JPS598583B2 - Brake valve for air brake equipment - Google Patents
Brake valve for air brake equipmentInfo
- Publication number
- JPS598583B2 JPS598583B2 JP12498479A JP12498479A JPS598583B2 JP S598583 B2 JPS598583 B2 JP S598583B2 JP 12498479 A JP12498479 A JP 12498479A JP 12498479 A JP12498479 A JP 12498479A JP S598583 B2 JPS598583 B2 JP S598583B2
- Authority
- JP
- Japan
- Prior art keywords
- spring
- receiving member
- piston
- spring receiving
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Landscapes
- Valves And Accessory Devices For Braking Systems (AREA)
Description
【発明の詳細な説明】
本発明は自動車用エアーブレーキ装置に用いるブレーキ
弁に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a brake valve used in an air brake system for automobiles.
この種のブレーキ弁は、従来より、弁本体にシリング孔
を設け、そのシリンダ孔にピストンを摺動自在に挿入し
、そのピストンを、ブレーキペダルにより、そのブレー
キペダルの揺動運動を受けて上下動するプランジャ、そ
のプランジャの押力を受けて直ちに変位する第１のばね
及び第１のばねの所定値以上の圧縮時に変位する第２の
ばねを介して上方より駆動し、そのピストンにより、流
体圧力源に接続する供給口とプレーキチャンバ等の流体
圧作動機器に接続する送出口との間、及びその送出口と
大気に連通ずる排気口との間の連通路を開閉する給排弁
を操作するようにし、プレーキペダルの踏力が小さいと
きには、第１のばねのみを変位して踏力に対するペダル
ストロークを犬きくし、踏力が大きくなると、第１及び
第２のばねを変位して踏力に対するペダルストロークを
小さくするようにしている。Conventionally, this type of brake valve has a cylinder hole in the valve body, a piston is slidably inserted into the cylinder hole, and the piston is moved up and down by the swinging motion of the brake pedal. The piston is driven from above through a moving plunger, a first spring that is displaced immediately upon receiving the pushing force of the plunger, and a second spring that is displaced when the first spring is compressed to a predetermined value or more. Operates the supply/discharge valve that opens and closes the communication path between the supply port connected to the pressure source and the delivery port connected to fluid pressure operated equipment such as a brake chamber, and between the delivery port and the exhaust port that communicates with the atmosphere. When the depressing force of the brake pedal is small, only the first spring is displaced to increase the pedal stroke relative to the depressing force, and when the depressing force is large, the first and second springs are displaced to increase the pedal stroke relative to the depressing force. I'm trying to keep it small.
そして、ブレーキペダルにより駆動されるプランジャの
押力を第１及び第２のばねに伝達すべく、プランジャと
第１、第２のばねとの間に介在する第１及び第２のばね
受部材は、ピストンに上方に延びる柱状の突起を設け、
その突起に第２のばね受部材を移動可能に外嵌させ、そ
の第２のばね受部材に第１のばね受部材を移動可能に外
嵌させることにより、ピストンに対し、その軸方向にの
み移動できるように支持＼
されていた。In order to transmit the pushing force of the plunger driven by the brake pedal to the first and second springs, first and second spring bearing members are interposed between the plunger and the first and second springs. , the piston is provided with a columnar projection extending upward,
By movably fitting the second spring receiving member onto the protrusion and movably fitting the first spring receiving member onto the second spring receiving member, the piston can be moved only in the axial direction. It was supported so that it could be moved.
しかし、ピストンに設けられた柱状突起により第１及び
第２のばね受部材を移動可能に支持する従来のブレーキ
弁においては、プランジャが、揺動するブレーキペダル
により駆動されるため、上下運動すると同時に、弁本体
に対し、すなわちピストンの軸に対して揺動運動を生じ
る。However, in the conventional brake valve in which the first and second spring bearing members are movably supported by a columnar projection provided on the piston, the plunger is driven by the swinging brake pedal, so it moves up and down and at the same time , which produces a rocking movement relative to the valve body, i.e. relative to the axis of the piston.
そして、この揺動運動はプランジャと第１のばね受部材
との摩擦係合及び第１のばね受部材と第２のばね受部材
との嵌合部を介して直接的にピストンに伝達される。This rocking motion is directly transmitted to the piston via the frictional engagement between the plunger and the first spring receiving member and the fitting portion between the first spring receiving member and the second spring receiving member. .
従って、ピストンに偏荷重が加わりピストンとシリンダ
孔との間にこじれが生じるのて、ピストンがシリンダ孔
内を滑らかに移動することができなくなり、ひいてはピ
ストンとシリンダ孔との摺動面が偏摩耗して、エアー漏
れを生じるという危険性がある。Therefore, an uneven load is applied to the piston, causing strain between the piston and the cylinder hole, making it impossible for the piston to move smoothly within the cylinder hole, and causing uneven wear on the sliding surface between the piston and the cylinder hole. Therefore, there is a risk of air leakage.
これに加えて、第１のばね受部材と第２のばね受部材と
が、あるいは第２のばね受部材と柱状突起とが偏荷重を
受けて摺動するので、それらの摺動面にこじれが発子し
て段付摩耗を生じ易く、ブレーキペダルの移動が滑らか
でなくなるという危険性がある。In addition, since the first spring receiving member and the second spring receiving member or the second spring receiving member and the columnar protrusion slide under an uneven load, the sliding surfaces may be strained. This tends to cause stepped wear, and there is a risk that the brake pedal will not move smoothly.
