JPS6336161Y2 - - Google Patents

Info

Publication number
JPS6336161Y2
JPS6336161Y2 JP1978124377U JP12437778U JPS6336161Y2 JP S6336161 Y2 JPS6336161 Y2 JP S6336161Y2 JP 1978124377 U JP1978124377 U JP 1978124377U JP 12437778 U JP12437778 U JP 12437778U JP S6336161 Y2 JPS6336161 Y2 JP S6336161Y2
Authority
JP
Japan
Prior art keywords
spool
hole
outlet port
pressure receiving
rod
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
Application number
JP1978124377U
Other languages
Japanese (ja)
Other versions
JPS5541612U (en
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed filed Critical
Priority to JP1978124377U priority Critical patent/JPS6336161Y2/ja
Priority to GB7930705A priority patent/GB2032062B/en
Priority to FR7922567A priority patent/FR2436271A1/en
Priority to CA335,420A priority patent/CA1114718A/en
Publication of JPS5541612U publication Critical patent/JPS5541612U/ja
Application granted granted Critical
Publication of JPS6336161Y2 publication Critical patent/JPS6336161Y2/ja
Expired legal-status Critical Current

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Classifications

    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/14—Fluid pressure control
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
    • B60W30/18—Propelling the vehicle
    • B60W30/18009—Propelling the vehicle related to particular drive situations
    • B60W30/18063—Creeping
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0209—Control by fluid pressure characterised by fluid valves having control pistons, e.g. spools
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0212—Details of pistons for master or slave cylinders especially adapted for fluid control
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0221—Valves for clutch control systems; Details thereof

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Automation & Control Theory (AREA)
  • Transportation (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Multiple-Way Valves (AREA)
  • Mechanically-Actuated Valves (AREA)

Description

【考案の詳細な説明】 本考案は、油圧バランス式インチングバルブ、
主として建設機械の油圧回路に用いられる油圧バ
ランス式インチングバルブに関する。[Detailed description of the invention] This invention consists of a hydraulically balanced inching valve,
This invention relates to hydraulically balanced inching valves mainly used in hydraulic circuits of construction machinery.

従来この種のインチングバルブとして第１図に
示すものが公知である。すなわち、弁本体ａに、
弁孔ｂを穿設すると共に、液圧源、例えばトルク
フローミツシヨンコントロールバルブにおけるモ
ジユレートバルブに接続される入口ポートｃと、
図示しない変速機のクラツチへ接続される出口ポ
ートｄをそれぞれ設け、前記弁孔ｂ内に、スプー
ルｅをスライド自在に嵌挿すると共に、該スプー
ルｅの中央部に前記入口ポートｃと前記出口ポー
トｄとを連通する括れ部ｆを形成し、前記スプー
ルｅの軸心に、インチングペダルｇに連係された
ロツドｈをスライド自在に挿通し、かつ該スプー
ルｅとロツドｈとの間に調整バネｉを弾装し、前
記スプールｅの一方寄りに、当該スプールｅを他
方側（図示では左方側）へ押圧する受圧部ｊを設
けると共に、該受圧部ｊを半径方向の絞りｋを介
して前記出口ポートｄに連通し、前記ロツドｈの
他方寄りに、当該ロツドｈを一方側（図示では右
方側）へ押圧する受圧部ｌを設けると共に、該受
圧部ｌを前記弁本体ａに設けた通路ｎを介して前
記出口ポートｄに連通し、しかも前記各受圧部
ｊ，ｌの面積は一応等しく形成される構成であ
る。 The inching valve shown in FIG. 1 is conventionally known as this type of inching valve. That is, in the valve body a,
an inlet port c having a valve hole b and connected to a hydraulic pressure source, such as a modulating valve in a torque flow transmission control valve;
An outlet port d connected to a clutch of a transmission (not shown) is provided, and a spool e is slidably inserted into the valve hole b, and the inlet port c and the outlet port are provided in the center of the spool e. A rod h connected to the inching pedal g is slidably inserted into the axis of the spool e, and an adjustment spring i is provided between the spool e and the rod h. A pressure receiving portion j is provided on one side of the spool e to press the spool e toward the other side (left side in the figure), and the pressure receiving portion j is A pressure receiving part l is provided on the other side of the rod h that communicates with the outlet port d and presses the rod h to one side (to the right in the illustration), and the pressure receiving part l is provided on the valve body a. The pressure receiving portions j and l communicate with the outlet port d via a passage n, and the areas of the pressure receiving portions j and l are approximately equal.

