JPH0421016B2 - - Google Patents
Info
- Publication number
- JPH0421016B2 JPH0421016B2 JP20764984A JP20764984A JPH0421016B2 JP H0421016 B2 JPH0421016 B2 JP H0421016B2 JP 20764984 A JP20764984 A JP 20764984A JP 20764984 A JP20764984 A JP 20764984A JP H0421016 B2 JPH0421016 B2 JP H0421016B2
- Authority
- JP
- Japan
- Prior art keywords
- pilot
- spool
- control
- hole
- tank
- 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
- 230000007246 mechanism Effects 0.000 claims description 13
- 230000004043 responsiveness Effects 0.000 description 5
- 230000007935 neutral effect Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000004044 response Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2285—Pilot-operated systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
- F15B13/0422—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with manually-operated pilot valves, e.g. joysticks
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Description
【発明の詳細な説明】
〔発明の属する技術分野〕
本発明は建設機械における油圧式或いは電気一
油圧式の遠隔制御装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Technical field to which the invention pertains] The present invention relates to a hydraulic or electro-hydraulic remote control device for construction machinery.
従来の油圧式遠隔制御装置の一例を第3図によ
り述べる。アクチエータ11にはタンク12の油
を吸い込みかつ最高圧力をリリーフ弁13により
制御されている主ポンプ14の圧油が逆止弁15
と制御弁16を介して接続されている。17は主
ポンプ14の吐出量を制御する吐出量制御機構で
ある。制御弁16の両側の油室18および19は
リリーフ弁20により最高圧力を制御されている
パイロツトポンプ21の圧油が、運転室22内に
あるパイロツト減圧弁23を介して給排されるこ
とにより制御弁16を切換えてアクチエータ11
へポンプ14の圧油の給排を行つている。なおパ
イロツト減圧弁23によりアクチエータ11の制
御弁16を調整しているが、これと同様に図示し
ていない他のパイロツト減圧弁により吐出量制御
機構17の調整を行つている。
An example of a conventional hydraulic remote control device will be described with reference to FIG. The actuator 11 sucks oil from the tank 12 and the pressure oil from the main pump 14 whose maximum pressure is controlled by the relief valve 13 is connected to the check valve 15.
and is connected via a control valve 16. 17 is a discharge amount control mechanism that controls the discharge amount of the main pump 14. The oil chambers 18 and 19 on both sides of the control valve 16 are supplied and discharged with pressure oil from a pilot pump 21 whose maximum pressure is controlled by a relief valve 20 via a pilot pressure reducing valve 23 located in an operator's cab 22. By switching the control valve 16, the actuator 11
Pressure oil is supplied to and discharged from the pump 14. Although the control valve 16 of the actuator 11 is adjusted by the pilot pressure reducing valve 23, the discharge amount control mechanism 17 is similarly adjusted by another pilot pressure reducing valve (not shown).
第4図は制御弁16の油室18および19の細
部を示したもので、スプール26の両端部は弁箱
体27を貫通してカバー28内に凸出しその小径
部は一対の座金29を介してスプリング30が張
り渡されている。従つてパイロツト減圧弁23を
右側に倒すと左側のカバー28の穴31からパイ
ロツト圧力弁23の2次圧が流入し、スプール2
6は右側のスプリング30に抗して右進してポン
プ14の圧油はアクチエータ11のヘツド側に流
入する。ここでスプール26の直径をDストロー
クをlとしかつD=2.5cm l=1cmとするとス
プール26のストロークに必要なパイロツト減圧
弁23からの流量q=4.9c.c.になる。 FIG. 4 shows the details of the oil chambers 18 and 19 of the control valve 16. Both ends of the spool 26 pass through the valve body 27 and protrude into the cover 28, and its small diameter portion is fitted with a pair of washers 29. A spring 30 is stretched through the spring 30. Therefore, when the pilot pressure reducing valve 23 is tilted to the right, the secondary pressure of the pilot pressure valve 23 flows through the hole 31 of the cover 28 on the left side, and the spool 2
6 moves to the right against the spring 30 on the right side, and the pressure oil of the pump 14 flows into the head side of the actuator 11. Here, assuming that the diameter of the spool 26 is D stroke 1 and D=2.5 cm and 1 cm, the flow rate q from the pilot pressure reducing valve 23 required for the stroke of the spool 26 is 4.9 cc.
