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
Links
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 230000005540 biological transmission Effects 0.000 description 7
- 244000145845 chattering Species 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
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)
- Mechanically-Actuated Valves (AREA)
- Multiple-Way 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.
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)
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.
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)
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)
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 |
-
1978
- 1978-09-12 JP JP1978124377U patent/JPS6336161Y2/ja not_active Expired
-
1979
- 1979-09-05 GB GB7930705A patent/GB2032062B/en not_active Expired
- 1979-09-10 FR FR7922567A patent/FR2436271A1/en active Granted
- 1979-09-11 CA CA335,420A patent/CA1114718A/en not_active Expired
Also Published As
Publication number | Publication date |
---|---|
JPS5541612U (en) | 1980-03-17 |
FR2436271B1 (en) | 1983-03-25 |
GB2032062A (en) | 1980-04-30 |
GB2032062B (en) | 1983-01-06 |
FR2436271A1 (en) | 1980-04-11 |
CA1114718A (en) | 1981-12-22 |
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