral surface 114 of the valve body 94 can be enlarged. For example, the interval can be set to about 2 times as large as the interval of 60 °. Therefore, the contact area between the inner peripheral surface 138 of the valve chamber 141 and the valve body 94 can be increased, and therefore, the axial movement of the valve body 94 becomes smoother. Therefore, variation in the valve opening pressure can be further suppressed. Further, since the recesses 116 are formed at 120 ° intervals in the circumferential direction of the valve body 94, the number of recesses 116 can be reduced, and the number of processing steps for the valve body 94 can be reduced.
The first valve mechanism 83 has the following structure. That is, the valve body 94 has a shaft portion 111 that protrudes on the opposite side of the valve seat portion 104 from the flange portion 112. The shaft portion 111 is inserted into one end side of the urging member 95. Thereby, one end of the biasing member 95 is brought into contact with the flange 112. The cover member 92 has a protruding shaft portion 134 on the biasing member 95 side. The protruding shaft portion 134 is inserted into the other end side of the urging member 95. Thereby, the other end of the biasing member 95 is brought into contact with the threaded shaft portion 133. This can shorten the length of the biasing member 95 while stabilizing the posture. Therefore, the possibility of buckling of the biasing member 95 can be reduced, and the expansion and contraction of the biasing member 95 can be stabilized. Further, by shortening the biasing member 95, the inclination of the valve body 94 can be suppressed.
Further, since the valve body 94 of the first valve mechanism 83 has a shape having only one flange portion 112, air easily passes through the valve body, and the valve body is not easily affected by air, and the posture is stable. Therefore, variation in the valve opening pressure can be further suppressed.
The same applies to the second valve mechanism 84.
[ second embodiment ]
Next, a second embodiment will be described mainly with reference to fig. 5 to 7, focusing on differences from the first embodiment. Parts common to the first embodiment are denoted by the same reference numerals and the same names.
As shown in fig. 5, a differential pressure valve 11A according to a second embodiment is provided with a first valve mechanism 83A instead of the first valve mechanism 83 according to the first embodiment. The differential pressure valve 11A is provided with a second valve mechanism 84A instead of the second valve mechanism 84 of the first embodiment. The first valve structure portion 81A of the first valve mechanism 83A is partially different from the first valve structure portion 81 of the first embodiment. The second valve structure portion 82A of the second valve mechanism 84A is partially different from the second valve structure portion 82 of the first embodiment. The first valve structure portion 81A and the second valve structure portion 82A have the same configuration. Therefore, the first valve structure portion 81A will be described below as an example.
The first valve structure 81A includes a seat member 91, a cap member 92A, a gasket 93, a valve body 94A, an urging member 95A, and a plurality of disks 200. The valve seat member 91 is the same as that of the first embodiment. The cover member 92A is screwed to the first threaded hole portion 34 of the first valve hole 21. The gasket 93 is interposed between the cover member 92A and the first seat portion 15, as in the first embodiment. The spool 94A is movably provided in the first main hole portion 33. The biasing member 95A biases the valve body 94A in the direction of the valve seat member 91.
As shown in fig. 6 and 7, the valve body 94A is circular. Specifically, the valve body 94A is a stepped bottomed cylindrical shape. The valve body 94A includes a shaft portion 111A, a flange portion 112A (first flange portion), and a flange portion 212 (second flange portion). The flange portion 112A (first flange portion) is radially outwardly expanded from one axial end side of the shaft portion 111A. The flange portion 212 (second flange portion) spreads radially outward from the other end side in the axial direction of the shaft portion 111A. The shaft portion 111A and the flange portions 112A and 212 are arranged coaxially with their central axes aligned.
As shown in fig. 5, the shaft portion 111A has a bottomed cylindrical shape. The shaft portion 111A has a cylindrical body portion 201 and a bottom portion 202 closing one end of the body portion 201. Flange portion 112A is provided at the end of shaft portion 111A on the bottom portion 202 side. The flange portion 212 is provided at an opening end portion of the shaft portion 111A on the side opposite to the bottom portion 202. In the body portion 201, a through hole 204 is formed at a position between the flange portion 112A and the flange portion 212. The through-hole 204 penetrating the body 201 in the radial direction of the body 201 is formed in a plurality of, specifically, four, portions at equal intervals in the circumferential direction of the body 201 in the through-hole 204 penetrating the body 201.
As with the flange portion 112 of the first embodiment, a plurality of recesses 116 (first recesses) having the same shape are formed in the flange portion 112A. The recess 116 (first recess) is recessed radially inward from the cylindrical outermost peripheral surface 114. Therefore, the flange portion 112A is formed with a plurality of projecting portions 118 (first projecting portions) of the same shape projecting radially outward from the shaft portion 111A.
