JP2513964Y2 - Hydraulic circuit for press - Google Patents
Hydraulic circuit for pressInfo
- Publication number
- JP2513964Y2 JP2513964Y2 JP1992073198U JP7319892U JP2513964Y2 JP 2513964 Y2 JP2513964 Y2 JP 2513964Y2 JP 1992073198 U JP1992073198 U JP 1992073198U JP 7319892 U JP7319892 U JP 7319892U JP 2513964 Y2 JP2513964 Y2 JP 2513964Y2
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic cylinder
- chamber
- double
- hydraulic
- cylinder
- 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 - Lifetime
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
- B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
- B30B1/323—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure using low pressure long stroke opening and closing means, and high pressure short stroke cylinder means
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Presses (AREA)
- Press Drives And Press Lines (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本考案は、金属板成形用プレス等
の主として中型の量産向き油圧プレス機に適した油圧回
路に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic circuit mainly suitable for a medium-sized hydraulic press machine for mass production such as a metal plate forming press.
【０００２】[0002]
【従来の技術】従来、５０〜２００ｔ程度の中型の金属
板成形用油圧プレス機に於いては、一般的に図１に示す
ような構成の油圧回路を使用し、プレススライドを１分
間に例えば１００回動作させて成形を行なっている。こ
れに於いて、プレススライドは、油圧シリンダａから出
没するピストン軸ｂで昇降され、該ピストン軸ｂを下降
させる場合は、該油圧シリンダａ内に設けた中軸ｃを介
して中室ｄへ固定容量ポンプｅの圧油を供給すると共
に、プレフィル弁ｆを介してタンクｇから下降用室ｈへ
油を供給し、更にリリーフ弁ｉのベント回路をソレノイ
ド開閉弁ｊで閉じる操作により行なわれる。この時、該
油圧シリンダａの上昇用室ｋ内の油は方向制御弁ｌを介
してタンクｇへと排除される。この下降後にプレススラ
イドに加圧作動を行なわせる場合には、上記の操作に加
え、ソレノイド開閉弁ｍを開いて該下降用室ｈへポンプ
ｅの吐出量の一部を導入する操作を行なう。また、該ピ
ストン軸ｂを上昇させる場合、該ベント回路をソレノイ
ド開閉弁ｊで閉じ、方向制御弁ｌを切換えて該上昇用室
ｋにポンプｅを接続すると共に中室ｄをタンクｇに接続
し、下降用室ｈ内の油はパイロット弁ｎを介して作用す
るパイロット圧により開かれたプレフィル弁ｆを介して
タンクｇに戻すことにより行なう。ｎはプレフィル弁ｆ
を強制的に開弁するためのパイロット圧を導入するパイ
ロット弁である。2. Description of the Related Art Conventionally, in a medium-sized hydraulic press machine for forming a metal plate of about 50 to 200 t, a hydraulic circuit having a structure as shown in FIG. Molding is performed by operating 100 times. In this, the press slide is moved up and down by a piston shaft b protruding and retracted from the hydraulic cylinder a, and when lowering the piston shaft b, the press slide is fixed to the internal chamber d via an intermediate shaft c provided in the hydraulic cylinder a. This is performed by supplying pressure oil from the capacity pump e, supplying oil from the tank g to the descending chamber h via the prefill valve f, and further closing the vent circuit of the relief valve i with the solenoid opening / closing valve j. At this time, the oil in the ascending chamber k of the hydraulic cylinder a is removed to the tank g via the direction control valve 1. When the press slide is to be pressurized after this descent, in addition to the above operation, the solenoid on-off valve m is opened to introduce a part of the discharge amount of the pump e into the descent chamber h. Further, when raising the piston shaft b, the vent circuit is closed by the solenoid opening / closing valve j, the direction control valve 1 is switched to connect the pump e to the raising chamber k and the middle chamber d to the tank g. The oil in the descending chamber h is returned to the tank g through the prefill valve f opened by the pilot pressure acting through the pilot valve n. n is the prefill valve f
Is a pilot valve for introducing a pilot pressure for forcibly opening the valve.