このような構成において制御弁16のストロー
ク調整或いは吐出量制御機構17の調整を行う場
合、オペレータにより操作されるパイロツト減圧
弁23を経て操作油量が例えば油室18或いは1
9に供給されるため、制御弁16と運転室22内
のパイロツト減圧弁23との位置が離れていると
パイロツト配管は長くなつて応答の遅れる欠点が
あつた。ここで応答性をよくするためパイロツト
減圧弁23のサイズを大きくすると操作力が重く
操作困難になる欠点があつた。 In such a configuration, when adjusting the stroke of the control valve 16 or adjusting the discharge amount control mechanism 17, the amount of operating oil is adjusted to, for example, the oil chamber 18 or 1 through the pilot pressure reducing valve 23 operated by the operator.
9, therefore, if the control valve 16 and the pilot pressure reducing valve 23 in the operator's cab 22 are located far apart, the pilot piping becomes long, resulting in a delay in response. Here, if the size of the pilot pressure reducing valve 23 is increased in order to improve responsiveness, there is a drawback that the operating force becomes heavy and operation becomes difficult.
従来の電気一油圧式遠隔制御装置は第5図に示
すように、コントローラ36により油室18或い
は19に接続されかつソレノイド39により制御
される電磁比例減圧弁37(図では油室18側の
みを示す)を制御する。なお38はバツテリーで
ある。このような構成であるからコントローラ3
6を左側に倒すと電磁比例制御弁37は励磁され
ることにより、パイロツトポンプ21の圧油を制
御弁16の油室18に送りアクチエータ11のヘ
ツド側にはポンプ14の圧油が流入する。このよ
うな構成では比較的小さな寸法即ち容量の小さい
電磁比例減圧弁37からの2次圧油により、前述
した第4図の説明で述べたように比較的大量の
4.9c.c.の流量を必要とするスプール26を移動さ
せるため応答性が悪かつた。 As shown in FIG. 5, the conventional electric-hydraulic remote control device has an electromagnetic proportional pressure reducing valve 37 connected to the oil chamber 18 or 19 by a controller 36 and controlled by a solenoid 39 (in the figure, only the oil chamber 18 side is connected to the oil chamber 18 or 19). control). Note that 38 is a battery. With this configuration, controller 3
6 to the left side, the electromagnetic proportional control valve 37 is energized, thereby sending the pressure oil of the pilot pump 21 to the oil chamber 18 of the control valve 16 and allowing the pressure oil of the pump 14 to flow into the head side of the actuator 11. In such a configuration, a relatively large amount of secondary pressure oil from the electromagnetic proportional pressure reducing valve 37 having a relatively small size, that is, a small capacity, is used as described in the explanation of FIG. 4 above.
The response was poor because the spool 26 was moved, which required a flow rate of 4.9cc.
本発明はこのような欠点を除去したものでその
目的は、油圧式に対しては応答性がよいと共に操
作力の軽いこと電気一油圧式に対しては応答性の
よい遠隔制御装置を提供することにある。
The present invention eliminates these drawbacks, and its purpose is to provide a remote control device that has good responsiveness and light operating force for hydraulic type systems, and has good responsiveness for electric-hydraulic type systems. There is a particular thing.
本発明の遠隔制御装置は下記の構成からなるこ
とを特徴にしている。
The remote control device of the present invention is characterized by having the following configuration.
