JPS62151601A - Single rod cylinder driving circuit - Google Patents
Single rod cylinder driving circuitInfo
- Publication number
- JPS62151601A JPS62151601A JP29200985A JP29200985A JPS62151601A JP S62151601 A JPS62151601 A JP S62151601A JP 29200985 A JP29200985 A JP 29200985A JP 29200985 A JP29200985 A JP 29200985A JP S62151601 A JPS62151601 A JP S62151601A
- Authority
- JP
- Japan
- Prior art keywords
- rod cylinder
- single rod
- signal
- hydraulic pump
- pump
- 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.)
- Pending
Links
Classifications
-
- 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
- F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
〈産業上の利用分野〉
本発明は油圧機械等の液圧を活用する機械に備えられる
片ロツドシリンダ駆動回路に関する。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a single rod cylinder drive circuit provided in a machine that utilizes hydraulic pressure, such as a hydraulic machine.
〈従来の技術〉
第６図は従来の片ロツドシリンダ駆動回路を例示する回
路図である。この図において、１は片ロツドシリンダ、
２はこの片ロツドシリンダ１に圧油を供給する油圧ポン
プ、３は片ロツドシリンダｌと油圧ポンプ２との間に介
設され、片ロツドシリンダ１に供給される圧油の方向を
切換える方向切換弁、４は油圧ポンプ２の吐出油あるい
は片ロツドシリンダ１の戻り油が導かれるタンクである
。<Prior Art> FIG. 6 is a circuit diagram illustrating a conventional single rod cylinder drive circuit. In this figure, 1 is a single rod cylinder,
2 is a hydraulic pump that supplies pressure oil to the single rod cylinder 1; 3 is a directional switching valve that is interposed between the single rod cylinder 1 and the hydraulic pump 2 and switches the direction of the pressure oil supplied to the single rod cylinder 1; 4; is a tank to which the discharge oil of the hydraulic pump 2 or the return oil of the single-rod cylinder 1 is led.
この従来例にあっては、油圧ポンプ２の吐出し圧力の最
大値、すなわち図示しないＩＪ ＩＪ−フ弁の設定圧力
をｐ、Ｓａ大吐出し流量をＱｌとすればその相関関係は
第７図のＰ、ＲＱ、となる。しだがって、Ｒを通る等馬
力曲線Ｅで示される駆動馬力が必要となる。ここで、説
明を簡単にするため各効率は１００％としである。In this conventional example, if the maximum value of the discharge pressure of the hydraulic pump 2, that is, the set pressure of the IJ valve (not shown) is p, and the Sa large discharge flow rate is Ql, the correlation between them is shown in FIG. P, RQ, and so on. Therefore, the drive horsepower shown by the equal horsepower curve E passing through R is required. Here, to simplify the explanation, each efficiency is assumed to be 100%.
なお、油圧ポンプ２を可変容欲油圧ポンプに設定した場
合、最大吐出し流量Ｑ１は同じにして、高圧例えば第７
図のＰｏになれば吐出し流１葎を下げ、等馬力線Ｅの範
囲内で作動させるようになっている。Note that when the hydraulic pump 2 is set as a variable-volume hydraulic pump, the maximum discharge flow rate Q1 is the same and the high pressure, for example, the seventh
When Po in the figure is reached, the discharge flow is lowered by 1 liter to operate within the range of the equal horsepower line E.
く発明が解決しようとする問題点〉
このように構成しである従来例にちっては、例えば片ロ
ツドシリンダｌを矢印５方向に押出す場合、最大吐出し
流−ｈｔ Ｑｌを片ロツドシリンダ１のヘッド側＋ｆｆ
＋面積Ｓ、で除した速度が当該片ロツドシリンダｌの押
出し最大速度であり、この片ロツドシリンダ１を介して
おこなわれる作業は、片ロツド／リンダ１にかかる負荷
の大小にかかわらずこの押出し最大速度によって制約を
受ける。なお、それ以上の速度を得るためにはより大容
量のポンプを設けるか、または多数のポンプを設けるこ
とが必要になる。Problems to be Solved by the Invention In the conventional example configured as described above, for example, when pushing out the single-rod cylinder 1 in the direction of arrow 5, the maximum discharge flow -htQl is determined by the head of the single-rod cylinder 1. side + ff
+ area S, is the maximum extrusion speed of the single rod cylinder 1, and the work performed via this single rod cylinder 1 is carried out at this maximum extrusion speed regardless of the magnitude of the load applied to the single rod/cylinder 1. subject to restrictions. Note that in order to obtain higher speeds, it is necessary to provide a pump with a larger capacity or a larger number of pumps.