As shown in fig. 6 and 7, a plurality of recesses 216 (second recesses) having the same shape are formed in the flange portion 212, as in the flange portion 112A. The recess 216 (second recess) is recessed radially inward from the cylindrical outermost peripheral surface 214. The outermost peripheral surface 214 has the same outer diameter as the outermost peripheral surface 114. Recess 216 is the same shape as recess 116. The recess portions 216 are formed at odd-numbered positions at equal intervals in the circumferential direction of the flange portion 212. Specifically, the recess portions 216 are formed at three locations at 120 ° intervals in the circumferential direction of the flange portion 212. The flange portion 212 has the position of the recess 216 in its circumferential direction aligned with the recess 116 of the flange portion 112A.
In the outer peripheral portion of the flange portion 212, a protruding portion 218 (second protruding portion) is formed between the recess 216 and the recess 216 adjacent in the circumferential direction. The projecting portion 218 (second projecting portion) projects radially outward of the flange portion 212 from the most recessed position of the recessed portion 216. The projections 218 of the flange portion 212 are all of the same shape. The protrusion 218 is the same shape as the protrusion 118. The flange portion 212 has the position of the projection 218 in its circumferential direction aligned with the projection 118. In other words, the protrusion 118 and the protrusion 218 are arranged uniformly in the circumferential direction of the spool 94A. The length of the protruding portion 218 in the circumferential direction of the flange portion 212 is longer than the length of the recess portion 216 in the same direction. The protruding portion 218 is formed with an odd number of portions at equal intervals in the circumferential direction of the flange portion 212. Specifically, the protruding portion 218 is formed at three locations at 120 ° intervals in the circumferential direction of the flange portion 212.
Therefore, the flange portion 112A and the flange portion 212 have the same shape, and the positions (phases) of the valve bodies 94A in the circumferential direction are aligned. The through hole 204 of the shaft portion 111A is formed closer to the flange portion 112A than the flange portion 212.
As shown in fig. 5, the outer diameter of the bottomed cylindrical shaft portion 111A is larger than the outer diameter of the valve seat portion 104 of the valve seat member 91. In other words, the minimum outer diameter of the flange portion 112A is larger than the outer diameter of the valve seat portion 104. Therefore, the maximum outer diameter of the flange portions 112A and 212, that is, the maximum outer diameter of the valve body 94A is also larger than the outer diameter of the seat portion 104.
The maximum outer diameters of the flange portions 112A, 212 are slightly smaller than the inner diameter of the first main hole portion 33.
The valve body 94A is inserted into the first main hole portion 33 in an orientation in which the flange portion 112A is on the seat portion 104 side and the flange portion 212 is on the opposite side of the seat portion 104. In this state, the valve body 94A can be seated on the seat portion 104 at the bottom portion 202 of the shaft portion 111A. The valve body 94A includes a seating body 123 similar to that of the first embodiment on the side of the bottom portion 202 opposite to the body portion 201. The seating body 123 also constitutes a portion of the valve body 94A that seats on the seat portion 104. The valve body 124A is made of, for example, metal, and the material of the valve body 94A is different from that of the seating body 123 except for the seating body 123. The valve main body 124A constitutes all of the shaft portion 111A except the seating body 123, the flange portion 112A, and the flange portion 212, and is integrally formed.
As shown in fig. 6, an odd number of portions are formed in the flange portion 212, the recess portion 216, and the projection portion 218, respectively. Therefore, the recess portions 216 are provided at positions opposite to 180 degrees in the circumferential direction of each flange portion 212 with respect to all the protruding portions 218. In other words, the flange portion 212 also includes: a plurality of projecting portions 218 projecting radially outward from the shaft portion 111A; and a recess 216 that is recessed radially inward at a position on the opposite side of each of the plurality of projections 218 in the circumferential direction of the flange portion 212.
As shown in fig. 5, the lid member 92A includes a head portion 131 and a disk portion 132 similar to those of the first embodiment, and a screw shaft portion 133A is provided on the opposite side of the disk portion 132 from the head portion 131. The maximum outer diameter of the threaded shaft portion 133A is smaller than the outer diameter of the disc portion 132. The head portion 131, the disk portion 132, and the threaded shaft portion 133A are disposed coaxially with their central axes aligned.