【０００３】[0003]
【考案が解決しようとする課題】上記従来の油圧回路で
プレス作動を高速で行なう場合、例えば１００ｔプレス
ではピストン軸ｂの直径が２１８mmで、中室ｄの直径は
７２mm、油圧シリンダａの下降用室ｈの内径は２３０mm
に設計され、これのプレススライドを１分間に１００回
動作させるときは、プレフィル弁ｆに１６００l/minの
流量が流れるので口径が約１２５mmの大きな弁を使用し
なければならず、タンクｇも大容量になるのでプレフィ
ル弁とタンクのために非常に大きなスペースを用意しな
ければならない不都合があった。また高速でプレフィル
弁ｆの通過流量１６００l/minをON-OFFするので、配管
ラインにショックが発生する欠点があった。更に、油圧
シリンダａの内圧が下降時負圧になり易く、加圧に切換
わってから昇圧するのに時間が掛かり過ぎる欠点もあっ
た。When the press operation is performed at high speed in the above-mentioned conventional hydraulic circuit, for example, in a 100t press, the diameter of the piston shaft b is 218 mm, the diameter of the inner chamber d is 72 mm, and the hydraulic cylinder a is for lowering. The inner diameter of the chamber h is 230 mm
When operating the press slide 100 times a minute, the pre-fill valve f has a flow rate of 1600 l / min, so a large valve with a diameter of about 125 mm must be used, and the tank g is also large. There was the inconvenience of having to prepare a very large space for the prefill valve and the tank because of the capacity. Further, since the flow rate of 1600 l / min passing through the prefill valve f is turned on and off at high speed, there is a drawback that a shock is generated in the piping line. Further, the internal pressure of the hydraulic cylinder a is likely to be a negative pressure when the hydraulic cylinder a is lowered, and it takes too much time to increase the pressure after switching to the pressurization.
【０００４】本考案は、プレス用油圧回路に於けるこう
した不都合、欠点を解決することを目的とするものであ
る。The present invention is intended to solve such inconveniences and drawbacks in a hydraulic circuit for a press.
【０００５】[0005]
【課題を解決するための手段】本考案では、プレススラ
イドを駆動する油圧シリンダを、両側の受圧面積が等し
い高速動作用の小口径の両ロッド油圧シリンダと、両側
の受圧面積が等しい低速高出力用の大口径の両ロッド油
圧シリンダとを直列に連結した２連油圧シリンダで構成
し、両吐出形油圧ポンプの一方の吐出回路に、該小口径
の両ロッド油圧シリンダの上昇用室を接続すると共に該
大口径の両ロッド油圧シリンダの上昇用室にこれより該
一方の吐出回路への流れを許容するチェック弁を介して
接続し、該両吐出形油圧ポンプの他方の吐出回路に、該
小口径の両ロッド油圧シリンダの下降用室を接続すると
共に該大口径の両ロッド油圧シリンダの下降用室に第１
ソレノイド開閉弁を介して接続し、該大口径の両ロッド
油圧シリンダの上昇用室と下降用室を第２ソレノイド開
閉弁を介して互いに接続することにより、上記の目的を
達成するようにした。SUMMARY OF THE INVENTION In the present invention, a hydraulic cylinder for driving a press slide is provided with a small diameter double rod hydraulic cylinder for high speed operation having equal pressure receiving areas on both sides and a low speed and high output having equal pressure receiving areas on both sides. A double-diameter hydraulic cylinder in which a large-diameter double-rod hydraulic cylinder is connected in series, and the ascending chamber of the small-diameter double-rod hydraulic cylinder is connected to one discharge circuit of a double-discharging hydraulic pump. At the same time, it is connected to the ascending chamber of the large diameter double rod hydraulic cylinder via a check valve that allows the flow to the one discharge circuit from this, and is connected to the other discharge circuit of the double discharge hydraulic pump to the small discharge chamber. The descending chamber of the large diameter double rod hydraulic cylinder is connected to the first descending chamber of the large diameter double rod hydraulic cylinder.