本発明は、このような従来技術における実情に鑑みてな
されたもので、その目的は、片ロッドシリンダにかかる
負荷が小さい場合に、ポンプ容量の大型化等を要するこ
となく、轟核片ロッドシリンダの速度を速くすることの
できる片ロッドシリンダ駆動回路を提供することにある
。The present invention has been made in view of the actual situation in the prior art, and its purpose is to provide a single rod cylinder with a rotary core without requiring an increase in pump capacity when the load applied to the single rod cylinder is small. The object of the present invention is to provide a single rod cylinder drive circuit that can increase the speed of the cylinder.
〈問題点を解決するだめの手段〉
この目的を達成するために本発明は、片ロツドシリンダ
のヘッド側およびロッド側に、ポンプに連絡されるもの
およびタンクに連絡されるものを含む少なくとも２つの
切換弁をそれぞれ設けるとともに、切換弁を所定の組合
せに切換えるＶＪ換倍信号発生装置設けた構成にしであ
る。<Means for Solving the Problem> To achieve this object, the present invention provides at least two switches on the head side and rod side of the single rod cylinder, including one connected to the pump and one connected to the tank. In addition to providing respective valves, a VJ switching signal generator for switching the switching valves to a predetermined combination is also provided.
く作用〉
本発明は、このように構成しであることから、片ロツド
シリンダにかかる負荷が小さい場合、すなわちポンプの
吐出圧が小さい場合には、切換信号発生装置ｕから出力
される信号によって切換弁が所定の組合せになるように
切換えられ、これによって片ロツドシリンダが多段速に
なり、ポンプ容量の大型化等を要することなく増速を実
現できる。Since the present invention is configured as described above, when the load applied to the single rod cylinder is small, that is, when the discharge pressure of the pump is small, the switching valve is activated by the signal output from the switching signal generator u. are switched to a predetermined combination, thereby making the single rod cylinder multi-speed, and increasing the speed without increasing the pump capacity.
〈実施例〉
以下、本発明の片ロツドシリンダ駆動装置を図に基づい
て説明する。<Embodiment> Hereinafter, a single rod cylinder drive device of the present invention will be explained based on the drawings.
第１図は本発明の一実施クリの概略構成を示す回路図で
ある。FIG. 1 is a circuit diagram showing a schematic configuration of one embodiment of the present invention.
この図においてＪＩＩｏ、１１は片ロッドシリンダ、１
２はこれらの片ロツドシリンダｔｏ、１１によって駆動
される負荷体で、この負荷体１２と片ロツドシリンダ１
０，１１のロッドとは例えば十分に剛性の高いピン結合
にしである。また、片ロツドシリンダ１０．１１の形状
寸法は全く同等であり、これらのヘッド側断面積とロッ
ド側断面積とは、例えば２：１に設定しである。１３は
片ロッドシリンダ１０．１１への圧油の供給が可能な油
圧ポンプ、１４は油圧ポンプ１３の吐出油または片ロツ
ドシリンダ１０．１１の戻り油が導かれるタンク、】５
は油圧ポンプ１３とタンク１４との間に介設した２位匁
２方形の電磁切換弁である。In this figure, JIIo, 11 is a single rod cylinder, 1
2 is a load body driven by these single-rod cylinders to, 11;
The rods numbered 0 and 11 are, for example, pin connections with sufficient rigidity. Further, the shapes and dimensions of the single-rod cylinders 10 and 11 are exactly the same, and the cross-sectional area on the head side and the cross-sectional area on the rod side are set, for example, at a ratio of 2:1. 13 is a hydraulic pump capable of supplying pressure oil to the single-rod cylinder 10.11; 14 is a tank to which discharge oil from the hydraulic pump 13 or return oil from the single-rod cylinder 10.11 is led; ]5
is a two-position, bidirectional electromagnetic switching valve interposed between the hydraulic pump 13 and the tank 14.