A receiving hole 206 is formed in the center of the threaded shaft 133A in the radial direction. The accommodation hole 206 is provided through the threaded shaft portion 133A from the opposite side of the head portion 131 in the axial direction. The lid member 92A is inserted into the first valve hole 21 with the threaded shaft portion 133A as a leading end. At this time, the threaded shaft 133A is screwed into the first threaded hole 34. At this time, the washer 93 is interposed between the disc portion 132 and the first seat portion 15. In the first valve mechanism 83A, the accommodation hole 206 faces the flange portion 212 in the axial direction in a state where the lid member 92A is screwed to the first valve hole 21 and the center axis thereof is substantially aligned with the valve body 94A. The valve body 94A is provided with a predetermined gap in the axial direction between the lid member 92A and the valve seat portion 104 in a state of abutting on the valve seat portion. The spool 94A moves in the axial direction within the range of the clearance. At this time, outermost peripheral surfaces 114 and 214 of flange portions 112A and 212 of the valve body 94A are guided by an inner peripheral surface 138 of the first main hole portion 33. Even if the valve body 94A moves within the above range, the flange portion 112A is always positioned between the inlet port 106 and the first outlet port 61.
The urging member 95A is a coil spring. One end in the axial direction of the biasing member 95A is inserted into the housing hole 206 of the lid member 92A, and the other end in the axial direction is inserted into the body 201 of the valve body 94A. One axial end of the biasing member 95A abuts against the bottom of the housing hole 206 of the lid member 92A via the plurality of disks 200, and the other axial end abuts against the bottom 202 of the valve body 94A. Therefore, the urging member 95A is longer in the axial direction than the urging member 95 of the first embodiment. The biasing member 95A biases the valve body 94A in a valve closing direction toward the valve seat portion 104.
Therefore, in a state where the differential pressure in the valve opening direction received by the valve body 94A is smaller than a predetermined value, the valve body 94A abuts against the valve seat portion 104 by the biasing force of the biasing member 95A to close the inlet 106. When the differential pressure in the valve opening direction received by the valve body 94A is greater than a predetermined value, the valve body 94A separates from the valve seat portion 104 against the biasing force of the biasing member 95A to open the inlet port 106. At this time, the outermost peripheral surfaces 114 and 214 of the flange portions 112A and 212 of the valve body 94A are guided by the inner peripheral surface 138 of the first main hole portion 33 and move in the axial direction.
The valve chamber 141A is formed by being surrounded by the first main hole portion 33 of the housing 12, the cap member 92A, and the seat member 91. The spool 94A is axially movably disposed in the valve chamber 141A. The valve seat member 91 constitutes a bottom portion 142 of the valve chamber 141A. A seat portion 104 on which the spool 94A is seated is provided in a bottom portion 142 of the first valve chamber 141A. An inlet port 106 including the passage hole 101 of the valve seat member 91 is formed in the bottom 142 of the valve chamber 141A. An inner peripheral surface 138 of the first main hole portion 33 is also an inner peripheral surface 138 of the valve chamber 141A.
The first outlet port 61 that opens in the first main hole portion 33 is formed in the inner peripheral surface 138 of the valve chamber 141A of the first valve mechanism 83A. Similarly, the second outlet 71 that opens to the second main hole portion 43 is formed in the inner peripheral surface 138 of the valve chamber 141A of the second valve mechanism 84A.
The valve body 94A includes a flange portion 112A on the bottom portion 142 side of the valve chamber 141A. The flange portion 112A extends radially outward of the seat portion 104. The plurality of projections 118 of the flange portion 112A project radially outward from the shaft portion 111A toward the inner circumferential surface 138 of the valve chamber 141A. The plurality of recesses 116 of the flange portion 112A are recessed inward in the radial direction of the flange portion 112A at positions on the opposite side in the circumferential direction of the protruding portions 118.
The valve body 94A includes a flange portion 212 on the side opposite to the bottom portion 142. The flange portion 212 extends radially outward from the shaft portion 111A below the inner peripheral surface 138 of the valve chamber 141A. The plurality of projecting portions 218 of the flange portion 212 project radially outward from the shaft portion 111A toward the inner peripheral surface 138 of the valve chamber 141A. The plurality of recesses 216 of the flange portion 212 are recessed inward in the radial direction of the flange portion 212 at positions on the opposite side in the circumferential direction of the protruding portion 218.
In the first valve mechanism 83A, the first outlet 61 intersects with, specifically, is orthogonal to, the direction connecting the inlet 106 and the valve chamber 141A. Therefore, when air flows from the inlet port 106 to the first outlet port 61 through the valve chamber 141A, the air flowing from the inlet port 106 into the valve chamber 141A passes mainly between the recess 116 of the flange portion 112A of the spool 94A and the inner circumferential surface 138 of the valve chamber 141A in the axial direction of the spool 94A, and then changes its direction in the radial direction of the spool 94A and flows out from the first outlet port 61.