そして、第１図図示の状態は、インチングペダ
ルｇの戻しバネｍの付勢力によりロツドｈが右方
に押され、また調整バネｉも圧縮され、スプール
ｅを右方へ押しつけて当該スプールｅの括れ部ｆ
を広く開放して入口ポートｃと出口ポートｄを導
通しているものであつて、液圧源、例えばトルク
フローミツシヨンコントロールバルブにおけるモ
ジレートバルブ（図示せず）より入口ポートｃに
導入された油圧は、広く開放された括れ部ｆを介
して出口ポートｄに流入し、図示しない変速機の
クラツチへ送られるものであり、この場合入口ポ
ートｃと出口ポートｄの油圧は同じである。 In the state shown in FIG. 1, the rod h is pushed to the right by the biasing force of the return spring m of the inching pedal g, and the adjustment spring i is also compressed, pushing the spool e to the right. Constriction f
is wide open and communicates between inlet port c and outlet port d, and is introduced into inlet port c from a hydraulic pressure source, such as a modulate valve (not shown) in a torque flow transmission control valve. The oil pressure flows into the outlet port d through the wide open constriction f and is sent to a transmission clutch (not shown), in which case the oil pressures at the inlet port c and the outlet port d are the same.

インチングペダルｇを踏み込むと、ロツドｈは
図示左方に引き出され、調整バネｉの弾撥力は弱
まり、その結果、受圧部ｊの油圧力がスプールｅ
を左方へ移動し入口ポートｃと出口ポートｄとの
連通を遮断しようとして油の流入を絞り、出口ポ
ートｄの油圧を入口ポートｃの油圧よりも低くす
る。このために、出口ポートｄ内の油圧を背圧と
する受圧部ｊに働らく油圧も低くなり、インチン
グペダルｇの踏み込みにより弱まつた調整バネｉ
の弾撥力とバランスする油圧力にまで減圧して出
口ポートｄ内の油圧力を調整するものであり、こ
のように、インチングペダルｇを踏み込みロツド
ｈを引き出し調整バネｉの弾撥力を弱めるに応じ
て受圧部ｊに働らく油圧力もバランスして低下
し、出口ポートｄ内の油圧力を減圧調整していく
ものである。 When the inching pedal g is depressed, the rod h is pulled out to the left in the figure, the elastic force of the adjustment spring i is weakened, and as a result, the hydraulic pressure of the pressure receiving part j is applied to the spool e.
is moved to the left to restrict the inflow of oil in an attempt to cut off communication between inlet port c and outlet port d, thereby making the oil pressure at outlet port d lower than the oil pressure at inlet port c. For this reason, the hydraulic pressure acting on the pressure receiving part j, which uses the hydraulic pressure in the outlet port d as back pressure, also decreases, and the adjustment spring i, which has weakened due to the depression of the inching pedal g,
The hydraulic pressure in the outlet port d is adjusted by reducing the pressure to a level that balances the elastic force of Accordingly, the hydraulic pressure acting on the pressure receiving part j also decreases in a balanced manner, and the hydraulic pressure inside the outlet port d is adjusted to be reduced.