The above object is achieved by connecting via a solenoid opening / closing valve, and connecting the raising chamber and the lowering chamber of the large diameter rod hydraulic cylinders to each other via a second solenoid opening / closing valve.
【０００６】[0006]
【作用】上記油圧シリンダをプレス作動のために下降さ
せる場合、大口径の両ロッド油圧シリンダの下降用室と
上昇用室を第２ソレノイド開閉弁により連通しておき、
両吐出形油圧ポンプから上記他方の吐出回路を介して小
口径の両ロッド油圧シリンダの下降用室へ作動油を供給
する。これによって小口径の両ロッド油圧シリンダの上
昇用室の油は該ポンプへと流れ、大口径の両ロッド油圧
シリンダの上昇用室から下降用室へと油が流れる。各油
圧シリンダの上昇用室と下降用室の同口径であるので、
下降のためにタンクから作動油の給排を受けることなく
油圧シリンダを下降作動させることが出来る。When the hydraulic cylinder is lowered for the press operation, the lowering chamber and the raising chamber of the large diameter double rod hydraulic cylinder are communicated with each other by the second solenoid opening / closing valve.
The hydraulic oil is supplied from the double-discharge hydraulic pump to the lowering chamber of the double-rod hydraulic cylinder of small diameter through the other discharge circuit. As a result, the oil in the raising chamber of the small diameter double rod hydraulic cylinder flows to the pump, and the oil flows from the raising chamber of the large diameter double rod hydraulic cylinder to the lowering chamber. Since the rise chamber and the descend chamber of each hydraulic cylinder have the same diameter,
The hydraulic cylinder can be moved downward without receiving or supplying hydraulic oil from the tank for lowering.
【０００７】また、プレススライドに加圧作動を行なわ
せるときは、該ポンプから上記の吐出作動を行なわせ乍
ら更に第１ソレノイド開閉弁を開くと共に第２ソレノイ
ド開閉弁を閉じる。これによってポンプから吐出される
作動油の圧力は大口径の両ロッド油圧シリンダの下降用
室に作用し、その上昇用室の油はチェック弁を介して該
ポンプへと流れ、油圧シリンダは小口径の両ロッド油圧
シリンダ及び大口径の両ロッド油圧シリンダの両方の下
降用室に作用する作動油によりプレススライドに加圧作
動を行なわせる。この加圧作動のための油圧シリンダ１
のストロークはわずかで、このためにポンプから多くの
流量は必要でない。When the press slide is to be pressurized, the discharge operation is performed from the pump to further open the first solenoid opening / closing valve and close the second solenoid opening / closing valve. As a result, the pressure of the hydraulic fluid discharged from the pump acts on the descending chamber of the large diameter double rod hydraulic cylinder, the oil in the ascending chamber flows to the pump through the check valve, and the hydraulic cylinder has a small diameter. The press slide is caused to perform a pressurizing operation by the hydraulic oil acting on the descending chambers of both the double rod hydraulic cylinder and the large diameter double rod hydraulic cylinder. Hydraulic cylinder 1 for this pressurizing operation
Has a small stroke, which does not require much flow from the pump.
【０００８】更に、上記油圧シリンダに上昇作動を行な
わせるときは、該ポンプに前記とは反対の吐出回路に作
動油を吐出させ、小口径の両ロッド油圧シリンダの上昇
用室へ供給する。このとき、小口径の両ロッド油圧シリ
ンダの下降用室の作動油はポンプへと排出され、また大
口径の両ロッド油圧シリンダの下降用室の作動油はその
上昇用室へ循環する。Further, when the hydraulic cylinder is caused to perform the raising operation, the pump causes the hydraulic fluid to be discharged to the discharge circuit opposite to the above and is supplied to the raising chamber of the small diameter double rod hydraulic cylinder. At this time, the hydraulic oil in the lowering chamber of the small diameter double rod hydraulic cylinder is discharged to the pump, and the hydraulic oil in the lowering chamber of the large diameter double rod hydraulic cylinder circulates to the rising chamber.