A:主制御対象であるアクチエータ
B:前記アクチエータへの圧油の給排を主スプー
ルの移動により制御する制御弁
C:制御弁に圧油を供給する主ポンプ
D:主スプールの両端外方に形成されたパイロツ
ト油圧と、主スプールの両端に固着或いはこれ
と一体的に設けられその両端近くにあけた2個
の軸直角方向の穴を軸方向の穴により連通した
コントロールスプールと、コントロールスプー
ルの外周に挿入されその両端近くにあけた2個
の軸直角方向の穴により内外周を連通したコン
トロールスリーブとと、その一側端面にパイロ
ツト圧油を受けることによりコントロールスリ
ーブを移動させるパイロツトピストンとからな
り、制御弁の非動作時はパイロツト油圧をタン
クに連通し制御弁の動作時は前記パイロツトピ
ストンを介してコントロールスリーブの移動し
たことによりパイロツト油室とタンクとの連通
を絞る一対の油圧サーボ機構
E:パイロツトポンプと油圧サーボ機構の中間に
設けられ、3個のランドおよびこのなかの2個
のランドの中間の凹部にあけた軸直角方向の穴
ならびにこの穴をその一側端面に開口する軸方
向の穴を有すると共に他側端面にパイロツト圧
油を受けるセレクタスプールと、セレクタスプ
ールを挿入した穴から前記パイロツト油室に向
けた連通穴と、穴をタンクに接続する管路と、
穴をパイロツトポンプに接続する接続穴とから
なり、制御弁の非動作時は前記パイロツト油室
をタンクに連通し制御弁の動作時はパイロツト
油室にパイロツトポンプのパイロツト圧油を供
給する一対のセレクタ。A: Actuator that is the main control target B: Control valve that controls supply and discharge of pressure oil to the actuator by movement of the main spool C: Main pump that supplies pressure oil to the control valve D: Externally located at both ends of the main spool The formed pilot hydraulic pressure is connected to the control spool, which is fixed to or integrated with both ends of the main spool and communicates with the two axially perpendicular holes drilled near both ends through the axial holes. A control sleeve that is inserted into the outer circumference and communicates between the inner and outer circumferences through two holes perpendicular to the axis drilled near both ends of the control sleeve, and a pilot piston that moves the control sleeve by receiving pilot pressure oil on one end surface of the control sleeve. A pair of hydraulic servo mechanisms communicate pilot oil pressure to the tank when the control valve is not operating, and restrict communication between the pilot oil chamber and the tank by moving the control sleeve via the pilot piston when the control valve is operating. E: A shaft that is provided between the pilot pump and the hydraulic servo mechanism and has three lands, a hole perpendicular to the axis made in the recess between two of these lands, and a shaft that opens this hole on one end surface of the hole. a selector spool having a hole in the direction and receiving pilot pressure oil on the other end face, a communication hole from the hole into which the selector spool is inserted to the pilot oil chamber, and a pipe connecting the hole to the tank;
It consists of a connection hole that connects the hole to the pilot pump, and a pair of connecting holes that communicate the pilot oil chamber with the tank when the control valve is not operating, and supply pilot pressure oil of the pilot pump to the pilot oil chamber when the control valve is operating. selector.
以下本発明について油圧式の一実施例を示した
第1図および第2図により説明する。なお従来例
である第3図と同等部材は同一符号を付して詳し
い説明を省略し異なる部分についてのみ説明す
る。
The present invention will be explained below with reference to FIGS. 1 and 2 showing an embodiment of a hydraulic type. Note that the same members as those in FIG. 3, which is a conventional example, are given the same reference numerals, detailed explanations are omitted, and only different parts will be explained.
第1図において51は主制御対象であるアクチ
エータ11への圧油の給排を制御する制御弁であ
つて、主スプール52(第2図参照)の両端部形
状のみが従来例のスプール26と異なるもので他
は同一である。53は油圧サーボ機構であつてパ
イロツトポンプ21の圧油をパイロツト減圧弁2
3からセレクタ54と絞り105を介して受けた
とき制御弁51を切換えるようになつている。 In FIG. 1, 51 is a control valve that controls the supply and discharge of pressure oil to the actuator 11, which is the main control target, and only the shape of both ends of the main spool 52 (see FIG. 2) is different from the conventional spool 26. They are different but otherwise the same. 53 is a hydraulic servo mechanism which supplies pressure oil from the pilot pump 21 to the pilot pressure reducing valve 2.
3 through the selector 54 and throttle 105, the control valve 51 is switched.