前述の如き従来のインチングバルブにおいて
は、前述の如く、スプールｅの一方寄りに、当該
スプールｅを他方側（図示では左方側）へ押圧す
る受圧部ｊを設けると共に、ロツドｈの他方寄り
に、当該ロツドｈを一方側（図示では右方側）へ
押圧する受圧部ｌを設け、かつこれら受圧部ｊ，
ｌを一応同一面積とすると共に出口ポートｄに連
通したから、これら受圧部ｌに働らく油圧力は、
相反する方向でありかつ理想的には一応等しいも
のとなつて相殺されることになり、インチングペ
ダルｇには戻しバネｍの弾撥力のみが作用するこ
とになつて、インチングペダルｇの操作感覚が把
握し易いばかりか、操作力が軽減できる、という
ような利点が一応認められる。 In the conventional inching valve as described above, a pressure receiving part j is provided on one side of the spool e to press the spool e toward the other side (left side in the figure), and a pressure receiving part j is provided on the other side of the rod h. , a pressure receiving part l is provided that presses the rod h to one side (right side in the illustration), and these pressure receiving parts j,
Since l has the same area and communicates with the outlet port d, the hydraulic pressure acting on these pressure receiving parts l is:
The directions are contradictory, but ideally they are equal and cancel each other out, and only the elastic force of the return spring m acts on the inching pedal g, which improves the operational feeling of the inching pedal g. It can be seen that there are advantages in that it is not only easier to grasp, but also that the operating force can be reduced.

しかしながら、その反面、スプールの一方寄り
に設けた受圧部ｊは、出口ポートｄに近接しかつ
半径方向の絞りｋを介して出口ポートｄに連通す
る一方、ロツドｈの他方寄りに設けた受圧部ｌ
は、出口ポートｄから離隔しかつ弁本体ａに設け
た長い通路ｎを介して出口ポートｄに連通してい
るから、各受圧部Ｊ，ｌの面積を一応同一に形成
したとしても、出口ポートｄの油圧力を導入する
絞りｋ及び通路ｎの長さ及び径等の相違により、
各受圧部ｊ，ｌに働らく油圧力が同時かつ同一に
ならないものであり、しかも出口ポートｄの油圧
変動の激しさと相俟つて、その油圧変動に直ちに
追随できず、したがつてバランスに崩れが生じて
チヤタリングを起こしやすい欠点があつた。 However, on the other hand, the pressure receiving part j provided on one side of the spool is close to the outlet port d and communicates with the outlet port d via the radial throttle k, while the pressure receiving part j provided on the other side of the rod h l
is separated from the outlet port d and communicates with the outlet port d via a long passage n provided in the valve body a. Therefore, even if the areas of the pressure receiving parts J and l are made the same, the outlet port Due to the difference in the length and diameter of the throttle k and passage n that introduce the hydraulic pressure of d,
The hydraulic pressures acting on each pressure receiving part j and l are not the same at the same time, and combined with the severe oil pressure fluctuations at the outlet port d, it is not possible to immediately follow the oil pressure fluctuations, and therefore the balance is affected. It had the disadvantage of being prone to crumbling and causing chattering.

本考案は、上記事情に鑑み案出されたものであ
つて、操作力の軽減を図ると共に、出口ポートの
油圧変動に同時に応答してバランスに崩れが生せ
ずチヤタリングを起こすことのない油圧バランス
式インチングバルブを得ることを目的とするもの
である。 The present invention was devised in view of the above circumstances, and it aims to reduce the operating force and simultaneously respond to oil pressure fluctuations at the outlet port to maintain a hydraulic balance that does not cause imbalance and does not cause chattering. The purpose is to obtain a type inching valve.

以下本考案の実施例を第２図に基づいて説明す
る。 An embodiment of the present invention will be described below based on FIG. 2.

弁本体１に、弁孔１ａを穿設すると共に、液圧
源、例えばトルクフローミツシヨンコントロール
バルブにおけるモジユレートバルブ（図示せず）
に接続される入口ポート１1と、例えば変速機の
クラツチ（図示せず）へ接続される出口ポート１
２をそれぞれ設け、前記弁孔１ａ内に、筒状のス
プール２をスライド自在に嵌挿している。 A valve hole 1a is bored in the valve body 1, and a modulating valve (not shown) in a hydraulic pressure source, for example, a torque flow transmission control valve.
and an outlet port 1 connected to, for example, a transmission clutch (not shown).
2 , and a cylindrical spool 2 is slidably inserted into the valve hole 1a.