【０００９】こうしたプレス作動に於いて、油圧シリン
ダからの給排される流量は基本的には図１に示す場合と
同等になるが、ポンプから１０kg/cm2程度のブースト圧
が掛かった状態で各油圧シリンダから強制的に給排する
ので、昇圧時間は短く、１分間に１００回程度の作動を
行なっても配管の口径が約８０mm程度の小さいものが使
用でき、作動油の慣性による衝撃も小さくなり、大きな
タンクを用意する必要もないので設備スペースを小さく
できる。In such a press operation, the flow rate supplied to and discharged from the hydraulic cylinder is basically the same as that shown in FIG. 1, but with a boost pressure of about 10 kg / cm 2 applied from the pump. Since each hydraulic cylinder is forcibly supplied and discharged, the boosting time is short, and even if the operation is performed about 100 times a minute, a pipe with a small diameter of about 80 mm can be used, and there is no impact due to the inertia of the hydraulic oil. Since it is smaller and there is no need to prepare a large tank, the equipment space can be reduced.
【００１０】[0010]
【実施例】本考案の実施例を図面に基づき説明すると、
図２に於いて符号１はプレススライド（図示してない）
を駆動する油圧シリンダで、該油圧シリンダ１は両側の
受圧面積が等しい高速動作用の小口径の両ロッド油圧シ
リンダ２と、両側の受圧面積が等しい低速高出力用の大
口径の両ロッド油圧シリンダ３とを直列に連結した２連
油圧シリンダで構成される。４は電動機等の原動機によ
りパイロットポンプ５と共に駆動される両吐出形油圧ポ
ンプで、該両吐出形油圧ポンプ４は吐出方向を制御する
制御シリンダ６を備えており、電磁弁７のソレノイド８
または９が励磁されると該パイロットポンプ５の吐出圧
が制御シリンダ６を作動し、両吐出形油圧ポンプ４が一
方の吐出回路１０または１１に吐出する。Embodiments of the present invention will be described with reference to the drawings.
In FIG. 2, reference numeral 1 is a press slide (not shown)
The hydraulic cylinder 1 is a double-cylinder hydraulic cylinder having a small diameter for both high speed operation and a large diameter double rod hydraulic cylinder for low speed and high output having the same pressure receiving area on both sides. It is composed of two hydraulic cylinders in which 3 and 3 are connected in series. Reference numeral 4 denotes a dual discharge hydraulic pump driven by a prime mover such as an electric motor together with a pilot pump 5. The dual discharge hydraulic pump 4 includes a control cylinder 6 for controlling the discharge direction, and a solenoid 8 of a solenoid valve 7 is provided.
Or when 9 is excited, the discharge pressure of the pilot pump 5 operates the control cylinder 6, and the double discharge hydraulic pump 4 discharges to one discharge circuit 10 or 11.