１６は油圧ポンプ１３と片ロッドシリンダ１０のヘッド
側とを連絡する管路に介設した２立ｆｉｔ ２方形の電
磁切換弁、１７は油圧ポンプ１３と片ロッド７１） ／
ダニ０のロッド側とを連絡する管路に介設した２泣置２
方形のａ磁切換弁、１８は油圧ポンプ】３と片ロツドシ
リンダ１１のヘッド（ＩｌｌとをＰ異格する管路に介設
した２泣置２方形のＩｉ工磁切換斤、１９は油圧ポンプ
１３と片ロッドシリンダ１１０ロツド１則とを連絡する
・α路に介設した２位ｚ２方形の電磁切換弁でちる。２
０はタック１４と片ロッドシリンダ１０のヘッド側とを
連絡する管路に介設した２泣置２方形の電磁切換弁、２
１はタンク１４と片ロツドシリンダ１０のロッド１＋１
ｊｌとを連絡する管路に介設した２泣置２方形の電磁切
換弁、２２はタンク１４と片ロツドシリンダ１１のヘッ
ド側とを連絡する管路に介設した２泣置２方形の電磁切
換弁、２３はタンク１４と片ロツドシリンダ１１のロッ
ド（Ｉｌｌとを連絡する管路に介設した２泣置２方形の
電磁切換弁である。２４は油圧ポンプ１３の吐出圧を検
出する圧力センサ、２５は圧力センサ２４からの信号に
応じて速度比を求める論理判断をおこなう制御装置で、
この制御装置ｄ２５には、例えば第２図に示すように、
油圧ポンプ１３の吐出圧力Ｐと片ロッドシリンダ１０゜
１１の速度比Ｖの関係があらかじめ設定されている。２
６は制御装置２５から出力された速度比に相応する信号
に応じて電磁切換弁１６〜２３のうちの該当するものを
切換える切換信号を発生する切換信号発生装置で、電磁
切換弁１６〜２３の駆動部はこの切換（ｇ号発生装置２
６に接続されている。２７は例えば第２図の速度比Ｖ１
． Ｖｔ 、 Ｖｊ、 Ｖ−に相応する切戻位置を有す
る手動操作スイッチからなる指令装置で、’＋１ＪＩＪ
＋卸装置ぴ２５に接続されている。この指令装置２７
から信号が出力されたときには、圧力センサ２４からの
信号によることなく優先的に指令装置Ｐｔ２７の信号に
相応する速度比を制御装置２５は切換信号発生装置２６
に出力する。Reference numeral 16 indicates a 2-vertical fit two-sided electromagnetic switching valve interposed in a pipe connecting the hydraulic pump 13 and the head side of the single-rod cylinder 10, and 17 indicates a hydraulic pump 13 and the single-rod cylinder 71).
2 holder 2 interposed in the conduit connecting the rod side of tick 0
A rectangular A magnetic switching valve, 18 is a hydraulic pump] 3 and a single rod cylinder 11 head (Ill) are interposed in a pipe line different from P, 2 square Ii magnetic switching valves, 19 are hydraulic pumps 13 Connect the single rod cylinder 110 rod 1 rule with the 2nd position z2 square electromagnetic switching valve installed in the α path.2.
0 is a two-way two-way electromagnetic switching valve installed in a pipe connecting the tack 14 and the head side of the single-rod cylinder 10;
1 is the tank 14 and the rod 1+1 of the single rod cylinder 10
22 is a 2-position, 2-square electromagnetic switching valve installed in a pipeline that communicates between the tank 14 and the head side of the single-rod cylinder 11. The valve 23 is a two-way, two-way electromagnetic switching valve installed in a pipe connecting the tank 14 and the rod (Ill) of the single-rod cylinder 11.24 is a pressure sensor that detects the discharge pressure of the hydraulic pump 13; 25 is a control device that makes a logical judgment to determine the speed ratio according to the signal from the pressure sensor 24;
This control device d25 includes, for example, as shown in FIG.
The relationship between the discharge pressure P of the hydraulic pump 13 and the speed ratio V of the single rod cylinder 10°11 is set in advance. 2
Reference numeral 6 denotes a switching signal generator that generates a switching signal for switching a corresponding one of the electromagnetic switching valves 16 to 23 in accordance with a signal corresponding to the speed ratio output from the control device 25; The drive unit uses this switching (G generator 2
6. 27 is the speed ratio V1 in Fig. 2, for example.
．． A command device consisting of a manually operated switch having reversal positions corresponding to Vt, Vj, V-, and '+1JIJ
+Connected to wholesaler device pi 25. This command device 27
When a signal is output from the switching signal generating device 26, the control device 25 preferentially changes the speed ratio corresponding to the signal from the command device Pt27 without depending on the signal from the pressure sensor 24.
Output to.