前記スプール２の中央部には、前記入口ポート
１1と前記出口ポート１2とを連通する括れ部２ａ
を形成すると共に、前記スプール２の両端部に
は、その一端面２1に開口する有底筒状の穴２ｂ
とその他端面２2に開口する有底筒状の穴２ｃと
を穿設している。 At the center of the spool 2, there is a constricted part 2a that communicates the inlet port 11 and the outlet port 12 .
At both ends of the spool 2, a cylindrical hole 2b with a bottom is formed at one end surface 21 of the spool 2.
and a bottomed cylindrical hole 2c that opens at the other end surface 22 .

他方、前記スプール２の軸心には、一端が弁本
体１外へ露出しインチングペダル（図示せず）に
連係されたロツド３がスライド自在に挿通されて
いる。 On the other hand, a rod 3 having one end exposed outside the valve body 1 and linked to an inching pedal (not shown) is slidably inserted into the axis of the spool 2.

前記スプール２の一端面２1に開口する前記穴
２ｂ内にはロードピストン４が嵌挿され、当該ロ
ードピストン４と前記穴２ｂの底壁及び内周壁と
で受圧室Ａを形成すると共に、該受圧室Ａは半径
方向の絞り５により当該スプール２の周面に開口
して前記出口ポート１2の油圧を受圧室Ａに導入
するように構成している。 A load piston 4 is inserted into the hole 2b opening on one end surface 21 of the spool 2, and the load piston 4, together with the bottom wall and inner peripheral wall of the hole 2b, form a pressure-receiving chamber A, which opens to the peripheral surface of the spool 2 by a radial restriction 5 so that the hydraulic pressure of the outlet port 12 is introduced into the pressure-receiving chamber A.

そして、前記ロードピストン４は、前記ロツド
３の他端に設けられた係止片６、例えばナツトに
係止されている。 The load piston 4 is locked to a locking piece 6, such as a nut, provided at the other end of the rod 3.

前記スプール２の他端面２2に開口する前記穴
２ｃの底壁と前記ロツド３のフランジ部３1との
間には調整バネ７が弾装されている。 An adjustment spring 7 is elastically mounted between the bottom wall of the hole 2c opening in the other end surface 22 of the spool 2 and the flange portion 31 of the rod 3.

なお、第２図において、８は弁孔１ａの一方の
開口を閉塞すると共に、前記スプール２の図示右
方向への移動を規制するプラグである。 In addition, in FIG. 2, 8 is a plug that closes one opening of the valve hole 1a and restricts the movement of the spool 2 in the right direction in the drawing.

しかして、液圧源、例えばモジユレートバルブ
（図示せず）より入口ポート１1に導入された油圧
は、第２図図示の状態、すなわちロツド３が右方
に押され、調整バネ７も圧縮されスプール２を右
方へ押しつけて当該スプール２の括れ部２ａを広
く開放して入口ポート１1と出口ポート１2を導通
している状態では、同一圧力でそのまま出口ポー
ト１2へ流入し、図示しない変速機のクラツチへ
送られるものである。この第２図図示の状態にお
いても、受圧室Ａには絞り５を介して出口ポート
１2の油圧が導入され、スプール２及びロードピ
ストン４の受圧面を押圧するが、スプール２の他
端面２2がロツド３のフランジ部３1の肩部に当接
し、またロードピストン４の外端部がナツト６に
当接係止しているから、その動きを規制され、し
かもこれら受圧面は同一面積であるから、押圧力
が相反する方向であつても互いに相殺され、ロツ
ド３に何らの偏倚力を生じさせないものである。 Therefore, the hydraulic pressure introduced into the inlet port 11 from a hydraulic pressure source, such as a modulating valve (not shown), causes the rod 3 to be pushed to the right and the adjustment spring 7 to be in the state shown in FIG. When compressed and the spool 2 is pressed to the right to widen the constricted portion 2a of the spool 2 and communicate between the inlet port 11 and the outlet port 12 , it flows directly into the outlet port 12 at the same pressure. , which is sent to a transmission clutch (not shown). Even in this state shown in FIG. 2, the hydraulic pressure of the outlet port 12 is introduced into the pressure receiving chamber A through the throttle 5, and presses the pressure receiving surfaces of the spool 2 and the load piston 4. 2 is in contact with the shoulder of the flange portion 31 of the rod 3, and the outer end of the load piston 4 is in contact with and locked in the nut 6, so its movement is restricted, and moreover, these pressure receiving surfaces have the same area. Therefore, even if the pressing forces are in opposite directions, they cancel each other out and do not produce any biasing force on the rod 3.