【００１１】該一方の吐出回路１０には、該小口径の両
ロッド油圧シリンダ２の上昇用室２ａを接続すると共に
該大口径の両ロッド油圧シリンダ３の上昇用室３ａをこ
れより該一方の吐出回路１０への流れを許容するチェッ
ク弁１２を介して接続する。また、該他方の吐出回路１
１には、該小口径の両ロッド油圧シリンダ２の下降用室
２ｂを接続すると共に該大口径の両ロッド油圧シリンダ
３の下降用室３ｂを第１ソレノイド開閉弁１３を介して
接続した。更に、該大口径の両ロッド油圧シリンダ３の
上昇用室３ａと下降用室３ｂを第２ソレノイド開閉弁１
４を介して互いに接続する。該両吐出形油圧ポンプ４と
該２連油圧シリンダは閉油圧回路で接続された構成にな
るので、回路からの洩れによる作動油の不足を補うため
に、パイロットポンプ５から補充弁１５、１５を介して
作動油を補充するようにした。To the one discharge circuit 10, the raising chamber 2a of the small diameter double rod hydraulic cylinder 2 is connected, and the raising chamber 3a of the large diameter double rod hydraulic cylinder 3 is connected to this one discharge circuit 10. Connection is made via a check valve 12 that allows the flow to the discharge circuit 10. In addition, the other discharge circuit 1
1, the lowering chamber 2b of the small diameter double rod hydraulic cylinder 2 was connected, and the lowering chamber 3b of the large diameter double rod hydraulic cylinder 3 was connected via a first solenoid opening / closing valve 13. Further, the ascending chamber 3a and the descending chamber 3b of the large diameter double rod hydraulic cylinder 3 are connected to the second solenoid opening / closing valve 1
4 are connected to each other. Since the double discharge hydraulic pump 4 and the double hydraulic cylinder are connected by a closed hydraulic circuit, in order to compensate for the shortage of hydraulic oil due to leakage from the circuit, the replenishment valves 15, 15 are supplied from the pilot pump 5. The hydraulic oil was replenished via the.
【００１２】尚、該小口径の両ロッド油圧シリンダ２の
ピストン軸と該大口径の両ロッド油圧シリンダ３のピス
トン軸を、これらの油圧シリンダを貫通した同径の共通
軸で構成し、その下端にプレススライドを取り付けるよ
うにした。It should be noted that the piston shaft of the small diameter double rod hydraulic cylinder 2 and the piston shaft of the large diameter double rod hydraulic cylinder 3 are constituted by a common shaft of the same diameter that penetrates these hydraulic cylinders, and the lower end thereof is formed. The press slide was attached to.
【００１３】その作動を説明すると、該２連油圧シリン
ダをプレス作動のために下降させる場合、予め大口径の
両ロッド油圧シリンダ３の上昇用室３ａと下降用室３ｂ
を第２ソレノイド開閉弁１４により連通しておき、電磁
弁７のソレノイド８を励磁して両吐出形油圧ポンプ４か
ら他方の吐出回路１１に作動油を吐出させる。吐出され
た作動油は該小口径の両ロッド油圧シリンダ２の下降用
室２ｂに流入し、その上昇用室２ａの油は該ポンプ４へ
と流れ、大口径の両ロッド油圧シリンダの上昇用室から
下降用室へと油が流れるので、該小口径の両ロッド油圧
シリンダ２はプレススライドと共に下降する。該下降用
室２ｂはその容積が小さいのでポンプ４からの吐出量で
高速で下降し、各油圧シリンダ２、３の上昇用室と下降
用室の同口径であるので、タンクから作動油の給排を受
けることなく油圧シリンダ１が高速で下降作動する。The operation will be described. When lowering the double hydraulic cylinders for press operation, the ascending chamber 3a and the descending chamber 3b of the large diameter double rod hydraulic cylinders 3 are previously prepared.
Is communicated with the second solenoid opening / closing valve 14, and the solenoid 8 of the solenoid valve 7 is excited to discharge the hydraulic oil from the dual discharge hydraulic pump 4 to the other discharge circuit 11. The discharged hydraulic oil flows into the descending chamber 2b of the small diameter double rod hydraulic cylinder 2, the oil in the ascending chamber 2a flows to the pump 4, and the ascending chamber of the large diameter double rod hydraulic cylinder. Since the oil flows from the to the descending chamber, the small diameter double rod hydraulic cylinder 2 descends together with the press slide. Since the volume of the descending chamber 2b is small, the descending chamber 2b descends at a high speed by the discharge amount from the pump 4, and since the ascending chamber and the descending chamber of the hydraulic cylinders 2 and 3 have the same diameter, the hydraulic oil is supplied from the tank. The hydraulic cylinder 1 descends at high speed without receiving discharge.
