JP2723882B2 - Hydraulic overload prevention device - Google Patents
Hydraulic overload prevention deviceInfo
- Publication number
- JP2723882B2 JP2723882B2 JP8077092A JP7709296A JP2723882B2 JP 2723882 B2 JP2723882 B2 JP 2723882B2 JP 8077092 A JP8077092 A JP 8077092A JP 7709296 A JP7709296 A JP 7709296A JP 2723882 B2 JP2723882 B2 JP 2723882B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- hydraulic
- receiving surface
- hydraulic chamber
- valve
- 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 - Fee Related
Links
Landscapes
- Fluid-Pressure Circuits (AREA)
- Control Of Presses (AREA)
- Press Drives And Press Lines (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、油圧過負荷防止装
置に関し、さらにそれを用いたプレス装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic overload prevention device, and more particularly to a press device using the same.
【０００２】[0002]
【従来の技術】プレス機械装置では、カムまたはクラン
クなどの機構によってたとえばポンチである一方の型を
往復駆動してたとえばダイスである他方の型との間で被
加工物をプレス加工する。このプレス装置において過負
荷が発生したとき、そのプレス装置の破損を防いで保護
するために、油圧過負荷防止装置が必要になる。2. Description of the Related Art In a press machine, a punch or a die is reciprocally driven by a mechanism such as a cam or a crank to press a workpiece with another die such as a die. When an overload occurs in this press device, a hydraulic overload prevention device is required to prevent and protect the press device from being damaged.
【０００３】典型的な先行技術は、特公平５−５５２４
０に開示され、これは簡略化されて図１０に示される。
プレス加工時に往復動されるピストン１はシリンダ２に
収納され、その油圧室３は管路４を経てシリンダ５内の
小径ピストン６側の油圧室７に接続される。シリンダ５
には小径ピストン６によって開かれる油抜き孔８が形成
される。小径ピストン６と一体的に形成される大径ピス
トン９に臨む空気室１０には空気圧源１１から圧縮空気
が供給されて封入される。[0003] A typical prior art is Japanese Patent Publication No. 5-5524.
0, which is simplified and shown in FIG.
A piston 1 reciprocated during press working is housed in a cylinder 2, and a hydraulic chamber 3 is connected to a hydraulic chamber 7 on a small-diameter piston 6 side in a cylinder 5 via a pipeline 4. Cylinder 5
Is formed with an oil draining hole 8 opened by the small diameter piston 6. Compressed air is supplied from an air pressure source 11 to an air chamber 10 facing a large-diameter piston 9 formed integrally with the small-diameter piston 6 and sealed therein.
【０００４】この先行技術では、空気室１０の空気圧を
たとえば０．９９ＭＰａ以上の高圧力にすることが困難
であり、したがって小径ピストン６に対する大径ピスト
ン９の受圧面積の面積比を大きくする必要がある。した
がって大径ピストン９が大形とならざるを得ない。これ
によって構成が大形化し、設備が大形化し、高価であ
り、しかも応答性が悪い。In this prior art, it is difficult to increase the air pressure in the air chamber 10 to a high pressure of, for example, 0.99 MPa or more. Therefore, it is necessary to increase the area ratio of the pressure receiving area of the large-diameter piston 9 to the small-diameter piston 6. is there. Therefore, the large-diameter piston 9 must be large. This results in a large-sized configuration, large-sized equipment, high cost, and poor response.
【０００５】他の先行技術は図１１に示されている。こ
の先行技術では、管路４は複数のアキュムレータ１２に
おけるシリンダ１３の油圧室１４に接続される。アキュ
ムレータ１２では、ピストン１５を介してＮ2ガスが封
入されたガス室１６が仕切られる。Another prior art is shown in FIG. In this prior art, the pipeline 4 is connected to a hydraulic chamber 14 of a cylinder 13 in a plurality of accumulators 12. In the accumulator 12, a gas chamber 16 filled with N 2 gas is partitioned via a piston 15.
【０００６】この図１１に示される先行技術では、油圧
室３からの圧油の吸収容量を大きくする必要がある場合
には、アキュムレータ１２の容量または数を増加する必
要があり、したがって構成が大形化し、設備が大きくな
り、高価になる。In the prior art shown in FIG. 11, when it is necessary to increase the absorption capacity of the hydraulic oil from the hydraulic chamber 3, it is necessary to increase the capacity or the number of the accumulators 12, and therefore the configuration is large. Shape, equipment becomes large and expensive.
【０００７】さらに他の先行技術は、図１２に簡略化し
て示されている。管路４はばね１７によって弁座に押圧
される弁体１８を備える直動形リリーフ弁１９に接続さ
れる。この先行技術において、管路４からの高圧力の圧
油を逃がすには、ばね１７のばね定数を小さく設定する
必要がある。そのようにすると、リリーフ弁１９が大形
になり、設備が大きくなり、また応答性が低下する。管
路４の圧油の油量が大きいときには、リリーフ弁１９も
また大形にする必要があり、このことによってもまた、
応答性が悪くなることになる。[0007] Yet another prior art is shown in simplified form in FIG. The line 4 is connected to a direct acting relief valve 19 having a valve element 18 pressed against a valve seat by a spring 17. In this prior art, it is necessary to set the spring constant of the spring 17 small in order to release high-pressure hydraulic oil from the pipeline 4. By doing so, the relief valve 19 becomes large, the equipment becomes large, and the responsiveness decreases. When the amount of pressurized oil in the line 4 is large, the relief valve 19 also needs to be large, which also
Responsiveness will be worse.