In the second valve mechanism 84A, the second outlet 71 intersects, specifically, orthogonally with, a direction connecting the inlet 106 and the valve chamber 141A. Therefore, when air flows from the inlet port 106 to the second outlet port 71 through the valve chamber 141A, the air flowing from the inlet port 106 into the valve chamber 141A passes mainly between the recess 116 of the flange portion 112A of the spool 94A and the inner circumferential surface 138 of the valve chamber 141A in the axial direction of the spool 94A, and then changes its direction in the radial direction of the spool 94A and flows out from the second outlet port 71.
In the differential pressure valve 11A, as in the valve chamber 141 of the first embodiment, the valve chamber 141A of the first valve mechanism 83A constitutes a communication passage 158 that communicates the air springs 155, 156. The valve chamber 141A of the second valve mechanism 84A constitutes a communication passage 159 that communicates the air springs 155, 156.
In the differential pressure valve 11A of the second embodiment, in the first valve mechanism 83A, the inlet port 106 through which air flows into one air spring 155 is formed in the bottom portion 142 of the valve chamber 141A, and the first outlet port 61 through which air flows out to the other air spring 156 is formed in the inner peripheral surface 138 of the valve chamber 141A.
With such a configuration, the first outlet 61 intersects the direction connecting the inlet 106 and the valve chamber 141A. Therefore, in the first valve mechanism 83A, when air flows from the inlet port 106 to the first outlet port 61 through the valve chamber 141A, the air flowing from the inlet port 106 into the valve chamber 141A mainly passes through between the recess 116 of the flange portion 112A of the spool 94A and the inner circumferential surface 138 of the valve chamber 141A in the axial direction of the spool 94A, and thereafter changes its direction in the radial direction of the spool 94A, and flows out from the first outlet port 61. At this time, when the recess 116 is located on the opposite side of the first outflow port 61 in the circumferential direction of the valve body 94A, a large radial force acts on the valve body 94A toward the first outflow port 61 due to the flow of air toward the first outflow port 61 through the recess 116. Thus, the valve body 94A may be inclined in the valve chamber 141A such that the flange portion 212 on the side opposite to the seat portion 104 is closer to the first outlet 61 than the flange portion 112B on the seat portion 104 side.
In contrast, in the first valve mechanism 83A, circular arc-shaped protruding portions 118 and 218 are provided at positions on the flange portion 112A of the valve body 94A on the opposite side in the circumferential direction from the recessed portions 116 and 216. Therefore, even if the spool 94A is inclined as described above, the protrusion 218 comes into line contact with the inner peripheral surface 138 of the valve chamber 141A, and the contact surface pressure decreases. Therefore, the axial movement of the spool 94A becomes smooth. Therefore, variation in valve opening pressure can be suppressed.
In addition, in the first valve mechanism 83A, in addition to the protruding portions 118, protruding portions 218 are formed on the spool 94A at intervals of 120 ° in the circumferential direction. Therefore, the area of the outermost peripheral surface 214 of the valve body 94A can be enlarged. Therefore, the contact area between the inner peripheral surface 138 of the valve chamber 141A and the spool 94A can be increased, and therefore, the axial movement of the spool 94A becomes smoother. Therefore, variation in the valve opening pressure can be further suppressed. Further, since the recesses 216 are formed at 120 ° intervals in the circumferential direction of the valve body 94A, the number of recesses 216 can be reduced. Therefore, the number of processing steps of the valve body 94A can be reduced.
Further, since the projection 118 and the projection 218 are arranged in a uniform manner in the circumferential direction of the valve body 94A, the number of steps for machining the valve body 94A can be reduced, and the air around the valve body 94A can flow smoothly.
The same applies to the second valve mechanism 84A.
[ third embodiment ]
Next, a third embodiment will be described mainly focusing on the differences from the second embodiment, with reference to fig. 8 to 10. Parts common to the second embodiment are denoted by the same reference numerals and the same names.
As shown in fig. 8, a differential pressure valve 11B according to a third embodiment is provided with a first valve mechanism 83B instead of the first valve mechanism 83A according to the second embodiment. The differential pressure valve 11B is provided with a second valve mechanism 84B in place of the second valve mechanism 84A of the second embodiment. The first valve structure portion 81B of the first valve mechanism 83B is partially different from the first valve structure portion 81A of the second embodiment. The second valve structure portion 82B of the second valve mechanism 84B is partially different from the second valve structure portion 82A of the second embodiment. Here, the first valve structure portion 81B and the second valve structure portion 82B have the same configuration. Therefore, the first valve structure portion 81B will be described as an example.