次に油圧サーボ機構53とセレクタ54の細部
を第2図により説明する。制御弁51の弁箱体6
1の左右両端面にはサーボケース62が不図示の
ボルトにより固着されている。(図は右側のみを
示しておりかつ制御弁51の中立状態を示してい
る。)油圧サーボ機構53については、主スプー
ル52右端の肩に挿入されたカラー63とサーボ
ケース62の肩に装着されたリテーナ64との間
に、主スプール52を中立状態に複帰させるため
のバネ65が設けてある。主スプール52の端面
にはこれと一体或いは螺着等により固着されたコ
ントロールスプール66がある。 Next, details of the hydraulic servo mechanism 53 and selector 54 will be explained with reference to FIG. Valve body 6 of control valve 51
A servo case 62 is fixed to both left and right end surfaces of 1 by bolts (not shown). (The figure shows only the right side and shows the neutral state of the control valve 51.) Regarding the hydraulic servo mechanism 53, a collar 63 inserted into the shoulder of the right end of the main spool 52 and a shoulder of the servo case 62 are attached to the hydraulic servo mechanism 53. A spring 65 is provided between the main spool 52 and the retainer 64 to return the main spool 52 to a neutral state. A control spool 66 is provided on the end surface of the main spool 52, either integrally with the main spool 52 or fixed thereto by screwing or the like.
コントロールスプール66はリテーナ64の中
心穴を摺動自在に通つてコントロールスリーブ6
7の中心穴68へ摺動自在に挿入され、かつ主ス
プール52の端面近くとコントロールスリーブ6
7内において軸直角方向の穴69および70があ
けられ、両穴69および70は軸方向の穴71に
より連通されている。コントロールスリーブ67
の中心の穴68は左右両端近くの軸直角方向の穴
72および73Aにより外周に連通している。 The control spool 66 is slidably passed through the center hole of the retainer 64 and the control sleeve 66 is inserted into the control sleeve 6.
7 is slidably inserted into the center hole 68 of the control sleeve 6 near the end surface of the main spool 52 and the control sleeve 6.
Holes 69 and 70 in the direction perpendicular to the axis are bored in the inside of the hole 7, and both the holes 69 and 70 are communicated with each other by a hole 71 in the axial direction. control sleeve 67
The center hole 68 communicates with the outer periphery through holes 72 and 73A in the direction perpendicular to the axis near both left and right ends.
コントロールスリーブ67とリテーナ64との
間には前述のバネ65にり弱いバネ73があり、
またコントロールスリーブ67の右端はバネ73
に押されてサーボケース62の壁面に接すると共
にサーボケース62の中心に挿入されたパイロツ
トピストン74の一側に接している。パイロツト
ピストン74の他側はパイロツト減圧弁23の一
側に接続されたサーボケース62の接続口75に
結ばれた管路76に面している。またコントロー
ルスリーブ67の外周は管路77によりタンク1
2に連通している。なお主スプール52の右端と
リテーナ64との対向面空間をパイロツト油室7
8という。 Between the control sleeve 67 and the retainer 64 is a spring 73 which is weaker than the spring 65 described above.
Also, the right end of the control sleeve 67 is connected to the spring 73.
The pilot piston 74 is pushed into contact with the wall surface of the servo case 62, and is also in contact with one side of a pilot piston 74 inserted into the center of the servo case 62. The other side of the pilot piston 74 faces a conduit 76 connected to a connection port 75 of the servo case 62 connected to one side of the pilot pressure reducing valve 23. In addition, the outer circumference of the control sleeve 67 is connected to the tank 1 by a conduit 77.
It is connected to 2. Note that the space facing the right end of the main spool 52 and the retainer 64 is the pilot oil chamber 7.
It's called 8.
セレクタ54は、サーボケース62の制御弁5
1側からあけた穴91の端部に置かれた栓92と
穴91へ摺動自在に挿入されたセレクタスプール
93、そして栓92とセレクタスプール93との
間に設けた比較的弱いスプリング94とを主な構
成要素にしている。セレクタスプール93は3個
のランド95ないし97を有しランド95と96
との間にある凹部98にあけた軸直角方向の穴9
9は軸方向の穴100によりその左端に開口して
いる。図の状態のとき凹部98はパイロツト油室
78に一側を開口したサーボケース62の連通穴
101の他側に接し、ランド95の左方は管路7
7に接続した管路102によりタンク12に連通
している。セレクタスプール93の右端は管路7
6に接しておりランド96と97との間の凹部1
03面する部分に設けた接続穴104はパイロツ
トポンプ21に固定絞り105を介して接続して
いる。 The selector 54 is connected to the control valve 5 of the servo case 62.