なお、上述した電磁切換弁１５の駆動部は制御装置２５
に接続されている。Note that the drive section of the electromagnetic switching valve 15 described above is controlled by the control device 25.
It is connected to the.
このように構成しである実施例にあって、片ロッドシリ
ンダ１０．１１を矢印２８方向に伸長させる動作につい
て説明する。指令装置２７から信号が出力されておらず
、通常の場合、すなわち前述の第６図に示す動作と同等
の作動をおこなう場合には、圧力センサ２４によって検
出される圧力はに２図のＰｌであり、制御装置２５はｉ
２図の関係から圧力Ｐ１に相応する速度比看を選択する
。なお、片ロツドシリンダ１０．１１のうちの１つの°
シリンダを単位長さだけ押出したときのヘッド側の容
積を１００とすると、このとき油圧ポンプ１３から吐出
される流量は１００＋１００＝２００はど必要となる。In the embodiment configured as described above, the operation of extending the single rod cylinder 10.11 in the direction of arrow 28 will be described. In a normal case where no signal is output from the command device 27, that is, when performing an operation equivalent to the operation shown in FIG. Yes, the control device 25
The speed ratio corresponding to the pressure P1 is selected from the relationship shown in FIG. In addition, the angle of one of the single rod cylinders 10 and 11 is
Assuming that the volume on the head side when the cylinder is pushed out by a unit length is 100, the flow rate discharged from the hydraulic pump 13 at this time is 100+100=200.
この場合の片ロツドシリンダ１０゜１１の押出し速度の
速度比を１とすると、Ｖ、＝１となる。そして、制御装
置２５は電磁切換弁１５を？Ｐ１図に示すアンロード状
聾から閉止位置に切換える信号を出力するとともに、切
換信号発生装置２６に速度比Ｖ、に相応する信号を出力
するっなお、以下において１片ロツドシリンダ１０．１
１を作動させるときは常に制御装置２５から電磁切換弁
１５に信号が出力され、この電磁切換弁１５が閉止位置
に切換えられる。そして、上記したように信号を受けた
切換信号発生装置２６は、第３図のＮｎ１の欄に「０」
印で示した各切換動作をおこなう信号を、電磁切換弁１
６，１８，２１．２３に出力する、これによって電磁切
換弁１６．１８゜２１．２３が開位置に切換えられ、片
ロッドシリンダ１０．１１のヘッド側が油圧ポンプ１３
に連通し、片ロッドシリンダ１０．１１のロッド側がタ
ンク１４に連通し、油圧ポンプ１３の圧油が電磁切換弁
１６．１８を経て片ロッドシリンダ１０゜１１０ヘツド
側に導かれ、一方、片ロッドシリンダ１０，１１のロッ
ド側の圧油が電磁切換弁２１゜２３を経てタンク１４に
導かれ、片ロツドシリンダ１０．１１は速度比ｖ１−１
で作動する。In this case, if the speed ratio of the extrusion speed of the single rod cylinder 10° 11 is 1, then V=1. Then, the control device 25 controls the electromagnetic switching valve 15? It outputs a signal for switching from the unloaded deaf to the closed position shown in Figure P1, and also outputs a signal corresponding to the speed ratio V to the switching signal generator 26.In the following, the one-piece rod cylinder 10.1
1, a signal is always output from the control device 25 to the electromagnetic switching valve 15, and the electromagnetic switching valve 15 is switched to the closed position. Then, the switching signal generator 26 that receives the signal as described above enters "0" in the Nn1 column of FIG.
The signals to perform each switching operation indicated by the marks are sent to the solenoid switching valve 1.
6, 18, 21.23. This switches the electromagnetic switching valve 16.18° 21.23 to the open position, and the head side of the single rod cylinder 10.11 is connected to the hydraulic pump 13.
The rod side of the single rod cylinder 10.11 is connected to the tank 14, and the pressure oil of the hydraulic pump 13 is guided to the single rod cylinder 10°110 head side via the electromagnetic switching valve 16.18. The pressure oil on the rod side of the cylinders 10 and 11 is led to the tank 14 through the electromagnetic switching valves 21 and 23, and the single rod cylinder 10 and 11 have a speed ratio of v1-1.
It operates with.