本発明は、上記問題点に鑑みてなされたものであって、
ピストンと第１及び第２のばね受部材とにプランジャの
揺動による偏荷重が作用するのを防止して、円滑に作動
し得るブレーキ弁な提供することを目的とし、その特徴
とするところは、第１のばね受部材に設けた係合部をプ
ランジャに係合して、第１のばね受部材をプランジャに
より支持すると共に、第２のばね受部材の軸部を第１の
ばね受部材に設けた案内孔に軸方向に移動可能に嵌合し
、第２のばね受部材を第１のばね受部材により案内した
ことにある。The present invention has been made in view of the above problems, and includes:
The purpose of this invention is to provide a brake valve that can operate smoothly by preventing unbalanced loads due to the swinging of the plunger from acting on the piston and the first and second spring bearing members, and its features are as follows: , an engaging portion provided on the first spring bearing member is engaged with the plunger to support the first spring bearing member by the plunger, and the shaft portion of the second spring bearing member is connected to the first spring bearing member. The first spring receiving member is fitted into a guide hole provided in the second spring receiving member so as to be movable in the axial direction, and the second spring receiving member is guided by the first spring receiving member.
以下、本発明の実施例について、図面に従って説明する
。Embodiments of the present invention will be described below with reference to the drawings.
本発明の一実施例を示す第１図において、弁本体１は、
その内部上方に第１のシリンダ孔２を、その下方に第２
のシリンダ孔３を設けており、弁本体１の上端には上蓋
部材４がボルト６により取付けられ、また下端にはシー
ルリング３０を介して下蓋部材５がボルト等適当な手段
によって取付けられている。In FIG. 1 showing one embodiment of the present invention, the valve body 1 is
A first cylinder hole 2 is provided above the interior, and a second cylinder hole 2 is provided below.
A cylinder hole 3 is provided, and an upper cover member 4 is attached to the upper end of the valve body 1 with bolts 6, and a lower cover member 5 is attached to the lower end via a seal ring 30 by appropriate means such as bolts. There is.
そして、第１のシリンダ孔２には、外周にシールリング
８を装着した第１のピストン７が摺動自在に挿入され、
その下側に、一方のブレーキ系統のプレーキチャンバ等
の流体圧作動機器（図示していない）に接続する送出口
９に連通ずる第１の送出室１０、及び通孔１１を介して
送出室１０に連通ずるリアクション室１２を形成してい
る。A first piston 7 having a seal ring 8 attached to its outer periphery is slidably inserted into the first cylinder hole 2.
On the lower side thereof, there is a first delivery chamber 10 which communicates with a delivery port 9 connected to a fluid pressure operated device (not shown) such as a brake chamber of one brake system, and a delivery chamber 10 through a through hole 11. A reaction chamber 12 is formed which communicates with the reactor.
そして、リアクション室１２の流体圧力は、送出室１０
の流体圧力が緩やかに変化するときには、送出室１０の
流体圧力と同一に保たれるが、送出室１０の流体圧力が
急激に変化するときには、多少遅れて応答する。The fluid pressure in the reaction chamber 12 is equal to the fluid pressure in the delivery chamber 10.
When the fluid pressure in the delivery chamber 10 changes slowly, it is kept the same as the fluid pressure in the delivery chamber 10, but when the fluid pressure in the delivery chamber 10 changes rapidly, the response is delayed.
ピストン戻しばね３１はリアクション室１２内に配置さ
れ第１のピストン７を上方に付勢している。The piston return spring 31 is disposed within the reaction chamber 12 and biases the first piston 7 upward.
第２のシリンダ孔３には、シールリング１４を外周に装
着した中継ピストンすなわち第２のピストン１３が摺動
自在に挿入され、その上側に通孔１５を介して第１の送
出室１０に連通する中継室１６を形成し、その下側に他
方のブレーキ系統のプレーキチャンバ等の流体圧作動機
器（図示していない）に接続する送出口１７に連通ずる
第２の送出室１８を形成している。A relay piston, that is, a second piston 13 equipped with a seal ring 14 on the outer periphery is slidably inserted into the second cylinder hole 3, and communicates with the first delivery chamber 10 through a through hole 15 on the upper side. A relay chamber 16 is formed under the relay chamber 16, and a second delivery chamber 18 is formed below the relay chamber 16, which communicates with a delivery port 17 connected to a fluid pressure operated device (not shown) such as a brake chamber of the other brake system. There is.
なお、上述の流体圧作動機器は、従来より知られている
エアーブレーキ装置に用いられ、ブレーキ弁から送出さ
れる流体圧力が作用可能な機器でればよく、例えば、ブ
レーキ弁からの流体圧力を信号圧力として受け、流体圧
力源からプレーキチャンバに流体圧力を供給可能な中継
弁、プレーキチャンバの代わりに設けることができるエ
アオーバーハイドロリツクプースタ、車両の積載状態に
応じて流体圧力を調整可能な荷重応動弁、ブレーキ弛め
時に流体圧力を迅速に解放可能な急弛め弁等を包含する
ものである。The above-mentioned fluid pressure operating device may be any device that is used in a conventionally known air brake device and can be acted upon by the fluid pressure sent out from the brake valve. A relay valve that receives signal pressure and can supply fluid pressure from a fluid pressure source to a brake chamber, an air over hydraulic booster that can be installed in place of a brake chamber, and allows fluid pressure to be adjusted according to the loading condition of the vehicle. This includes load-responsive valves, quick release valves that can quickly release fluid pressure when the brake is released, and the like.