A plug 92 placed at the end of a hole 91 drilled from the first side, a selector spool 93 slidably inserted into the hole 91, and a relatively weak spring 94 provided between the plug 92 and selector spool 93. is the main component. The selector spool 93 has three lands 95 to 97, and lands 95 and 96.
A hole 9 in the direction perpendicular to the axis in a recess 98 between the
9 is opened at its left end by an axial hole 100. In the state shown in the figure, the recess 98 is in contact with the other side of the communication hole 101 of the servo case 62, which has one side open to the pilot oil chamber 78, and the left side of the land 95 is in contact with the other side of the communication hole 101 of the servo case 62.
It communicates with the tank 12 by a conduit 102 connected to the tank 7. The right end of the selector spool 93 is the pipe 7
Recess 1 between lands 96 and 97 and in contact with 6
A connection hole 104 provided in the portion facing 03 is connected to the pilot pump 21 via a fixed throttle 105.
なおパイロツトピストン74とセレクタスプー
ル93は通常直径がほぼ0.6cmであり、管路76
にパイロツトポンプ21のパイロツト圧油を受け
たときのストロークはパイロツトピストンが1cm
セレクタスプール93が0.6cm程度である。 Note that the pilot piston 74 and selector spool 93 usually have a diameter of approximately 0.6 cm, and the pipe line 76
When the pilot pump 21 receives pilot pressure oil, the stroke of the pilot piston is 1 cm.
The selector spool 93 is approximately 0.6 cm.
続いて前述した実施例の動作を説明する。第2
図は前記したように制御弁51の中立状態を示し
ておりこの状態のとき、パイロツト油室78は一
側通路である穴69ないし72から管路77を介
してタンク12に連通し、また他側通路である穴
101から穴99および100と管路102およ
び77を介してタンク12に連通しているため、
パイロツト油室78は無圧であつて主スプール5
2は左右のバネ65により中立位置にある。ここ
でパイロツト減圧弁23を右側に倒すとパイロツ
トポンプ21のパイロツト圧油は第2図に示す右
側のサーボケース62の接続口75から管路76
に作用する。これを受けてセレクタスプール93
は左行しパイロツトポンプ21のパイロツト圧油
は固定絞り105から凹部103と穴101を通
つてパイロツト油室78に流入、また穴101と
管路102の連通は断即ちパイロツト油室78の
タンク12に至る他側の通路は断になる。 Next, the operation of the above-described embodiment will be explained. Second
The figure shows the neutral state of the control valve 51 as described above, and in this state, the pilot oil chamber 78 communicates with the tank 12 from the holes 69 to 72, which are passages on one side, through the pipe 77, and on the other side. Since hole 101, which is a side passage, communicates with tank 12 via holes 99 and 100 and pipes 102 and 77,
The pilot oil chamber 78 is unpressurized and the main spool 5
2 is in a neutral position by left and right springs 65. When the pilot pressure reducing valve 23 is tilted to the right side, the pilot pressure oil of the pilot pump 21 flows from the connection port 75 of the servo case 62 on the right side to the pipe line 76 as shown in FIG.
It acts on In response to this, selector spool 93
moves to the left, and the pilot pressure oil of the pilot pump 21 flows from the fixed throttle 105 through the recess 103 and the hole 101 into the pilot oil chamber 78, and the communication between the hole 101 and the pipe 102 is cut off, that is, the tank 12 of the pilot oil chamber 78 The passage on the other side that leads to is cut off.
セレクタスプール93の左行と同時にコントロ
ールスリーブ67もパイロツトピストン74に押
されて左行しパイロツト油室78のタンク12に
至る一側通路も穴70と72とが絞られる。この
結果パイロツト油室78の圧力は高くなり主スプ
ール52は左行し左行に伴いバネ65に相当する
左側のサーボケース内のバネの力を受ける。 At the same time as the selector spool 93 moves to the left, the control sleeve 67 is also pushed by the pilot piston 74 and moves to the left, and the holes 70 and 72 of the pilot oil chamber 78 leading to the tank 12 are also narrowed. As a result, the pressure in the pilot oil chamber 78 increases, and the main spool 52 moves to the left, receiving the force of a spring in the left servo case corresponding to the spring 65 as the main spool 52 moves to the left.