また、圧力センサ２４で前述したＰｌよりも小さい第２
図に示すＰ、が検出されると、制御装置２５において、
第２図に示す関係から前述した速度比ｖ１よりも大きい
速度比Ｖ、が選択され、この速度比Ｖ？に相応する信号
が切換信号発生装置２６に出力される。切換信号発生装
置２６はこの信号を受けて第３図の陽２の欄に「０」印
で示した各切換動作をおこなう信号を電磁切換弁１６．
１８，１９゜２１に出力する。これによって電磁切換弁
１６゜１８．１９．２１が開位置に切換えられ、片ロツ
ドシリンダ１０のヘッド側が油圧ポンプ１３に連通し、
片コンドシリンダ１００ロツド側がタンク１４に連通し
、片ロツドシリンダ１１のヘッド側とロッド側の双方が
油圧ポンプ１３に連通ずる。In addition, in the pressure sensor 24, a second
When P shown in the figure is detected, in the control device 25,
From the relationship shown in FIG. 2, a speed ratio V, which is larger than the speed ratio v1 described above, is selected, and this speed ratio V? A signal corresponding to the switching signal generator 26 is outputted to the switching signal generator 26. Upon receiving this signal, the switching signal generator 26 sends a signal to the electromagnetic switching valve 16.
Output to 18,19°21. As a result, the electromagnetic switching valve 16° 18, 19, 21 is switched to the open position, and the head side of the single rod cylinder 10 is communicated with the hydraulic pump 13.
The rod side of the single rod cylinder 100 communicates with the tank 14, and both the head side and the rod side of the single rod cylinder 11 communicate with the hydraulic pump 13.
この状態にあっては、片ロツドシリンダ１１のロッド側
から押出された圧油が電磁切換弁１８のところで合流し
て片ロッドシリンダ１１のヘッド側に入る。すなわち１
片ロッドシリンダ１１を作動させるために油圧ポンプ１
３から送り出される容量は通常の半分の５０でよい。し
たがって、速房比は前述の場合の１よりも大きい１．３
３となる。In this state, the pressure oil pushed out from the rod side of the single rod cylinder 11 joins at the electromagnetic switching valve 18 and enters the head side of the single rod cylinder 11. i.e. 1
Hydraulic pump 1 to operate single rod cylinder 11
The capacity delivered from 3 may be 50, which is half the normal capacity. Therefore, the velocity ratio is 1.3, which is greater than 1 in the previous case.
It becomes 3.
このとき、片ロツドシリンダ１１はラムシリンダとして
機能する。また、このときの片ロツドシリンダ１１自身
の出力は通常の％となり、前述の圧力Ｐ、のときの全体
の出力を２とすれば、この圧力Ｐ、における全体の出力
は１５となる。At this time, the single rod cylinder 11 functions as a ram cylinder. Further, the output of the single rod cylinder 11 itself at this time is % of the normal output, and if the total output at the aforementioned pressure P is 2, the total output at this pressure P is 15.
また、圧力センサ２４で前述したＰ、よりも小さい第２
図に示すＰ、が検出されると、制御装置２５において同
第２図に示す関係から前述の速変比看よりも大きい速度
比■、が選択され、この速度比ｖ１に相応する信号が切
換信号発生装置２６に出力される。切換信号発生装置２
６はこの信号を受けて第３図のＮＱ３の欄に「０」印で
示した各切換動作をおこなう信号を電磁切換弁１６．１
７，１８゜１９に出力する、これによって電磁切換弁１
６゜１７．１８．１９が開位置に切換えられ、片ロツド
シリンダ１０．１１のヘッド１則およびロッド側が油圧
ポンプ１３に連通する。この場合、片ロッドシリンダ１
０．１１のそれぞれを作動させるために油圧ポンプ１３
から送り出される容量は共に通常の半分の５０でよ＜、
シたがって速度比は２となるっ
また、圧力センサ２４で前述したＰ、よりもさらに小さ
い氾２図に示すＰ、が検出されると、制御装置２５にお
いて同第２図に示す関係から前述の速度比Ｖ、よりも大
きい速度比Ｖ、が選択され、この速度比Ｖ、に相応する
信号が切換信号発生装置２６に出力される。切換信号発
生装置２６はこの信号を受けて第３図のＭ４の欄にｌ−
ＯＪ印で示した各切換動作をおこなう信号を電磁切換弁
１６．１７゜２２．２３に出力する、これによって電磁
切換弁１６．１７，２２．２３が開位置に切換えられ、
片ロッドシリンダ１０のヘッド（Ｉｌｌが油圧ポンプ１
３に連通し、片ロツドシリンダ１０のロッド側がタンク
１４に連通し、片ロツドシリンダ１１のヘッド側および
ロッド側の双方がタンク１４に連通ずる。この場合、片
ロッドシリンダ１１は片ロッドシリンダ１０の作動に引
すられて作動することになり、片ロツドシリンダ１０を
作動させるために油圧ポンプ１３から送り出される容量
は５０でよく、したがって速度比は酵も速い４となる。In addition, in the pressure sensor 24, a second
When P shown in the figure is detected, the control device 25 selects a speed ratio ■ larger than the above-mentioned speed ratio from the relationship shown in FIG. 2, and a signal corresponding to this speed ratio v1 is switched. The signal is output to the signal generator 26. Switching signal generator 2
6 receives this signal and sends a signal to the electromagnetic switching valve 16.1 to perform each switching operation indicated by the "0" mark in the NQ3 column in Fig. 3.