以下、送出口９ １７のそれぞれに接続する流体圧作動
機器をプレーキチャンバ又は中継弁として説明する。Hereinafter, the fluid pressure operated devices connected to each of the outlet ports 917 will be described as a brake chamber or a relay valve.
また、第２のピストン１３はピストン戻しばね３２によ
り上方に付勢されている。Further, the second piston 13 is urged upward by a piston return spring 32.
第１のシリンダ孔２の下方に設けられた第１の弁室１９
は、内周及び外周にシールリング２０及び２１を装着し
た仕切壁部材２２により中継室１６から気密に区画され
、供給口２３を介して一方のブレーキ系統の流体圧力源
（図示していない）に接続している。First valve chamber 19 provided below the first cylinder hole 2
is airtightly separated from the relay chamber 16 by a partition wall member 22 equipped with seal rings 20 and 21 on the inner and outer peripheries, and is connected to a fluid pressure source (not shown) of one brake system via a supply port 23. Connected.
この弁室１９には、弁ばね２４により土方に付勢された
第１０給排弁部材２５が、第１のピストン７の下端に設
けた排気弁座２６及び弁本体１に設けた供給弁座２７に
係合可能に配置されており、給排弁部材２５と供給弁座
２７とにより供給口２３と送出室１０との連通路を開閉
する供給弁を、また、給排弁部材２５と排気弁座２６と
により、送出室１０を第２のピストン１３の上方に延び
る管状部に設けられた切欠部２８排気孔２９及び第２０
給排弁部材３３に設けられた排気孔３４を介して大気に
接続する排気弁を構成し、供給弁及び排気弁により給排
弁を構成している。In this valve chamber 19, a tenth supply/discharge valve member 25 biased toward Hijikata by a valve spring 24 is connected to an exhaust valve seat 26 provided at the lower end of the first piston 7 and a supply valve seat provided on the valve body 1. 27, and the supply valve which opens and closes the communication path between the supply port 23 and the delivery chamber 10 by the supply/discharge valve member 25 and the supply valve seat 27, and the supply/discharge valve member 25 and the exhaust valve seat 27. The valve seat 26 allows the delivery chamber 10 to be connected to the notch 28 provided in the tubular portion extending above the second piston 13 and the exhaust hole 29 and the
An exhaust valve is configured to be connected to the atmosphere through an exhaust hole 34 provided in the supply/discharge valve member 33, and the supply/discharge valve is configured by the supply valve and the exhaust valve.
なお、第２のピストン１３の管状部と給排弁部材２５と
の摺動部にはシールリング３５が設げられている。Note that a seal ring 35 is provided at the sliding portion between the tubular portion of the second piston 13 and the supply/discharge valve member 25.
下蓋部材５に設けられた弁室３６は、外周、内周がシー
ルリング３７ ３８によりシールされた部材３９により
、大気から区画され、供給口４０を介して他方のブレー
キ系統の流体圧力源（図示していない）に接続している
。The valve chamber 36 provided in the lower lid member 5 is separated from the atmosphere by a member 39 whose outer and inner peripheries are sealed by seal rings 37 and 38, and is connected to the fluid pressure source of the other brake system ( (not shown).
そして、弁室３６には、弁ばね４１により上方に付勢さ
れた第２の給排弁部材３３が、ピストン１３の下端に設
けた排気弁座４３及び下蓋部材５に設けた供給弁座４２
と保合可能に配置されており、給排弁部材３３と供給弁
座４２とにより供給口４０と第２の送出室１８との間の
連通路を開閉する供給弁を、給排弁部材３３と排気弁座
４３とにより送出室１８を排気孔３４を介して大気に接
続する排気弁を構成し、供給弁と排気弁とにより第２０
給排弁を構成している。In the valve chamber 36, a second supply/discharge valve member 33, which is urged upward by a valve spring 41, is connected to an exhaust valve seat 43 provided at the lower end of the piston 13 and a supply valve seat provided on the lower lid member 5. 42
The supply valve which opens and closes the communication path between the supply port 40 and the second delivery chamber 18 by the supply/discharge valve member 33 and the supply valve seat 42 is connected to the supply/discharge valve member 33 . and the exhaust valve seat 43 constitute an exhaust valve that connects the delivery chamber 18 to the atmosphere via the exhaust hole 34, and the supply valve and the exhaust valve constitute the 20th exhaust valve.
It constitutes a supply/discharge valve.
下蓋部材５の下端に設けられた大気に連通ずる排気口４
４には、開口４５を有する支持板４６に装着されたダス
ト力バー４７が取付けられている。Exhaust port 4 connected to the atmosphere provided at the lower end of the lower lid member 5
4 is fitted with a dust force bar 47 mounted on a support plate 46 having an opening 45.
ブレーキペダル５０は、上蓋部材４に設けられた回転軸
５１に回転可能に取付けられており、軸５２に支持され
たローラ５３により、上蓋部材４に設けられた孔５４内
に摺動自在に挿入されたプランジャ５５を下方に押圧す
る。The brake pedal 50 is rotatably attached to a rotating shaft 51 provided in the upper lid member 4, and is slidably inserted into a hole 54 provided in the upper lid member 4 by a roller 53 supported by a shaft 52. The plunger 55 is pressed downward.