ここでパイロツト油室78の圧力は穴70と7
2の絞り状態により定まり主スプール52パイロ
ツト油室78の圧力と上記した左側のバネ力とが
バランスする位置に停止する。そしてこの位置は
パイロツト減圧弁23のレバーの倒す位置により
定まる。なお主スプール52の左行時左側のパイ
ロツト油室は左側のセレクタが不作動であるため
タンク12に連通していることにより支障なく左
行する。そして主スプール52の左行にともない
アクチエータ11のロツド側に主スプール52の
置により定まる主ポンプ14の圧油が流入する。 Here, the pressure in the pilot oil chamber 78 is
2, the main spool 52 stops at a position where the pressure in the pilot oil chamber 78 and the above-mentioned left spring force are balanced. This position is determined by the tilted position of the lever of the pilot pressure reducing valve 23. When the main spool 52 moves to the left, the pilot oil chamber on the left side is in communication with the tank 12 because the selector on the left side is inactive, so that the main spool 52 moves to the left without any problem. As the main spool 52 moves to the left, pressure oil from the main pump 14, which is determined by the position of the main spool 52, flows into the rod side of the actuator 11.
なお第1図の一点鎖線で囲んだパイロツト減圧
弁23を第5図に示したコントローラ36、電磁
比例減圧弁37、バツテリー38としてソレノイ
ド39等と置き換えれば、本発明が電気一油式圧
に適用可能であることは理解されよう。 If the pilot pressure reducing valve 23 surrounded by the dashed line in FIG. 1 is replaced with the controller 36, electromagnetic proportional pressure reducing valve 37, and solenoid 39 as the battery 38 shown in FIG. It is understood that this is possible.
本発明の遠隔制御装置は以上説明したように、
従来例に対し小形のコントロールスプール、コン
トロールスリーブ、リテーナ、セレクタスプール
そして3個のバネを追加したのみであるためコス
ト上昇は僅かである。一方制御弁の主スプール切
換に要する減圧弁のパイロツト圧油の流量は、パ
イロツトピストンに対し0.28c.c.そしてセレクタス
プールに対し0.17c.c.の計0.45c.c.であつて従来の4.9
c.c.に対し10%以下になつた。このため油圧式にお
いては応答性のよいことと操作力の軽くなつたこ
と、そして電気一油圧式においは応答性のよい利
点を有する。
As explained above, the remote control device of the present invention has the following features:
Compared to the conventional example, only a small control spool, a control sleeve, a retainer, a selector spool, and three springs are added, so the cost increase is small. On the other hand, the flow rate of the pilot pressure oil of the pressure reducing valve required for switching the main spool of the control valve is 0.28 cc for the pilot piston and 0.17 cc for the selector spool, a total of 0.45 cc, compared to the conventional 4.9 cc.
It became less than 10% of cc. For this reason, the hydraulic type has the advantage of good responsiveness and light operating force, and the electric-hydraulic type has the advantage of good responsiveness.
第1図および第2図は本発明の一実施例を示し
第1図は係統図、第2図は本発明の要部の拡大断
面図、第3図は従来例の係統図、第4図は従来例
の一部断面図、第5図は本発明の他の実施例なら
びに従来の他の例における一部を示した係統図で
ある。
11……アクチエータ、14……主ポンプ、2
1……パイロツトポンプ、23……パイロツト減
圧弁、37……電磁比例減圧弁、51……制御
弁、52……主スプール、53……油圧サーボ機
構、54……セレクタ、66……コントロールス
プール、67……コントロールスリーブ、74…
…パイロツトピストン、78……パイロツト油
室、93……セレクタスプール。
Figures 1 and 2 show one embodiment of the present invention, Figure 1 is a system diagram, Figure 2 is an enlarged sectional view of the main part of the present invention, Figure 3 is a system diagram of a conventional example, and Figure 4. 5 is a partial sectional view of a conventional example, and FIG. 5 is a related diagram showing another embodiment of the present invention and a part of another conventional example. 11... Actuator, 14... Main pump, 2
1...Pilot pump, 23...Pilot pressure reducing valve, 37...Solenoid proportional pressure reducing valve, 51...Control valve, 52...Main spool, 53...Hydraulic servo mechanism, 54...Selector, 66...Control spool , 67...control sleeve, 74...