【００１４】この下降後に、プレススライドに加圧作動
を行なわせるときは、該ポンプ４から吐出させ乍ら第１
ソレノイド開閉弁１３を開くと共に第２ソレノイド開閉
弁１４を閉じ、ポンプ４からの作動油を大口径の両ロッ
ド油圧シリンダの下降用室３ｂにも供給し、その上昇用
室３ａの油はチェック弁１２を介して該ポンプ４へと排
出させる。油圧シリンダ１は両ロッド油圧シリンダ２、
３の両方の下降用室２ｂ，３ｂに作動油の圧力が作用す
るのでピストン軸には大きな力が発生し、プレススライ
ドは加圧作動を行なう。この加圧作動のための油圧シリ
ンダ１のストロークはわずかであるので、ポンプ４から
は多くの流量が必要でない。After the descent, when the press slide is to be pressed, the pump 4 is first discharged.
The solenoid opening / closing valve 13 is opened and the second solenoid opening / closing valve 14 is closed, and the working oil from the pump 4 is also supplied to the descending chamber 3b of the large diameter double rod hydraulic cylinder, and the oil in the ascending chamber 3a is a check valve. It is discharged to the pump 4 via 12. The hydraulic cylinder 1 is a double rod hydraulic cylinder 2,
Since the pressure of the hydraulic oil acts on both lowering chambers 2b and 3b of No. 3, a large force is generated on the piston shaft, and the press slide performs a pressurizing operation. Since the stroke of the hydraulic cylinder 1 for this pressurizing operation is small, a large flow rate from the pump 4 is not required.
【００１５】更に、該油圧シリンダ１を上昇作動すると
きは、電磁弁７のソレノイド１０を励磁して該ポンプ４
から吐出回路１０に作動油を吐出させ、小口径の両ロッ
ド油圧シリンダ２の上昇用室２ａへ供給する。このと
き、小口径の両ロッド油圧シリンダ２の下降用室２ｂの
作動油はポンプ４へと排出され、大口径の両ロッド油圧
シリンダ３の下降用室３ｂの作動油は第２ソレノイド開
閉弁１４を介して上昇用室３ａへ循環する。Further, when the hydraulic cylinder 1 is operated to rise, the solenoid 10 of the solenoid valve 7 is excited to pump the pump 4
The hydraulic oil is discharged from the discharge circuit 10 to the rising chamber 2a of the double rod hydraulic cylinder 2 having a small diameter. At this time, the hydraulic oil in the lowering chamber 2b of the small diameter double rod hydraulic cylinder 2 is discharged to the pump 4, and the hydraulic oil in the lowering chamber 3b of the large diameter double rod hydraulic cylinder 3 is discharged to the second solenoid opening / closing valve 14 Through the ascending chamber 3a.
【００１６】例えば従来例と同等の１００ｔプレスを考
えたとき、油圧シリンダ２、３のピストン軸の径が１２
０mmで、小口径の両ロッド油圧シリンダ２の直径が１４
０mm、大口径の油圧シリンダ３の直径を２５０mmに設計
すれば、プレス作動で２つの油圧シリンダ１からの給排
される流量は図１に示す場合と略同等になる。しかし各
油圧シリンダ２、３はポンプ４から１０kg/cm2程度のブ
ースト圧が掛かった状態で強制的給排が行なわれるの
で、昇圧時間も短く１分間に１００回程度の作動はシリ
ンダ吸入側であっても口径が約８０mmの小さい配管で対
応できる。作動油の動く量が少ないため、作動油の慣性
による衝撃も小さくなり、大きなタンクは不要になる。For example, considering a 100t press equivalent to the conventional example, the diameter of the piston shaft of the hydraulic cylinders 2 and 3 is 12
With a diameter of 0 mm, the small diameter double rod hydraulic cylinder 2 has a diameter of 14 mm.