調節ねじ５６はブレーキペダル５０の左端に装着され、
ブレーキペダル５０の戻り位置を調整可能にしている。The adjustment screw 56 is attached to the left end of the brake pedal 50,
The return position of the brake pedal 50 is adjustable.
第１のばね受部材５７は、プランジャ５５に設けられた
孔５８と嵌合する保合部５９を備えており、この係合部
５９を孔５８に嵌合することにより、プランジャ５５に
支持されている。The first spring receiving member 57 includes a retaining portion 59 that fits into a hole 58 provided in the plunger 55. By fitting the engaging portion 59 into the hole 58, the first spring receiving member 57 is supported by the plunger 55. ing.
なお、係合部５９と孔５８との嵌合は、圧入である必要
はなく、第１のばね受部材５７がプランジャ５５に対し
横方向に移動しないよう制約すればよい。Note that the fitting between the engaging portion 59 and the hole 58 does not need to be press-fitting, and it is sufficient to restrict the first spring receiving member 57 from moving laterally with respect to the plunger 55.
また、第１のばね受部材５１は螺合等一般的保合機構に
よって、プランジャ５５に取付けられてもよい。Further, the first spring receiving member 51 may be attached to the plunger 55 by a general locking mechanism such as screwing.
第１のばね受部材５７と第１のピストン７との間には第
１のばね６０が設げられてぃる。A first spring 60 is provided between the first spring receiving member 57 and the first piston 7.
第２のばね受部材６１は、第１のばね受部材５７の下端
と係合し得るフランジ部６２を有し、その上方に形成し
た軸部は第１のばね受部材５７に設けられた案内孔６３
に摺動自在に嵌合している。The second spring receiving member 61 has a flange portion 62 that can engage with the lower end of the first spring receiving member 57, and a shaft portion formed above the flange portion 62 is connected to a guide provided on the first spring receiving member 57. hole 63
It is slidably fitted.
そして、第２のばね受部材６１と第１のピストン７との
間に第２のばね６４が設けられている。A second spring 64 is provided between the second spring receiving member 61 and the first piston 7.
ピストン７に設けられた柱状の突起６６は、第２のばね
受部材６１に穿設された孔６５を貫通して上方に延び、
頂部にボルト６γにより取付けられた停止板６８を備え
ている。A columnar projection 66 provided on the piston 7 extends upward through a hole 65 formed in the second spring receiving member 61.
It has a stop plate 68 attached to the top with bolts 6γ.
この停止板６８は、ブレーキペダル５０がブレーキ弛め
位置すなわち図に示す位置にあるとき、第１のばね受部
材５７及び第２のばね受部材６１の上端部と当接し、両
ばね受部材５７及び６１の上限位置を規定している。When the brake pedal 50 is in the brake release position, that is, the position shown in the figure, this stop plate 68 comes into contact with the upper ends of the first spring receiver member 57 and the second spring receiver member 61, and both spring receiver members 57 and 61 upper limit positions are defined.
このとき、ばね６０及び６４のばね力は零又は非常に小
さい。At this time, the spring force of springs 60 and 64 is zero or very small.
また、ブレーキペダル５０が踏み込まれるとき、孔５４
とプランジャ５５との間の僅かな嵌合隙間のため、プラ
ンジャ５５が揺動運動を生じ、第１のばね受部材５７が
横方向に移動し、従って第２のばね受部材６１が横方向
に移動する。Further, when the brake pedal 50 is depressed, the hole 54
Due to the slight fitting gap between the plunger 55 and the plunger 55, the plunger 55 causes a rocking movement, the first spring receiving member 57 moves laterally, and therefore the second spring receiving member 61 moves laterally. Moving.
しかし、柱状突起６６と第２のばね受部材６１の穴６５
との間隙はその横方向移動より十分大きく設定されてい
る。However, the columnar projection 66 and the hole 65 of the second spring receiving member 61
The gap is set to be sufficiently larger than the lateral movement thereof.
ブーツ７０はプランジャ５５と上蓋部材４との間に装着
されており、また、通孔７１は第１のピストン７の上部
に形成された室を排気孔２９ ３４及び排気口４４を介
して大気に連通ずる。The boot 70 is installed between the plunger 55 and the upper cover member 4, and the through hole 71 connects the chamber formed in the upper part of the first piston 7 to the atmosphere through the exhaust hole 29, 34 and the exhaust port 44. Communicate.
次にこの実施例の作用について説明する。Next, the operation of this embodiment will be explained.
運転者がブレーキをかけるため、ブレーキペダル５０を
踏み込むと、ブレーキペダル５０は回転軸５１を中心に
矢印Ａの方向に回転し、ローラ５３によりプランジャ５
５を下方に押し、第１のばね受部材５７を介して第１の
ばね６０を圧縮する。When the driver depresses the brake pedal 50 to apply the brakes, the brake pedal 50 rotates in the direction of arrow A around the rotating shaft 51, and the plunger 5 is rotated by the roller 53.
5 downward to compress the first spring 60 via the first spring receiving member 57.