...Pilot piston, 78...Pilot oil chamber, 93...Selector spool.
Claims (1)
ルの移動により制御する制御弁 C:前記制御弁に圧油を供給する主ポンプ D:前記主スプールの両端外方に形成されたパイ
ロツト油圧と、前記主スプールの両端に固着或
いはこれと一体的に設けられその両端近くにあ
けた2個の軸直角方向の穴を軸方向の穴により
連通したコントロールスプールと、同コントロ
ールスプールの外周に挿入されその両端近くに
あけた2個の軸直角方向の穴により内外周を連
通したコントロールスリーブと、その一側端面
にパイロツト圧油を受けることにより前記コン
トロールスリーブを移動させるパイロツトピス
トンとからなり、前記制御弁の非動作時は前記
パイロツト油室をタンクに連通し前記制御弁の
動作時は前記パイロツトピストンを介して前記
コントロールスリーブの移動させたことにより
前記パイロツト油室と前記タンクとの連通を絞
る一対の油圧サーボ機構 E:パイロツトポンプと前記油圧サーボ機構の中
間に設けられ、3個のランドおよびこのなかの
2個のランドの中間の凹部にあけた軸直角方向
の穴ならびにこの穴をその一側端面に開口する
軸方向の穴を有すると共に他側端面にパイロツ
ト圧油を受けるセレクタスプールと、同セレク
タスプールを挿入した穴から前記パイロツト油
室に向けた連通穴と、前記穴をタンクに接続す
る管路と、前記穴をパイロツトポンプに接続す
る接続穴とからなり、前記制御弁の非動作時は
前記パイロツト油室を前記タンクに連通し前記
制御弁の動作時は前記パイロツト油室に前記パ
イロツトポンプのパイロツト圧油を供給する一
対のセレクタ。[Claims] 1. A remote control device having the following configuration. A: Actuator that is the main control target B: Control valve that controls supply and discharge of pressure oil to the actuator by movement of the main spool C: Main pump that supplies pressure oil to the control valve D: Outside both ends of the main spool a control spool that is fixed to or integrated with both ends of the main spool and communicates with two axially perpendicular holes drilled near both ends through an axial hole; A control sleeve is inserted into the outer circumference of the control spool, and the inner and outer circumferences are communicated through two holes drilled near both ends of the control sleeve in a direction perpendicular to the axis, and the control sleeve is moved by receiving pilot pressure oil on one end surface of the control sleeve. When the control valve is not in operation, the pilot oil chamber is communicated with the tank, and when the control valve is in operation, the control sleeve is moved via the pilot piston, thereby connecting the pilot oil chamber with the tank. A pair of hydraulic servo mechanisms E that restrict communication with the tank: A pair of hydraulic servo mechanisms E are provided between the pilot pump and the hydraulic servo mechanism, and are provided with three lands and a recess in the middle of two of these lands, extending in the direction perpendicular to the axis. a selector spool having a hole and an axial hole opening on one end face of the selector spool and receiving pilot pressure oil on the other end face; and a communication hole extending from the hole into which the selector spool is inserted to the pilot oil chamber. , a pipe line connecting the hole to a tank, and a connection hole connecting the hole to a pilot pump, and when the control valve is not operating, the pilot oil chamber is connected to the tank, and when the control valve is operating, the pilot oil chamber is connected to the tank. a pair of selectors for supplying pilot pressure oil of the pilot pump to the pilot oil chamber;
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP20764984A JPS6187039A (en) | 1984-10-03 | 1984-10-03 | Remote controller |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP20764984A JPS6187039A (en) | 1984-10-03 | 1984-10-03 | Remote controller |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6187039A JPS6187039A (en) | 1986-05-02 |
JPH0421016B2 true JPH0421016B2 (en) | 1992-04-08 |
Family
ID=16543270
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP20764984A Granted JPS6187039A (en) | 1984-10-03 | 1984-10-03 | Remote controller |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6187039A (en) |
-
1984
- 1984-10-03 JP JP20764984A patent/JPS6187039A/en active Granted
Also Published As
Publication number | Publication date |
---|---|
JPS6187039A (en) | 1986-05-02 |
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Legal Events
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---|---|---|---|
EXPY | Cancellation because of completion of term |