If the diameter of the hydraulic cylinder 3 having a diameter of 0 mm and the large diameter is designed to be 250 mm, the flow rate of supply and discharge from the two hydraulic cylinders 1 by the press operation becomes substantially the same as that shown in FIG. However, since the hydraulic cylinders 2 and 3 are forcibly supplied and discharged with the boost pressure of about 10 kg / cm 2 applied from the pump 4, the boosting time is short and about 100 operations per minute are performed on the cylinder intake side. Even if there is, a small pipe with a diameter of about 80 mm can be used. Since the amount of movement of the hydraulic oil is small, the impact due to the inertia of the hydraulic oil is small, and a large tank is unnecessary.
【００１７】[0017]
【考案の効果】以上のように本考案では、油圧プレスの
油圧シリンダを、両側の受圧面積が等しい高速動作用の
小口径の両ロッド油圧シリンダと、両側の受圧面積が等
しい低速高出力用の大口径の両ロッド油圧シリンダとを
直列に連結して構成し、両吐出形油圧ポンプの一方の吐
出回路を、該小口径の両ロッド油圧シリンダの上昇用室
とチェック弁を介して該大口径の両ロッド油圧シリンダ
の上昇用室に接続し、該ポンプの他方の吐出回路に、該
小口径の両ロッド油圧シリンダの下降用室と第１ソレノ
イド開閉弁を介して大口径の両ロッド油圧シリンダの下
降用室を接続し、大口径の両ロッド油圧シリンダの上昇
用室と下降用室を第２ソレノイド開閉弁を介して接続し
たので、単純な閉回路で油圧回路を構成することがで
き、大口径のプレフィル弁や大きなタンクが不要にな
り、油圧シリンダはブースト圧が掛かった状態で作動油
が給排されるので、昇圧時間は短く、プレス用油圧シリ
ンダの配管口径を小さくでき、油圧シリンダの往復によ
る作動油の慣性が小さくなって衝撃が少なくなる等の効
果がある。As described above, according to the present invention, the hydraulic cylinders of the hydraulic press are the same as those of the small diameter double rod hydraulic cylinders for high speed operation where the pressure receiving areas on both sides are the same, and those for low speed and high output where the pressure receiving areas on both sides are the same. A large-diameter double-rod hydraulic cylinder is connected in series, and one discharge circuit of a double-discharging hydraulic pump is connected to the large-diameter double-rod hydraulic cylinder through a rising chamber and a check valve. Connected to the ascending chamber of the double rod hydraulic cylinder, and to the other discharge circuit of the pump through the descending chamber of the small rod hydraulic cylinder and the large solenoid double rod hydraulic cylinder via the first solenoid opening / closing valve. Since the lowering chamber is connected, and the raising chamber and the lowering chamber of the large diameter double rod hydraulic cylinder are connected via the second solenoid opening / closing valve, the hydraulic circuit can be configured with a simple closed circuit. Large caliber pref Valve and large tank are no longer required, and hydraulic oil is supplied and discharged while boost pressure is applied to the hydraulic cylinder, so the pressurization time is short and the piping diameter of the hydraulic cylinder for press can be reduced. The inertia of the hydraulic oil is reduced and the impact is reduced.
【図１】 従来例の線図FIG. 1 is a diagram of a conventional example.
【図２】 本考案の実施例の線図FIG. 2 is a diagram of an embodiment of the present invention.