すると、第１のピストン７は第１のばね６０により下方
に移動し、排気弁座２６が第１０給排弁部材２５に係合
して排気弁を閉じた後、給排弁部材２５が供給弁座２７
から離座して供給弁を開き、供給口２３を通して一方の
系統の流体圧力源から供給された圧力流体が、供給弁を
通して送出室１０に供給され、送出口９を介して、一方
の系統のプレーキチャンバに又は中継弁を介してプレー
キチャンバに供給され、その系統のブレーキが作用する
。Then, the first piston 7 is moved downward by the first spring 60, and after the exhaust valve seat 26 engages with the tenth supply/discharge valve member 25 and closes the exhaust valve, the supply/discharge valve member 25 closes the supply/discharge valve member 25. Valve seat 27
The pressure fluid supplied from the fluid pressure source of one system through the supply port 23 is supplied to the delivery chamber 10 through the supply valve, and the pressure fluid is supplied to the delivery chamber 10 through the delivery port 9 to the fluid pressure source of one system through the supply port 23. The brake fluid is supplied to the brake chamber or via a relay valve, and the brake of that system is activated.
このとき、送出室１０の圧力流体は通孔１１を通してリ
アクション室１２に供給され、リアクション室１２の圧
力が送出室１０の圧力に追随して上昇する。At this time, the pressure fluid in the delivery chamber 10 is supplied to the reaction chamber 12 through the through hole 11, and the pressure in the reaction chamber 12 increases following the pressure in the delivery chamber 10.
リアクション室１２の流体圧力すなわち実質的に送出室
１０の流体圧力によりピストン１を上方に押圧する力が
、第１のばね６０を介して作用するプランジャ５５の押
力に等しくなると、戻しばね３１によりピストン７がわ
ずかに上動し、供給弁が閉じ、送出室１０の流体圧力は
ブレーキペダル５０に加えられた踏力に比例した値に保
たれる。When the force pushing the piston 1 upward by the fluid pressure in the reaction chamber 12, that is, substantially the fluid pressure in the delivery chamber 10, becomes equal to the pushing force of the plunger 55 acting through the first spring 60, the return spring 31 The piston 7 moves up slightly, the supply valve closes, and the fluid pressure in the delivery chamber 10 is maintained at a value proportional to the depression force applied to the brake pedal 50.
第１の送出室１０の流体圧力が上昇し始めると同時に、
その送出室１０の圧力流体が通孔１５を通って中継室１
６に供給される。At the same time as the fluid pressure in the first delivery chamber 10 begins to rise,
The pressure fluid in the delivery chamber 10 passes through the through hole 15 to the relay chamber 1.
6.
すると、第２のピストン１３はその中継室１６の流体圧
力を受けて下方に移動し、排気弁座４３が第２の給排弁
部材３３に係合して排気弁が閉じ、給排弁部材３３が供
給弁座４２から離座して供給弁が開き、他方の系統の流
体圧力源からの圧力流体が、供給口４０及び供給弁を通
って第２の送出室１８に供給され、更に、送出口１７を
通って他方の系統のプレーキチャンバ又は中継弁に供給
され、その系統のブレーキが作用する。Then, the second piston 13 moves downward in response to the fluid pressure in the relay chamber 16, and the exhaust valve seat 43 engages with the second supply/discharge valve member 33 to close the exhaust valve. 33 is removed from the supply valve seat 42 to open the supply valve, and pressurized fluid from the fluid pressure source of the other system is supplied to the second delivery chamber 18 through the supply port 40 and the supply valve, and further, It is supplied to the brake chamber or relay valve of the other system through the outlet 17, and the brake of that system is activated.
そして、送出室１８の圧力が中継室１６の圧力すなわち
第１の送出室１０の圧力に等しくなると供給弁が閉じ、
第１の送出室１０の圧力に実質的に等しく保たれる。Then, when the pressure in the delivery chamber 18 becomes equal to the pressure in the relay chamber 16, that is, the pressure in the first delivery chamber 10, the supply valve closes.
The pressure in the first delivery chamber 10 is kept substantially equal.
ブレーキペダル５０が更に強く踏み込まれ、第１のばね
６０の圧縮量が所定の値以上になると、第１のばね１受
部材５７の下端が第２のばね受部材６１のフランジ部６
２に係合する。When the brake pedal 50 is further depressed and the amount of compression of the first spring 60 exceeds a predetermined value, the lower end of the first spring 1 receiving member 57 touches the flange portion 6 of the second spring receiving member 61.
2.
そのため、第１のピストン７はグランジャ５５により第
１及び第２のばね６０及び６４を介して下方に押圧され
る。Therefore, the first piston 7 is pressed downward by the granger 55 via the first and second springs 60 and 64.
すると、前述と同様に供給弁が開き、一方の系統の流体
圧力源からの圧力流体が供給口２３及び供給弁を通って
再び第１の送出室１０に供給され、送出室１０の流体圧
力が上昇すると共に、より高い圧力の圧力流体が送出口
９より一方の系統のプレーキチャンバ又は中継弁に供給
される。Then, the supply valve opens in the same manner as described above, and the pressure fluid from the fluid pressure source of one system is supplied to the first delivery chamber 10 again through the supply port 23 and the supply valve, and the fluid pressure in the delivery chamber 10 is increased. As the pressure rises, higher pressure fluid is supplied from the outlet 9 to the brake chamber or relay valve of one system.