図示しないインチングペダルを踏んでロツド３
を図示左方に引くと、調整バネ７の弾撥力は弱ま
り、その結果受圧室Ａの油圧力がスプール２を左
方へ移動し、入口ポート１1と出口ポート１2との
連通を遮断しようとして油の流入を絞り、出口ポ
ート１2の油圧を入口ポート１1の油圧よりも低く
する。このために、出口ポート１2内の油圧を背
圧とする受圧室Ａに働らく油圧も低くなり、イン
チングペダルの踏み込みにより弱まつた調整バネ
７の弾撥力とバランスする油圧力にまで減圧して
出口ポート１2内の油圧力を調整するものである。 Press the inching pedal (not shown) and press Rod 3.
When pulled to the left in the figure, the elastic force of the adjustment spring 7 weakens, and as a result, the hydraulic pressure in the pressure receiving chamber A moves the spool 2 to the left, cutting off communication between the inlet port 1 1 and the outlet port 1 2 . This restricts the inflow of oil and makes the oil pressure at the outlet port 12 lower than the oil pressure at the inlet port 11 . For this reason, the hydraulic pressure acting on the pressure receiving chamber A, which uses the hydraulic pressure in the outlet port 12 as back pressure, becomes lower, and the pressure is reduced to a level that balances the elastic force of the adjustment spring 7, which has weakened due to the depression of the inching pedal. This is used to adjust the hydraulic pressure inside the outlet port 12 .

なお、インチングペダルを踏んでロツド３を左
方へ引き調整バネ７の弾撥力を弱める時は、ロツ
ド３の係止片６を介してロードピストン４が左方
へ動かされ受圧室Ａの容積が小さくなるだけであ
つて、スムーズに作動するものである。 When stepping on the inching pedal and pulling the rod 3 to the left to weaken the elastic force of the adjustment spring 7, the load piston 4 is moved to the left via the locking piece 6 of the rod 3, reducing the volume of the pressure receiving chamber A. However, it operates smoothly.