7, 18° 19, this causes the solenoid switching valve 1
6.17.18.19 are switched to the open position, and the head and rod sides of the single-rod cylinder 10.11 communicate with the hydraulic pump 13. In this case, single rod cylinder 1
Hydraulic pump 13 to operate each of 0.11
The capacity sent out from both is 50, which is half of the normal capacity.
Therefore, the speed ratio becomes 2. Furthermore, when the pressure sensor 24 detects P shown in Fig. 2, which is even smaller than the P mentioned above, the control device 25 uses the relation shown in Fig. 2 as described above. A speed ratio V that is larger than the speed ratio V is selected, and a signal corresponding to this speed ratio V is output to the switching signal generator 26. Upon receiving this signal, the switching signal generator 26 inputs l- to the column M4 in FIG.
A signal to perform each switching operation indicated by the OJ symbol is output to the electromagnetic switching valves 16.17° and 22.23, thereby switching the electromagnetic switching valves 16.17 and 22.23 to the open position,
The head of the single rod cylinder 10 (Ill is the hydraulic pump 1
3, the rod side of the single rod cylinder 10 communicates with the tank 14, and both the head side and the rod side of the single rod cylinder 11 communicate with the tank 14. In this case, the single rod cylinder 11 will be operated by being pulled by the operation of the single rod cylinder 10, and the capacity delivered from the hydraulic pump 13 to operate the single rod cylinder 10 may be 50, so the speed ratio is It also becomes a fast 4.
また、指令装置２７が操作されて、速度比ｖ１゜Ｖ、、
Ｖ、、 Ｖ、のいずれかに相応する信号が制御装置２
５に入力されると、切換信号発生装（り２６から該当す
る速度比を得るための切換信号が該当する電磁切換弁に
出力され、これによって圧力センサ２４の出力値にかか
わらず手動により片ロッドシリンダ１０．１１を所望の
速度比で作動させることができる、
このように構成しである実施例にあっては、片ロツドシ
リンダ１０．１１にかかる負荷が小さい場合に、すなわ
ち通常時のポンプ吐出圧であるＰ。In addition, the command device 27 is operated to change the speed ratio v1°V, .
A signal corresponding to either V, , V, is sent to the control device 2.
5, a switching signal for obtaining the corresponding speed ratio is output from the switching signal generator (26) to the corresponding electromagnetic switching valve. In an embodiment constructed in this way, the cylinder 10.11 can be operated at a desired speed ratio, when the load on the single-rod cylinder 10.11 is small, that is, when the normal pump discharge pressure P.
よりもはるかに低圧のＰ、である場合には、速度比を通
常時の４倍程に速くすることができ、しかも油圧ポンプ
１３の容量の大型化等を招くことがなく、作業能率の向
上を図ることができる。When the pressure P is much lower than that of P, the speed ratio can be increased to about four times the normal speed, and the work efficiency is improved without increasing the capacity of the hydraulic pump 13. can be achieved.
第４図は本発明の別の実施例の概略構成を示す回路図で
ある。FIG. 4 is a circuit diagram showing a schematic configuration of another embodiment of the present invention.