The first valve structure portion 81B has a spool 94B. The spool 94B is partially different from the spool 94A of the second embodiment. As shown in fig. 9 and 10, the valve body 94B includes a shaft portion 111A, a flange portion 112B (first flange portion), and a flange portion 212B (second flange portion). The shaft portion 111A is the same as that of the second embodiment. The flange portion 112B (first flange portion) is radially outwardly expanded from one axial end side of the shaft portion 111A. The flange portion 212B (second flange portion) spreads radially outward from the other end side in the axial direction of the shaft portion 111A. The shaft portion 111A and the flange portions 112B and 212B are arranged coaxially with their central axes aligned. As shown in fig. 8, the flange portion 112B is provided on the bottom portion 202 side of the shaft portion 111A. Flange portion 212B is provided on the opposite side of shaft portion 111A from bottom portion 202.
The flange portion 112B is formed with a plurality of recesses 116B (first recesses) having the same shape. The recess 116B (first recess) is recessed radially inward from the cylindrical outermost peripheral surface 114B. An even number of the recessed portions 116B are formed at equal intervals in the circumferential direction of the flange portion 112B. Specifically, the recess 116B is formed with 6 locations at 60 ° intervals in the circumferential direction of the flange portion 112B.
Thus, a protruding portion 118B (first protruding portion) is formed between the recess 116B and the recess 116B adjacent in the circumferential direction on the outer peripheral portion of the flange portion 112B. The protruding portion 118B protrudes outward in the radial direction of the flange portion 112B from the most recessed position of the recessed portion 116B. The projections 118B of the flange portion 112B are all of the same shape. The length of the protruding portion 118B in the circumferential direction of the flange portion 112B is shorter than the length of the recess portion 116B in the same direction. The projecting portion 118B is formed at an even number of locations at equal intervals in the circumferential direction of the flange portion 112B. Specifically, the protruding portion 118B is formed with 6 locations at 60 ° intervals in the circumferential direction of the flange portion 112B.
A plurality of recesses 216B (second recesses) having the same shape are formed in the flange portion 212B. The recess 216B (second recess) is recessed radially inward from the cylindrical outermost peripheral surface 214B. The outermost peripheral surface 214B has the same outer diameter as the outermost peripheral surface 114B. Recess 216B is the same shape as recess 116B. The recess portions 216B are formed at even number of locations at equal intervals in the circumferential direction of the flange portion 212B. Specifically, the recess portions 216B are formed at 6 locations at 60 ° intervals in the circumferential direction of the flange portion 212B. The flange portion 212B has the position of the recess 216B in its circumferential direction aligned with the projection 118B of the flange portion 112B.
In the outer peripheral portion of the flange portion 212B, a protruding portion 218B (second protruding portion) is formed between the recess 216B and the recess 216B adjacent in the circumferential direction. The projecting portion 218B (second projecting portion) projects outward in the radial direction of the flange portion 212B from the most recessed position of the recessed portion 216B. The projections 218B of the flange portion 212B are all of the same shape. Protrusion 218B is the same shape as protrusion 118B. The flange portion 212B has the position of the projection 218B in the circumferential direction thereof aligned with the recess 116B of the flange portion 112B. The length of the protruding portion 218B in the circumferential direction of the flange portion 212B is shorter than the length of the recess portion 216B in the same direction. The projecting portion 218B is formed at an even number of locations at equal intervals in the circumferential direction of the flange portion 212B. Specifically, the protruding portion 218B is formed with 6 locations at 60 ° intervals in the circumferential direction of the flange portion 212B.
Therefore, the flange portion 112B and the flange portion 212B have the same shape, and the positions (phases) of the protruding portion 118B and the protruding portion 218B are shifted in the circumferential direction of the valve body 94B. In other words, the projection 118B and the projection 218B are arranged offset in the circumferential direction of the spool 94B.
The maximum outer diameters of the flange portions 112B, 212B are slightly smaller than the inner diameter of the first main hole portion 33.
As shown in fig. 8, the valve body 94B is inserted into the first main hole portion 33 in an orientation in which the flange portion 112B is on the valve seat portion 104 side and the flange portion 212B is on the opposite side of the valve seat portion 104. In this state, the valve body 94B can be seated on the seat portion 104 by the seating body 123 provided at the bottom portion 202 of the shaft portion 111A. The valve body 124B made of, for example, metal is formed in a portion of the valve body 94B other than the seating body 123, the material of which is different from that of the seating body 123. The valve main body 124B constitutes all of the shaft portion 111A except the seating body 123, the flange portion 112B, and the flange portion 212B, and is integrally formed.