上述のように、本考案に係る油圧バランス式イ
ンチングバルブは、入口ポート１1と出口ポート
１2を有する弁本体１の弁孔１ａ内に、筒状であ
りかつ外周に前記入口ポート１1と前記出口ポー
ト１2とを連通する括れ部２ａを形成すると共に
その長手方向両端面２1，２2にそれぞれ開口する
有底筒状の穴２ｂ，２ｃを穿設したスプール２を
スライド自在に挿通し、該スプール２の軸心に、
一端が前記弁本体１外へ露出しインチングペダル
に連係されたロツド３をスライド自在に挿通し、
前記スプール２の一端面２1に開口する前記穴２
ｂ内にロードピストン４を嵌挿して、当該ロード
ピストン４の一端面と前記穴２ｂの底壁及び内周
壁とより成りかつ当該ロードピストン４の一端面
と前記穴２ｂの底壁とが同一面積の受圧面をなす
受圧室Ａを形成すると共に、前記ロードピストン
４を前記ロツド３の他端に設けた係止片６に係止
し、前記受圧室Ａを絞り５を介して前記出口ポー
ト１2に連通すると共に、前記スプール２の他端
面２2に開口する前記穴２ｃの底壁と前記ロツド
３の中間部に設けたフランジ部３1との間に、調
整バネ７を介在させたから、受圧室Ａにおけるス
プール２の受圧面及びロードピストン４の受圧面
に押圧力が働らいてもその相反する押圧力は互い
に相殺され、ロツド３に何らの偏倚力を生じさせ
ないものであり、したがつてロツド３の操作力が
軽減できるものであるばかりか、スプール２の受
圧面及びロードピストン４の受圧面は、同一の受
圧室Ａに面しているから、同時かつ同一の油圧力
を受けることになつて、出口ポート１2の油圧変
動に同時に応答してバランス崩れが生ぜず、チヤ
タリングを起こすことがなくなるものである。 As described above, the hydraulically balanced inching valve according to the present invention has a cylindrical shape in the valve hole 1a of the valve body 1, which has the inlet port 11 and the outlet port 12 , and has the inlet port 11 and the outlet port 12 on the outer periphery. A spool 2 having a constricted portion 2a communicating with the outlet port 1 2 and bottomed cylindrical holes 2 b and 2 c opening at both longitudinal end surfaces 2 1 and 2 2 , respectively, is slidably inserted into the spool 2 . At the axis of the spool 2,
A rod 3, one end of which is exposed outside the valve body 1 and connected to an inching pedal, is slidably inserted;
The hole 2 opens in one end surface 2 1 of the spool 2
A load piston 4 is inserted into the hole 2b, and the load piston 4 is made up of one end surface of the load piston 4 and the bottom wall and inner peripheral wall of the hole 2b, and the one end surface of the load piston 4 and the bottom wall of the hole 2b have the same area. The load piston 4 is locked to a locking piece 6 provided at the other end of the rod 3, and the pressure receiving chamber A is connected to the outlet port 1 through the throttle 5. 2 , and an adjustment spring 7 is interposed between the bottom wall of the hole 2c which is open to the other end surface 22 of the spool 2 and the flange portion 31 provided at the intermediate portion of the rod 3. Even if a pressing force acts on the pressure receiving surface of the spool 2 and the pressure receiving surface of the load piston 4 in the pressure receiving chamber A, the opposing pressing forces cancel each other out and do not cause any biasing force on the rod 3. Not only can the operating force of the rod 3 be reduced, but the pressure receiving surface of the spool 2 and the pressure receiving surface of the load piston 4 face the same pressure receiving chamber A, so that they receive the same hydraulic pressure at the same time. As a result, imbalance does not occur in response to oil pressure fluctuations at the outlet ports 12 at the same time, and chattering does not occur.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は従来のインチングバルブの断面図、第
２図は本考案の一実施例を示す断面図である。 １は弁本体、１1は入口ポート、１2は出口ポー
ト、１ａは弁孔、２はスプール、２ｂ，２ｃは盲
穴、３はロツド、３1はフランジ部、４はロード
ピストン、５は絞り、７は調整バネ、Ａは受圧
室。 FIG. 1 is a sectional view of a conventional inching valve, and FIG. 2 is a sectional view showing an embodiment of the present invention. 1 is the valve body, 1 1 is the inlet port, 1 2 is the outlet port, 1a is the valve hole, 2 is the spool, 2b, 2c are the blind holes, 3 is the rod, 3 1 is the flange part, 4 is the load piston, 5 is the The aperture, 7 is the adjustment spring, and A is the pressure receiving chamber.

Claims (1)