そして、送出室１０の流体圧力従ってリアクション室１
２の流体圧力によりピストン７を上方に押圧する力が第
１及び第２のばね６０及び６４により加えられる押力に
等し《なると、ピス１ンγはわずかに上動し、供給弁が
閉じ圧力は一定に保たれる。Then, the fluid pressure in the delivery chamber 10 and the reaction chamber 1
When the force pushing the piston 7 upward due to the fluid pressure of the first and second springs 60 and 64 becomes equal to the pushing force applied by the first and second springs 60 and 64, the piston 1 moves upward slightly and the supply valve closes. The pressure remains constant.
それと同時に、第１の送出室１０の流体圧力が上昇する
と、中継室１６の圧力が上昇し、第２のピストン１３が
下動して供給弁が開へそのため、第２の送出室１８の流
体圧力が中継室１６の圧力に等しくなるまで上昇し、他
方の系統のプレーキチャンバ又は中継弁に送出口１７を
通して、より高い圧力の圧力流体が供給される。At the same time, when the fluid pressure in the first delivery chamber 10 increases, the pressure in the relay chamber 16 increases, the second piston 13 moves downward, and the supply valve opens, so that the fluid in the second delivery chamber 18 increases. The pressure increases until it becomes equal to the pressure in the relay chamber 16, and higher pressure fluid is supplied to the brake chamber or relay valve of the other system through the outlet 17.
この操作の際、プランジャ５５は第１及び第２のばね６
０及び６４を圧縮するので、ブレーキペダルの踏力に対
する踏み込み量は、その踏力が小さ《第１のばね６０の
みを圧縮する場合に比して小さい値となる。During this operation, the plunger 55 is connected to the first and second springs 6
0 and 64, the amount of depression of the brake pedal with respect to the depression force becomes a smaller value than when the depression force is small (compared to the case where only the first spring 60 is compressed).
ブレーキを弛めるため、ブレーキペダル５０に加えてい
る踏力を取り除くと、第１のピストン７はリアクション
室１２の流体圧力及び戻しばね３１のばね力により上方
に移動し、排気弁座２６が第１０給排弁２５から離れ排
気弁が開く。When the pedal force applied to the brake pedal 50 is removed in order to release the brake, the first piston 7 moves upward due to the fluid pressure in the reaction chamber 12 and the spring force of the return spring 31, and the exhaust valve seat 26 moves toward the tenth piston 7. It moves away from the exhaust valve 25 and the exhaust valve opens.
すると、送出室１０及びリアクション室１２の圧力流体
が排気孔２９ ３４及び排気口４４を通って大気に排気
されると共に、一方の系統のプレーキチャンバあるいは
中継弁に供給されている圧力流体が送出口９、送出室１
０及び排気孔２９及び３４を通って排気され、一方の系
統のブレーキが弛む。Then, the pressure fluid in the delivery chamber 10 and the reaction chamber 12 is exhausted to the atmosphere through the exhaust holes 29 to 34 and the exhaust port 44, and the pressure fluid supplied to the brake chamber or relay valve of one system is discharged from the delivery port. 9. Delivery chamber 1
0 and through the exhaust holes 29 and 34, and the brakes of one system are released.
それと共に、中継室１６の圧力が流体が通孔１５を通っ
て排気されるので、第２のピストン１３が第２の送出室
１８の流体圧力及び戻しばね３２のばね力により上方に
移動し、排気弁座４３が給排弁部材３３から離れ排気弁
が開く。At the same time, since the pressure in the relay chamber 16 is exhausted through the through hole 15, the second piston 13 is moved upward by the fluid pressure in the second delivery chamber 18 and the spring force of the return spring 32. The exhaust valve seat 43 separates from the supply/discharge valve member 33 and the exhaust valve opens.
従って、送出室１８の圧力流体が排気孔３４より排気さ
れると共に、他方の系統のプレーキチャンバあるいは中
継弁に供給されている圧力流体が送出口１γ、送出室１
８及び排気孔３４を通って排気され、他方の系統のブレ
ーキもゆるむ。Therefore, the pressure fluid in the delivery chamber 18 is exhausted from the exhaust hole 34, and the pressure fluid supplied to the brake chamber or relay valve of the other system is transferred to the delivery port 1γ and the delivery chamber 1.
8 and the exhaust hole 34, and the brakes of the other system are also loosened.
このブレーキ弁の作動の際、プランジャ５５は揺動運動
を含んで下方に移動するので、第１のばね受部材５７は
横方向に振れながらプランジャ５５の下端と一体になっ
て下方に移動する。When the brake valve is actuated, the plunger 55 moves downward including a rocking motion, so the first spring receiving member 57 swings laterally and moves downward integrally with the lower end of the plunger 55.
しかし、第１のばね受部材５７０案内孔６３に嵌合した
第２のばね受部材６１の穴６５と第１のピストン７の柱
状突起６６との間には十分な隙間が設けられているので
、穴６５の内面と柱状突起６６の外面とが当たることは
ない。However, since a sufficient gap is provided between the hole 65 of the second spring receiving member 61 fitted into the guide hole 63 of the first spring receiving member 570 and the columnar projection 66 of the first piston 7. , the inner surface of the hole 65 and the outer surface of the columnar projection 66 never come into contact with each other.