As shown in fig. 9 and 10, an even number of recesses 116B and projections 118B are formed in the flange portion 112B, and an even number of recesses 216B and projections 218B are formed in the flange portion 212B. As described above, the projecting portions 118B are provided at positions opposite to 180 degrees in the circumferential direction of each valve body 94B with respect to all the projecting portions 118B of the flange portion 112B. Further, the recess 116B is provided at a position opposite to the 180-degree side in the circumferential direction of each valve body 94B with respect to all the recesses 116B of the flange portion 112B. Further, the projecting portions 218B are provided at positions opposite to 180 degrees in the circumferential direction of each valve body 94B with respect to all the projecting portions 218B of the flange portion 212B. Further, the recess portions 216B are provided at positions opposite to 180 degrees in the circumferential direction of each valve body 94B with respect to all the recess portions 216B of the flange portion 212B.
The phase of the recess 116B of the flange portion 112B matches the phase of the projection 218B of the flange portion 212B, and the phase of the projection 118B of the flange portion 112B matches the phase of the recess 216B of the flange portion 212B. As described above, the recess 216B of the flange portion 212B is provided at a position opposite to 180 degrees in the circumferential direction of each valve body 94B with respect to all the protruding portions 118B of the flange portion 112B. Further, the recess 116B of the flange portion 112B is provided at a position opposite to the 180-degree side in the circumferential direction of each valve body 94B with respect to all the protruding portions 218B of the flange portion 212B. In other words, the flange portion 112B has a plurality of projecting portions 118B projecting radially outward. The flange portion 212B has a recess 216B that is recessed radially inward at a position on the opposite side of each of the plurality of projections 118B in the circumferential direction of the valve body 94B. The flange portion 212B has a plurality of projecting portions 218B projecting radially outward. The flange portion 112B has a recess 116B that is recessed radially inward at a position on the opposite side of each of the plurality of projections 218B in the circumferential direction of the valve body 94B.
As shown in fig. 8, the spool 94B includes a flange portion 112B on the bottom 142 side of the valve chamber 141A. The flange portion 112B extends radially outward of the seat portion 104. The plurality of projecting portions 118B of the flange portion 112B project radially outward from the shaft portion 111A toward the inner circumferential surface 138 of the valve chamber 141A. The valve body 94B includes a flange portion 212B extending radially outward from the shaft portion 111A toward the lower side of the inner circumferential surface 138 of the valve chamber 141A on the side opposite to the bottom portion 142 of the valve chamber 141A. The flange portion 212B includes a plurality of protruding portions 218B at positions circumferentially shifted from the protruding portions 118B of the flange portion 112B. The protruding portion 218B protrudes radially outward from the shaft portion 111A toward the inner peripheral surface 138 of the valve chamber 141A.
In the first valve mechanism 83B, the first outlet 61 intersects with, specifically, is orthogonal to, the direction connecting the inlet 106 and the valve chamber 141A. Therefore, when air flows from the inlet port 106 to the first outlet port 61 through the valve chamber 141A, the air flowing from the inlet port 106 into the valve chamber 141A mainly passes through between the recess 116B of the flange portion 112B of the spool 94B and the inner circumferential surface 138 of the valve chamber 141A in the axial direction of the spool 94B, and then changes its direction in the radial direction of the spool 94B, and flows out from the first outlet port 61.
In the second valve mechanism 84B, the second outlet 71 intersects, specifically, orthogonally with, a direction connecting the inlet 106 and the valve chamber 141A. Therefore, when air flows from the inlet port 106 to the second outlet port 71 through the valve chamber 141A, the air flowing from the inlet port 106 into the valve chamber 141A mainly passes through between the recess 116B of the flange portion 112B of the spool 94B and the inner circumferential surface 138 of the valve chamber 141A in the axial direction of the spool 94B, and then changes its direction in the radial direction of the spool 94B, and flows out from the second outlet port 71.
In the differential pressure valve 11B according to the third embodiment, in the first valve mechanism 83B, the inlet port 106 through which air flows into one air spring 155 is formed in the bottom portion 142 of the valve chamber 141A, and the first outlet port 61 through which air flows out to the other air spring 156 is formed in the inner peripheral surface 138 of the valve chamber 141A.