１ 油圧シリンダ ２ 小口径の
両ロッド油圧シリンダ ３ 大口径の両ロッド油圧シリンダ ２ａ，３ａ
上昇用室 ２ｂ，３ｂ 下降用室 ４ 両吐出形
油圧ポンプ １０ 一方の吐出回路 １１ 他方の
吐出回路 １２ チェック弁 １３ 第１ソ
レノイド開閉弁 １４ 第２ソレノイド開閉弁1 hydraulic cylinder 2 small diameter double rod hydraulic cylinder 3 large diameter double rod hydraulic cylinder 2a, 3a
Ascending chamber 2b, 3b Descent chamber 4 Double discharge hydraulic pump 10 Discharge circuit 11 One discharge circuit 12 Check valve 13 First solenoid opening / closing valve 14 Second solenoid opening / closing valve
Claims (2)
を、両側の受圧面積が等しい高速動作用の小口径の両ロ
ッド油圧シリンダと、両側の受圧面積が等しい低速高出
力用の大口径の両ロッド油圧シリンダとを直列に連結し
た２連油圧シリンダで構成し、両吐出形油圧ポンプの一
方の吐出回路に、該小口径の両ロッド油圧シリンダの上
昇用室を接続すると共に該大口径の両ロッド油圧シリン
ダの上昇用室にこれより該一方の吐出回路への流れを許
容するチェック弁を介して接続し、該両吐出形油圧ポン
プの他方の吐出回路に、該小口径の両ロッド油圧シリン
ダの下降用室を接続すると共に該大口径の両ロッド油圧
シリンダの下降用室に第１ソレノイド開閉弁を介して接
続し、該大口径の両ロッド油圧シリンダの上昇用室と下
降用室を第２ソレノイド開閉弁を介して互いに接続した
ことを特徴とするプレス用油圧回路。1. A hydraulic cylinder for driving a press slide comprises a small diameter double rod hydraulic cylinder for high speed operation where pressure receiving areas on both sides are equal, and a large diameter double rod hydraulic cylinder for low speed and high output where pressure receiving areas on both sides are equal. A double hydraulic cylinder in which the cylinder and the cylinder are connected in series, and the ascending chamber of the rod hydraulic cylinder of the small diameter is connected to one of the discharge circuits of the double discharge hydraulic pump and the hydraulic pressure of the large rod of the double hydraulic cylinder is connected. It is connected to the chamber for raising the cylinder via a check valve that allows the flow to the one discharge circuit, and the other discharge circuit of the double discharge hydraulic pump is connected to the lower rod hydraulic cylinder of the small diameter. And a lower chamber of the large diameter double rod hydraulic cylinder is connected via a first solenoid opening / closing valve, and a rising chamber and a downward chamber of the large diameter double rod hydraulic cylinder are connected to a second solenoid. A hydraulic circuit for a press, characterized in that they are connected to each other via an id opening / closing valve.
ストン軸と上記大口径の両ロッド油圧シリンダのピスト
ン軸は、これらの油圧シリンダを貫通して設けた同径の
共通軸で構成したことを特徴とする請求項１に記載のプ
レス用油圧回路。2. A piston shaft of the small-diameter double-rod hydraulic cylinder and a piston shaft of the large-diameter double-rod hydraulic cylinder are constituted by a common shaft having the same diameter and penetrating the hydraulic cylinders. The hydraulic circuit for a press according to claim 1, which is characterized.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992073198U JP2513964Y2 (en) | 1992-10-20 | 1992-10-20 | Hydraulic circuit for press |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1992073198U JP2513964Y2 (en) | 1992-10-20 | 1992-10-20 | Hydraulic circuit for press |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0639285U JPH0639285U (en) | 1994-05-24 |
| JP2513964Y2 true JP2513964Y2 (en) | 1996-10-09 |
Family
ID=13511213
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1992073198U Expired - Lifetime JP2513964Y2 (en) | 1992-10-20 | 1992-10-20 | Hydraulic circuit for press |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2513964Y2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5865088A (en) * | 1995-07-25 | 1999-02-02 | Komatsu Ltd. | High-speed safety circuit for a hydraulic press |
| CN103603842B (en) * | 2013-12-02 | 2015-12-30 | 北京乐冶液压气动设备技术有限公司 | A kind of compound start cylinder for vibration test and loading method thereof |
| EP2952750B1 (en) | 2014-06-04 | 2018-09-05 | MOOG GmbH | Hydraulic system |
| EP3609692B1 (en) * | 2017-08-01 | 2021-07-21 | Moog GmbH | Apparatus for controlling the switch over of hydraulic cylinders |
-
1992
- 1992-10-20 JP JP1992073198U patent/JP2513964Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0639285U (en) | 1994-05-24 |
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