【実用新案登録請求の範囲】 入口ポート１1と出口ポート１2を有する弁本体
１の弁孔１ａ内に、筒状でありかつ外周に前記入
口ポート１1と前記出口ポート１2とを連通する括
れ部２ａを形成すると共にその長手方向両端面２
１，２2にそれぞれ開口する有底筒状の穴２ｂ，２
ｃを穿設したスプール２をスライド自在に挿通
し、 該スプール２の軸心に、一端が前記弁本体１外
へ露出しインチングペダルに連係されたロツド３
をスライド自在に挿通し、 前記スプール２の一端面２1に開口する前記穴
２ｂ内にロードピストン４を嵌挿して、当該ロー
ドピストン４の一端面と前記穴２ｂの底壁及び内
周壁とより成りかつ当該ロードピストン４の一端
面と前記穴２ｂの底壁とが同一面積の受圧面をな
す受圧室Ａを形成すると共に、前記ロードピスト
ン４を前記ロツド３の他端に設けた係止片６に係
止し、 前記受圧室Ａを絞り５を介して前記出口ポート
１2に連通すると共に、前記スプール２の他端面
２2に開口する前記穴２ｃの底壁と前記ロツド３
の中間部に設けたフランジ部３1との間に、調整
バネ７を介在させた ことを特徴とする油圧バランス式インチングバル
ブ。[Claims for Utility Model Registration] A valve hole 1a of a valve body 1 having an inlet port 11 and an outlet port 12 is cylindrical, and the inlet port 11 and the outlet port 12 communicate with each other on the outer periphery. A constricted portion 2a is formed, and both longitudinal end surfaces 2 of the constricted portion 2a are formed.
Bottomed cylindrical holes 2b and 2 open at 1 and 2 , respectively
A spool 2 having a hole c is slidably inserted thereinto, and a rod 3 having one end exposed outside the valve body 1 and connected to an inching pedal is attached to the axis of the spool 2.
The load piston 4 is slidably inserted into the hole 2b opened in the one end surface 21 of the spool 2, and the one end surface of the load piston 4 is connected to the bottom wall and inner peripheral wall of the hole 2b. A locking piece is provided at the other end of the rod 3 to form a pressure receiving chamber A in which one end surface of the load piston 4 and the bottom wall of the hole 2b form a pressure receiving surface of the same area. 6, communicates the pressure receiving chamber A with the outlet port 12 through the throttle 5, and connects the bottom wall of the hole 2c opening to the other end surface 22 of the spool 2 with the rod 3.
A hydraulically balanced inching valve characterized in that an adjustment spring 7 is interposed between a flange portion 31 provided at an intermediate portion of the inching valve.
JP1978124377U 1978-09-12 1978-09-12 Expired JPS6336161Y2 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP1978124377U JPS6336161Y2 (en) 1978-09-12 1978-09-12
GB7930705A GB2032062B (en) 1978-09-12 1979-09-05 Inching valves
FR7922567A FR2436271A1 (en) 1978-09-12 1979-09-10 HYDRAULIC BALANCING DISPENSER-METER
CA335,420A CA1114718A (en) 1978-09-12 1979-09-11 Inching valve of the hydraulic balance type

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1978124377U JPS6336161Y2 (en) 1978-09-12 1978-09-12

Publications (2)

Publication Number Publication Date
JPS5541612U JPS5541612U (en) 1980-03-17
JPS6336161Y2 true JPS6336161Y2 (en) 1988-09-26

Family

ID=14883886

Family Applications (1)

Application Number Title Priority Date Filing Date
JP1978124377U Expired JPS6336161Y2 (en) 1978-09-12 1978-09-12

Country Status (4)

Country Link
JP (1) JPS6336161Y2 (en)
CA (1) CA1114718A (en)
FR (1) FR2436271A1 (en)
GB (1) GB2032062B (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0214693Y2 (en) * 1984-09-29 1990-04-20
JPS61143915U (en) * 1985-02-28 1986-09-05
DE19815889A1 (en) * 1998-04-08 1999-10-14 Mannesmann Rexroth Ag Inch brake device
CN103527803A (en) * 2013-10-29 2014-01-22 合肥今典机械科技有限公司 End face whole-sealing structure for inching valve
US9582007B2 (en) 2014-08-21 2017-02-28 Louis P. Vickio, Jr. Pressure regulator

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB781651A (en) * 1900-01-01
GB375537A (en) * 1931-06-17 1932-06-30 Crosby Valve & Engineering Com Improvements relating to valves for controlling the flow of fluids
GB740631A (en) * 1953-02-16 1955-11-16 Charles Scott Prendergast Improvements relating to valves for regulating fluid flow
GB801951A (en) * 1956-05-23 1958-09-24 Jaroco Engineering Co A fluid-pressure control system for remotely controlling fluid control valves
GB885393A (en) * 1957-07-18 1961-12-28 Zahnradfabrik Friedrichshafen Improvements in and relating to pressure relief valves
GB847679A (en) * 1957-11-07 1960-09-14 Twin Disc Clutch Co Hydraulically actuated friction clutch
GB974907A (en) * 1962-05-31 1964-11-11 Davy & United Eng Co Ltd Fluid regulating valves

Also Published As

Publication number Publication date
GB2032062A (en) 1980-04-30
GB2032062B (en) 1983-01-06
FR2436271B1 (en) 1983-03-25
CA1114718A (en) 1981-12-22
JPS5541612U (en) 1980-03-17
FR2436271A1 (en) 1980-04-11

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