なお、ブレーキペダル５０の踏み込み量が小さく、第２
のばね６４が圧縮されないときには、停止板６８は第２
のばね受部材６１の上端面に当接しているが、このとき
第２のばね６４の第２のばね受部材６１に作用するばね
力は零かあるいは非常に小さいため、その当接面には摩
擦力はほとんど作用しない。Note that the amount of depression of the brake pedal 50 is small and the second
When the spring 64 is not compressed, the stop plate 68
The second spring 64 is in contact with the upper end surface of the spring receiving member 61, but since the spring force acting on the second spring receiving member 61 at this time is zero or very small, the contact surface is Frictional force hardly acts.
従って、第１のピストン７には、第１のばね６０または
、第１及び第２のばね６０及び６４を介してのみ押力が
伝達されるので、プランジャ５５の揺動による偏荷重が
ピストンＩに作用することはない。Therefore, since the pushing force is transmitted to the first piston 7 only via the first spring 60 or the first and second springs 60 and 64, the unbalanced load due to the swinging of the plunger 55 is transferred to the piston I. It has no effect on
その結果、第１のピストンγと第１のシリンダ孔２との
間にこじれを生ずることがなくなるので、第１のピスト
ン７が第１のシリンダ孔２内を滑らか１に移動すること
ができ、その両者の摺動面にエア一漏れを引き起こすよ
うな偏摩耗を生じることもない。As a result, no distortion occurs between the first piston γ and the first cylinder hole 2, so the first piston 7 can move smoothly within the first cylinder hole 2, Uneven wear that causes air leakage does not occur on both sliding surfaces.
そしてさらに、第２のばね受部材６１が、柱状突起６６
に接触することなく、第１のばね受部材５１によっての
み半径方向に支持されているため、第２のばね受部材６
１の穴６５内面と柱状突起６６の外面との間に摩擦を生
じないのはもちろんのこと、プランジャ５５の揺動に対
して第２のばね受部材６１と第１のばね受部材５７とが
一体となって横方向に振れるので、第１のばね受部材５
７０案内孔６３と第２のばね受部材６１の軸部との間の
摺動面に偏荷重が作用することはないそれゆえ、第１の
ばね受部材５１と第２のばね受部材６１との間、および
第２のばね受部材６１と柱状突起６６との間には、段付
摩耗を招くようなこじれが発生せず、第１のばね受部材
５７が第２のばね受部材６１に対して、第２のばね受部
材６１が第１のピストン７に対して滑らかに移動するこ
とができる。Furthermore, the second spring receiving member 61 has the columnar projection 66
Since it is supported in the radial direction only by the first spring receiving member 51 without contacting the second spring receiving member 6
Not only does friction not occur between the inner surface of the first hole 65 and the outer surface of the columnar projection 66, but also the second spring receiving member 61 and the first spring receiving member 57 are protected against the swinging of the plunger 55. Since it can swing laterally as a unit, the first spring receiving member 5
70 An unbalanced load does not act on the sliding surface between the guide hole 63 and the shaft portion of the second spring receiving member 61. Therefore, the first spring receiving member 51 and the second spring receiving member 61 There is no twisting that would cause stepped wear between the second spring receiving member 61 and the columnar protrusion 66, and the first spring receiving member 57 is connected to the second spring receiving member 61. On the other hand, the second spring bearing member 61 can move smoothly with respect to the first piston 7.
上述したように、第１のピストン７、第１及び第２のば
ね受部材５７．６１の各各が滑らかに移動し得るので、
ブレーキペダルの移動も滑らかに行なわれ、円滑に作動
するブレーキ弁を得ることができる。As described above, since each of the first piston 7 and the first and second spring bearing members 57, 61 can move smoothly,
The brake pedal moves smoothly, and a brake valve that operates smoothly can be obtained.
また、穴６５の内面と柱状突起６６の外面との間に摺動
面を設けていないので、それらの面を精度よく加工する
必要がなく、第１のピストン１、第２のばね受部材６１
の加工を簡略化できる。Further, since there is no sliding surface between the inner surface of the hole 65 and the outer surface of the columnar projection 66, there is no need to process these surfaces with high precision, and the first piston 1 and the second spring receiving member 61
Processing can be simplified.
以上の説明からも明らかなように、本発明は、第１のば
ね受部材をプランジャに支持させると共に、第２のばね
受部材を第１のばね受部材により軸方向に移動可能に案
内支持したことにより、第１及び第２のばね受部材とピ
ストンとの保合を無くすることができるので、プランジ
ャの揺動が第１及び第２のばね受部材を介してピストン
に伝達されてピストンに偏荷重が加わることがなく、さ
らに、第２のばね受部材とピストンとの間はもちろんの
こと、第１のばね受部材と第２のばね受部材との摺動面
にも偏荷重が作用することがない。As is clear from the above description, the present invention has the first spring bearing member supported by the plunger, and the second spring bearing member guided and supported by the first spring bearing member so as to be movable in the axial direction. By doing so, it is possible to eliminate the engagement between the first and second spring bearing members and the piston, so that the swinging motion of the plunger is transmitted to the piston via the first and second spring bearing members, and is transmitted to the piston through the first and second spring bearing members. No unbalanced load is applied, and the unbalanced load acts not only between the second spring bearing member and the piston, but also on the sliding surfaces of the first spring bearing member and the second spring bearing member. There's nothing to do.