この実施例にあっては油圧ポンプ１３の他に、この油圧
ポンプ１３と同等の容量の別の油圧ポンプ１３ａを設け
てあり、油圧ポンプ１３ａとタンク１４との間に電磁切
換弁１５と同等の電磁切換弁１５ａを設けである。また
、油圧ポンプ１３の吐出油の圧力を検出する圧力センサ
２４ａを設けてあり、この圧力センサ２４ａを制御装置
２５に接続させである。制御装置２５は、片ロツドシリ
ンダ１０．１１の駆動時に電磁切換弁１５．１５ａの駆
動部に信号を出力して、これらの電磁切換弁１５．１５
ａを閉止位置に切換える。また、制御装（ｊ！！、２５
には第５図のＭｌからＮｎ６に相応する圧力と速度比の
相関関係が設定されており、前述した実施例と同様に、
圧力センサ２４，２４ａから出力される圧力値に応じて
該当すう：！Ｐ、ｏ比を選択し、切換信号発生装置２６
に出力する。In this embodiment, in addition to the hydraulic pump 13, another hydraulic pump 13a having the same capacity as this hydraulic pump 13 is provided. An electromagnetic switching valve 15a is provided. Further, a pressure sensor 24a is provided to detect the pressure of oil discharged from the hydraulic pump 13, and this pressure sensor 24a is connected to the control device 25. The control device 25 outputs a signal to the drive section of the electromagnetic switching valves 15.15a when the single-rod cylinder 10.11 is driven, so that these electromagnetic switching valves 15.15
Switch a to the closed position. In addition, the control device (j!!, 25
The correlation between pressure and speed ratio corresponding to Ml to Nn6 in FIG. 5 is set, and as in the above-mentioned embodiment,
Applicable depending on the pressure value output from the pressure sensors 24, 24a:! Select the P and O ratios and switch the switching signal generator 26.
Output to.
そして、この実施例にあっては、油圧ポンプ１３ａと片
ロツドシリンダ１０．１１のヘッド側との間に２位置２
方形の電磁切換弁３０．３２をそれぞれ設けてあり、油
圧ポンプ１３ａと片ロツドシリンダ１０，１１のロッド
側との間に２位置２方形の電磁切換弁３１．３３をそれ
ぞれ設げである。In this embodiment, two positions 2 are provided between the hydraulic pump 13a and the head side of the single rod cylinder 10.11.
Square electromagnetic switching valves 30, 32 are provided, and two-position, two-sided electromagnetic switching valves 31, 33 are provided between the hydraulic pump 13a and the rod side of the single-rod cylinders 10, 11, respectively.
このように構成した実施例にあっても、例えば圧力セン
サ２４，２４ａから検出される圧力値に応じて、あるい
は指令装置２７からの信号に応じて制御装置２５が該当
する速度比に相応する信号を切換信号発生装置２６に出
力し、これＫよって当該切換信号発生装置２６は第５図
のＭ１〜ｍ６の１０１印で示す電磁切換弁を開位置に作
動させる信号を出力する。Even in the embodiment configured in this way, the control device 25 generates a signal corresponding to the corresponding speed ratio in response to the pressure value detected from the pressure sensors 24, 24a, or in response to a signal from the command device 27. K is output to the switching signal generating device 26, and the switching signal generating device 26 thereby outputs a signal for operating the electromagnetic switching valves indicated by marks 101 of M1 to m6 in FIG. 5 to the open position.
このように構成した別の実施例にあっては、２つの油圧
ポンプ１３，１３ａを設け、電磁切換弁１６〜２３に加
えて電磁切換弁３０〜３３を設けであることから、最高
で通常時の８倍の速度比を得ることができ、さらに作業
能率の向上を図れる。In another embodiment configured in this way, two hydraulic pumps 13 and 13a are provided, and electromagnetic switching valves 30 to 33 are provided in addition to the electromagnetic switching valves 16 to 23. It is possible to obtain a speed ratio of 8 times that of the previous one, further improving work efficiency.
〈発明の効果〉
本発明の片ロッドシリンダ駆動回路は、以上のように構
成しであることから、片ロッドシリンダにかかる負荷が
小さい場合に、ポンプ容量：の大型化等を要することな
く当該片ロツドシリンダの速変を速くすることができ、
従来に比べて作業能率を向上させることができる効果が
ある。<Effects of the Invention> Since the single rod cylinder drive circuit of the present invention is configured as described above, when the load applied to the single rod cylinder is small, the single rod cylinder drive circuit of the present invention can be operated without increasing the pump capacity. The speed change of the rod cylinder can be made faster,
This has the effect of improving work efficiency compared to conventional methods.