With such a configuration, the first outlet 61 intersects the direction connecting the inlet 106 and the valve chamber 141A. Therefore, when air flows from the inlet port 106 to the first outlet port 61 through the valve chamber 141A, the air flowing from the inlet port 106 into the valve chamber 141A mainly passes through between the recess 116B of the flange portion 112B of the spool 94B and the inner circumferential surface 138 of the valve chamber 141A in the axial direction of the spool 94B, and then changes its direction in the radial direction of the spool 94B, and flows out from the first outlet port 61. At this time, when the recess 116B is located on the opposite side of the first outflow port 61 in the circumferential direction of the valve body 94B, a large radial force acts on the valve body 94B toward the first outflow port 61 due to the flow of air toward the first outflow port 61 through the recess 116B. Thus, the valve body 94B may be inclined in the valve chamber 141A such that the flange portion 212B on the opposite side from the seat portion 104 is closer to the first outlet 61 than the flange portion 112B on the seat portion 104 side.
In contrast, in the first valve mechanism 83B, the arc-shaped protruding portion 218B of the flange portion 212B is provided at a position on the valve body 94B on the opposite side in the circumferential direction of the recess portion 116B of the flange portion 112B. Therefore, even if the spool 94B is inclined as described above, the protrusion 218B comes into line contact with the inner peripheral surface 138 of the valve chamber 141A, and the contact surface pressure decreases. Therefore, the axial movement of the spool 94B becomes smooth. Therefore, variation in valve opening pressure can be suppressed.
Further, since the projection 118B and the projection 218B are arranged offset in the circumferential direction, imbalance in the weight of the valve body 94B can be suppressed.
The same applies to the second valve mechanism 84B.
A first aspect of the above-described embodiment is a differential pressure valve that is disposed in a communication passage connecting two air springs provided between a vehicle body and a bogie, and opens and closes the communication passage in accordance with a pressure difference between the two air springs. The differential pressure valve has: a valve chamber; a circular valve cartridge disposed within the valve chamber; an inflow port formed at a bottom of the valve chamber, through which air of one of the air springs flows; an outlet port formed in an inner peripheral surface of the valve chamber and configured to allow air to flow out to the other air spring; a valve seat portion that is formed at a bottom portion of the valve chamber so as to surround the inlet port and on which the valve body is seated; and a biasing member that biases the valve body in a valve closing direction toward the valve seat portion. The valve body includes a first flange portion extending radially outward from the valve seat portion on the bottom portion side. The first flange portion includes: a plurality of first protrusions protruding radially outward toward an inner circumferential surface of the valve chamber; and a first recess that is recessed radially inward at a position on the opposite side of the first projection in the circumferential direction. This can suppress variation in valve opening pressure.
In addition, a second aspect is the first aspect, wherein the first protrusions are formed at 120 ° intervals in the circumferential direction. This can suppress variation in valve opening pressure. In addition, the number of steps for machining the valve body can be reduced.
A third aspect is the valve body of the first or second aspect, wherein the valve body includes, on a side opposite to the bottom portion, a second flange portion extending radially outward toward an inner peripheral surface of the valve chamber, the second flange portion including: a plurality of second protrusions protruding radially outward toward an inner circumferential surface of the valve chamber; and a second recess that is recessed radially inward at a position on the opposite side of the second projection in the circumferential direction. This can suppress variation in valve opening pressure.
In addition, a fourth aspect is the third aspect, wherein the second protrusions are formed at intervals of 120 ° in the circumferential direction. This can suppress variation in valve opening pressure.
In addition, according to a fifth aspect, in the third or fourth aspect, the first protruding portion and the second protruding portion are arranged to be circumferentially uniform. This reduces the number of steps for machining the valve body, and smoothes the flow of air around the valve body.
A sixth aspect is the third or fourth aspect, wherein the first protruding portion and the second protruding portion are arranged to be circumferentially offset. This can suppress imbalance in the weight of the valve body.
A seventh aspect is a differential pressure valve which is disposed in a communication passage connecting two air springs provided between a vehicle body and a bogie, and opens and closes the communication passage in accordance with a pressure difference between the two air springs. The differential pressure valve has: a valve chamber; a circular valve cartridge disposed within the valve chamber; an inflow port formed at a bottom of the valve chamber, through which air of one of the air springs flows; an outlet port formed in an inner peripheral surface of the valve chamber and configured to allow air to flow out to the other air spring; a valve seat portion that is formed at a bottom portion of the valve chamber so as to surround the inlet port and on which the valve body is seated; and a biasing member that biases the valve body in a valve closing direction toward the valve seat portion. The valve body includes a first flange portion extending radially outward from the valve seat portion on the bottom portion side, and a second flange portion extending radially outward toward the inner peripheral surface of the valve chamber on a side opposite to the bottom portion. The first flange portion includes a plurality of first protruding portions that protrude radially outward toward the inner peripheral surface of the valve chamber. The second flange portion includes a plurality of second protruding portions protruding radially outward toward the inner peripheral surface of the valve chamber at positions circumferentially offset from the first protruding portions. This can suppress variation in valve opening pressure.