従ッて、ピストンとシリンダ孔との間、第１のばね受部
材と第２のばね受部材との間、および第２のばね受部材
とピストンとの間にこじれが発生しないので、ピストン
、第１のばね受部材及び第２のばね受部材の各々が円滑
に移動することができ、よってブレーキペダルの移動を
円滑になし得、また、ピストンとシリンダ孔との摺動面
の偏摩耗によるエアー漏れや第１のばね受部材と第２の
ばね受部材との摺動面の段付摩耗を防止することができ
、さらにまた、第２のばね受部材とピストンとの間の摺
動面を不要にしたことによりそれらの加工が簡単になる
等の顕著な効果を奏する。Therefore, since no twisting occurs between the piston and the cylinder hole, between the first spring bearing member and the second spring bearing member, and between the second spring bearing member and the piston, the piston, Each of the first spring bearing member and the second spring bearing member can move smoothly, and therefore the brake pedal can be moved smoothly. It is possible to prevent air leakage and stepped wear of the sliding surface between the first spring receiving member and the second spring receiving member, and furthermore, the sliding surface between the second spring receiving member and the piston. By eliminating the need for these, there are significant effects such as simplification of processing.
図は本発明の一実施例を示す二系統用ブレーキ弁の断面
図である。
１・・・・・・弁本体、２，３・・・・・・シリンダ孔
、７，１３・・・・・・ピストン、５０・・・・・・ブ
レーキヘタル、５５・・・・・・プランジャ、５７・・
・・・・第１のばね受部材、５８・・・・・・孔、５９
・・・・・・係合部、６０・・・・・・第１のばね、６
１・・・・・・第２のばね受部材、６３・・・・・・案
内孔、６４・・・・・・第２のばねっThe figure is a sectional view of a dual-system brake valve showing an embodiment of the present invention. 1... Valve body, 2, 3... Cylinder hole, 7, 13... Piston, 50... Brake head, 55... Plunger, 57...
...First spring receiving member, 58 ... Hole, 59
...Engagement portion, 60...First spring, 6
1...Second spring receiving member, 63...Guide hole, 64...Second spring
Claims (1)
の流体圧作動機器に接続する送出口、大気に連通ずる排
気口を各々備えた弁本体と、該弁本体に設けたシリンダ
孔と、前記供給口と前記送出口との間及び前記送出口と
前記排気口との間の連通路を開閉する給排弁と、前記シ
リンダ孔に摺動自在に挿入され、前記給排弁と係合して
これを操作するピストンと、前記弁本体の上端に固定し
た上蓋部材に前記シリンダ孔と同心に設けた孔内に摺動
自在に挿入され、ブレーキペダルにより駆動されるプラ
ンジャと、第１のばね受け部材を介して前記プランジャ
の押力を受け前記ピストンを押圧する第１のばねと、該
第１のばねに並設され、該第１のばねが所定値以上圧縮
されたとき７ランジ部が前記第１のばね受け部材に当接
する第２のばね受け部材を介して前記プランジャの押力
を受け、前記ピストンを押圧する第２のばねとを備え、
前記第１のばね受け部材に設けた係合部を前記プランジ
ャに係合して、前記第１のばね受け部材を前記プランジ
ャにより支持すると共に、前記第２のばね受け部材の軸
部を前記第１のばね受部材に設けた案内孔に軸方向に移
動可能に嵌合し、前記第２のばね受げ部材を前記第１の
ばね受げ部材により案内してなるエアーブレーキ装置用
ブレーキ弁。1. A valve body having a supply port connected to a fluid pressure source, a discharge port connected to a fluid pressure operated device such as a brake chamber, and an exhaust port communicating with the atmosphere; a cylinder hole provided in the valve body; a supply/discharge valve that opens and closes a communication path between the port and the outlet and between the outlet and the exhaust port, and a supply/discharge valve that is slidably inserted into the cylinder hole and engaged with the supply/discharge valve. a piston that operates the valve body; a plunger that is slidably inserted into a hole provided in a top lid member fixed to the upper end of the valve body and coaxial with the cylinder hole and is driven by a brake pedal; and a first spring receiver. a first spring that receives the pushing force of the plunger through a member and presses the piston; and a first spring that is arranged in parallel with the first spring, and when the first spring is compressed to a predetermined value or more, the seven langes are compressed. a second spring that receives the pushing force of the plunger via a second spring receiving member that contacts the first spring receiving member and presses the piston;
An engaging portion provided on the first spring receiving member is engaged with the plunger to support the first spring receiving member by the plunger, and the shaft portion of the second spring receiving member is supported by the plunger. A brake valve for an air brake device, which is fitted into a guide hole provided in a first spring receiving member so as to be movable in the axial direction, and the second spring receiving member is guided by the first spring receiving member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12498479A JPS598583B2 (en) | 1979-09-27 | 1979-09-27 | Brake valve for air brake equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12498479A JPS598583B2 (en) | 1979-09-27 | 1979-09-27 | Brake valve for air brake equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5647350A JPS5647350A (en) | 1981-04-30 |
| JPS598583B2 true JPS598583B2 (en) | 1984-02-25 |
Family
ID=14899040
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12498479A Expired JPS598583B2 (en) | 1979-09-27 | 1979-09-27 | Brake valve for air brake equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS598583B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH048625Y2 (en) * | 1984-07-21 | 1992-03-04 |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2119464B (en) * | 1982-03-17 | 1985-03-20 | Lucas Ind Plc | Improvements in dual brake valves |
-
1979
- 1979-09-27 JP JP12498479A patent/JPS598583B2/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH048625Y2 (en) * | 1984-07-21 | 1992-03-04 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5647350A (en) | 1981-04-30 |
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