第１図は本発明の片ロツドシリンダ駆動回路の一実施例
の概略構成を示す回路図、第２図は第１図に示す駆動回
路の制御装置で設定されるポンプ吐出圧カー速度比の相
関関係を示す説明図、ｖ、３図は第１図に示す駆動回路
の切換信号発生装置によって出力される切換信号の組合
せを示す説明図、第４図は本発明の別の実施例の概略構
成を示す回路図、第５図は第４図に示す駆動回路の切換
信号発生装置によって出力される切換信号の紹合せを示
す説明図、第６図は従来の片ロツドシリンダ駆動回路を
例示する回路図、第７図は第６図に示す片ロツドシリン
ダ駆動回路におけるポンプ吐出圧カーポンプ吐出流量特
性を示す説明図である。
１０．１１・・・・・・片ロツドシリンダ、１２・°°
“°偵荷体、１３，１３ａ・・・・・・油圧ポンプ、１
４・・・・・・タンク、１５，１５ａ＋ １６，１７
，１８，１９゜２０．２１，２２，２３，３０．３１．
３２．３３・・・・・・電磁切換弁、２４．２４ａ・・
・・・圧力センサ、２５・・・・・・制御装置′、２６
・・・・・切換信号発生装置、２７・・・・・・指令装
置。
、、二′）−′二ニー
ノー１ ｒ
才１０
才 ２ 口
才 ３ 団
ブ 乙 ７
？ ５図FIG. 1 is a circuit diagram showing a schematic configuration of an embodiment of the single rod cylinder drive circuit of the present invention, and FIG. 2 is a correlation between the pump discharge pressure and car speed ratio set by the control device of the drive circuit shown in FIG. FIG. 3 is an explanatory diagram showing the combination of switching signals output by the switching signal generator of the drive circuit shown in FIG. FIG. 5 is an explanatory diagram showing an introduction of switching signals output by the switching signal generator of the drive circuit shown in FIG. 4, and FIG. 6 is a circuit diagram illustrating a conventional single rod cylinder drive circuit. FIG. 7 is an explanatory diagram showing the pump discharge pressure and car pump discharge flow rate characteristics in the single rod cylinder drive circuit shown in FIG. 6. 10.11・・・Single rod cylinder, 12・°°
“° Reconnaissance cargo body, 13, 13a...Hydraulic pump, 1
4... Tank, 15, 15a+ 16, 17
, 18, 19° 20.21, 22, 23, 30.31.
32.33...Solenoid switching valve, 24.24a...
...Pressure sensor, 25...Control device', 26
...Switching signal generator, 27...Command device. ,,2')-'2nino 1 r sai 10 sai 2 mouth sai 3 group bu otsu 7 ? Figure 5
Claims (1)
プに連絡されるものおよびタンクに連絡されるものを含
む少なくとも２つの切換弁をそれぞれ設けるとともに、
上記切換弁を所定の組合せに切換える切換信号発生装置
を設けたことを特徴とする片ロツドシリンダ駆動回路。At least two switching valves, including one connected to the pump and one connected to the tank, are provided on the head side and rod side of the single rod cylinder, respectively, and
A single rod cylinder drive circuit comprising a switching signal generator for switching the switching valves to a predetermined combination.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP29200985A JPS62151601A (en) | 1985-12-26 | 1985-12-26 | Single rod cylinder driving circuit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP29200985A JPS62151601A (en) | 1985-12-26 | 1985-12-26 | Single rod cylinder driving circuit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62151601A true JPS62151601A (en) | 1987-07-06 |
Family
ID=17776344
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP29200985A Pending JPS62151601A (en) | 1985-12-26 | 1985-12-26 | Single rod cylinder driving circuit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62151601A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010203500A (en) * | 2009-03-02 | 2010-09-16 | Ckd Corp | Air cylinder |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5833925A (en) * | 1981-08-18 | 1983-02-28 | 松下電器産業株式会社 | 3-phase rotation automatic controller |
| JPS5950202A (en) * | 1982-09-15 | 1984-03-23 | Kayaba Ind Co Ltd | Control valve device constituting differential circuit |
| JPS59121203A (en) * | 1982-12-27 | 1984-07-13 | Ube Ind Ltd | Method and apparatus for controlling fluid pressure cylinder |
-
1985
- 1985-12-26 JP JP29200985A patent/JPS62151601A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5833925A (en) * | 1981-08-18 | 1983-02-28 | 松下電器産業株式会社 | 3-phase rotation automatic controller |
| JPS5950202A (en) * | 1982-09-15 | 1984-03-23 | Kayaba Ind Co Ltd | Control valve device constituting differential circuit |
| JPS59121203A (en) * | 1982-12-27 | 1984-07-13 | Ube Ind Ltd | Method and apparatus for controlling fluid pressure cylinder |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010203500A (en) * | 2009-03-02 | 2010-09-16 | Ckd Corp | Air cylinder |
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