Industrial applicability
According to the differential pressure valve, variations in valve opening pressure can be suppressed.
Description of the reference numerals
11. 11A, 11B differential pressure valve
61 first outflow opening (outflow opening)
71 second outflow opening (outflow opening)
94. 94A, 94B valve core
95 force application component
104 valve seat part
106 flow inlet
152 vehicle body
153 bogie
155. 156 air spring
158. 159 a communication passage
141. 141A valve chamber
142 bottom
138 inner peripheral surface
112. 112A, 112B flange parts (first flange part)
116. 116B recess (first recess)
118. 118B projection (first projection)
212. 212B Flange part (second flange part)
216. 216B recess (second recess)
218. 218B projection (second projection)

Claims (7)

1. A differential pressure valve which is disposed in a communication passage connecting two air springs provided between a vehicle body and a bogie and opens and closes the communication passage according to a pressure difference between the two air springs, the differential pressure valve comprising:
a valve chamber;
a circular valve cartridge disposed within the valve chamber;
an inflow port formed at a bottom of the valve chamber, through which air of one of the air springs flows;
an outlet port formed in an inner peripheral surface of the valve chamber and configured to allow air to flow out to the other air spring;
a valve seat portion that is formed at a bottom portion of the valve chamber so as to surround the inlet port and on which the valve body is seated; and
a biasing member that biases the valve body in a valve closing direction toward the valve seat portion,
the valve body includes a first flange portion extending radially outward from the valve seat portion on the bottom portion side,
the first flange portion includes:
a plurality of first protrusions protruding radially outward toward an inner circumferential surface of the valve chamber; and
a first recess that is recessed radially inward at a position on the opposite side of the first projection in the circumferential direction.
2. The differential pressure valve of claim 1,
the first protrusions are formed at intervals of 120 ° in the circumferential direction.
3. A differential pressure valve according to claim 1 or 2,
the valve body includes a second flange portion extending radially outward toward an inner peripheral surface of the valve chamber on a side opposite to the bottom portion,
the second flange portion includes:
a plurality of second protrusions protruding radially outward toward an inner circumferential surface of the valve chamber; and
a second recess that is recessed radially inward at a position on the opposite side of the second projection in the circumferential direction.
4. A differential pressure valve according to claim 3,
the second protrusions are formed at intervals of 120 ° in the circumferential direction.
5. A differential pressure valve according to claim 3 or 4,
the first protruding portion and the second protruding portion are arranged circumferentially in line.
6. A differential pressure valve according to claim 3 or 4,
the first protruding portion and the second protruding portion are arranged to be circumferentially offset.
7. A differential pressure valve which is disposed in a communication passage connecting two air springs provided between a vehicle body and a bogie and opens and closes the communication passage according to a pressure difference between the two air springs, the differential pressure valve comprising:
a valve chamber;
a circular valve cartridge disposed within the valve chamber;
an inflow port formed at a bottom of the valve chamber, through which air of one of the air springs flows;
an outlet port formed in an inner peripheral surface of the valve chamber and configured to allow air to flow out to the other air spring;
a valve seat portion that is formed at a bottom portion of the valve chamber so as to surround the inlet port and on which the valve body is seated; and
a biasing member that biases the valve body in a valve closing direction toward the valve seat portion,
the valve body includes a first flange portion extending radially outward from the valve seat portion on the bottom portion side, and a second flange portion extending radially outward toward an inner peripheral surface of the valve chamber on a side opposite to the bottom portion,
the first flange portion includes a plurality of first protruding portions protruding radially outward toward an inner peripheral surface of the valve chamber,
the second flange portion includes a plurality of second protruding portions protruding radially outward toward the inner peripheral surface of the valve chamber at positions circumferentially offset from the first protruding portions.
CN202080024059.8A 2019-06-26 2020-06-19 Differential pressure valve Pending CN113661343A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2019118690 2019-06-26
JP2019-118690 2019-06-26
PCT/JP2020/024177 WO2020262244A1 (en) 2019-06-26 2020-06-19 Differential pressure valve

Publications (1)

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CN113661343A true CN113661343A (en) 2021-11-16

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CN (1) CN113661343A (en)
WO (1) WO2020262244A1 (en)

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PT3997542T (en) * 2019-07-12 2024-08-29 Hagepe Int B V Check valve

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JP2005106452A (en) * 2003-09-08 2005-04-21 Tgk Co Ltd Expansion device
JP6065648B2 (en) 2013-02-28 2017-01-25 Ｋｙｂ株式会社 Differential pressure valve
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