【０００８】図１０〜図１２にそれぞれ示されている各
先行技術ではまた、油圧室３および管路４内の圧油の過
大な圧力の発生を防ぐ特性を、たとえば遠隔制御などに
よって変化することが困難であるという問題もある。In each of the prior arts shown in FIGS. 10 to 12, the characteristics of preventing the generation of excessive pressure of the hydraulic oil in the hydraulic chamber 3 and the pipeline 4 are changed by, for example, remote control. There is also a problem that is difficult.
【０００９】さらに他の先行技術は、図１３に示されて
いる。この先行技術では、管路４はピストン２０が収納
されたシリンダ２１の油圧室２２に接続され、ピストン
２０が弁座から離間したときにもう１つの油圧室２３か
らタンクに圧油が逃がされる。管路４にはパイロット油
路２４が接続され、シリンダ２１のパイロット室２５が
さらに接続され、リリーフ弁２６が設けられ、こうして
自己圧パイロット制御が行われる。Yet another prior art is shown in FIG. In this prior art, the pipeline 4 is connected to a hydraulic chamber 22 of a cylinder 21 in which a piston 20 is housed, and when the piston 20 is separated from a valve seat, pressure oil is released from another hydraulic chamber 23 to a tank. A pilot oil passage 24 is connected to the pipe 4, a pilot chamber 25 of the cylinder 21 is further connected, and a relief valve 26 is provided, thus performing self-pressure pilot control.
【００１０】図１３に示される先行技術では、リリーフ
弁２６はパイロット室２５の圧油の開弁する設定圧を調
整するので、構成の小形化が可能であるという利点があ
る。さらに図１３の先行技術では、リリーフ弁２６のリ
リーフ圧をたとえば遠隔制御して変化することが可能で
ある。また安価に実現することができるという利点もあ
る。しかしながらリリーフ弁２６が開いた後に、ピスト
ン２０が弁座から離間して、管路４の圧油がタンクに流
れることになり、したがって応答性が悪いという問題が
ある。In the prior art shown in FIG. 13, since the relief valve 26 adjusts the set pressure at which the pressure oil in the pilot chamber 25 opens, there is an advantage that the configuration can be downsized. Further, in the prior art of FIG. 13, the relief pressure of the relief valve 26 can be changed by, for example, remote control. Another advantage is that it can be realized at low cost. However, after the relief valve 26 is opened, the piston 20 separates from the valve seat, and the pressure oil in the pipeline 4 flows to the tank, and therefore, there is a problem that response is poor.
【００１１】[0011]
【発明が解決しようとする課題】本発明の目的は、構成
を小形化し、安価に実現することができ、しかも応答性
を向上し、さらに遠隔制御などによって過負荷防止特性
を変化することができるようにした油圧過負荷防止装置
およびそれを用いたプレス装置を提供することである。SUMMARY OF THE INVENTION An object of the present invention is to reduce the size of the structure, to realize it at low cost, to improve the responsiveness, and to change the overload prevention characteristic by remote control or the like. An object of the present invention is to provide a hydraulic overload prevention device and a press device using the same.
【００１２】[0012]
【課題を解決するための手段】本発明は、（ａ）弁体で
あって、弁体の軸線方向一方端に第１受圧面を有する大
径部と、この大径部に弁体の軸線方向に連なりかつ弁体
の軸線方向他方端に第１受圧面よりも小さい第２受圧面
を有する小径部とを備え、第１受圧面と第２受圧面との
間で弁体の軸線方向に第２受圧面と同じ側で第１受圧面
よりも小さい第３受圧面を有する弁体と、（ｂ）弁体を
収納し、大径部を案内し、かつ小径部が着座する弁座を
有し、第１受圧面が臨む第１油圧室と、弁体が弁座に着
座している状態で第２受圧面が臨む第２油圧室と、第３
受圧面が臨み弁座から小径部が離間して第２油圧室に連
なる第３油圧室とを形成し、過大な油圧の発生を防止す
べき油圧回路が、第２または第３油圧室のいずれか一方
に接続され、第２または第３油圧室のいずれか他方にタ
ンクが接続されるケーシングと、（ｃ）第１油圧室に接
続されるアキュムレータと、（ｄ）圧油を供給する油圧
源と、（ｅ）第１油圧室と油圧源との間に介在され、第
１油圧室側の２次圧を予め定める第１の値に調圧する減
圧弁と、（ｆ）第１油圧室の油路に接続され、第１の値
未満の予め定める第２の値に設定圧が定められて余分の
圧油をタンクに戻すリリーフ弁とを含むことを特徴とす
る油圧過負荷防止装置である。 また本発明は、（ａ）弁体であって、弁体の軸線方向一
方端に第１受圧面を有する大径部と、この大径部に弁体
の軸線方向に連なりかつ弁体の軸線方向他方端に第１受
圧面よりも小さい第２受圧面を有する小径部とを備え、
第１受圧面と第２受圧面との間で弁体の軸線方向に第２
受圧面と同じ側で第１受圧面よりも小さい第３受圧面を
有する弁体と、（ｂ）弁体を収納し、大径部を案内し、
かつ小径部が着座する弁座を有し、第１受圧面が臨む第
１油圧室と、弁体が弁座に着座している状態で第２受圧
面が臨む第２油圧室と、第３受圧面が臨み弁座から小径
部が離間して第２油圧室に連なる第３油圧室とを形成
し、過大な油圧の発生を防止すべき油圧回路が、第２ま
たは第３油圧室のいずれか一方に接続され、第２または
第３油圧室のいずれか他方にタンクが接続されるケーシ
ングと、（ｃ）第１油圧室に接続されるアキュムレータ
と、（ｄ）圧油を供給する油圧源と、（ｅ）第１油圧室
と油圧源との間に介在され、第１油圧室側の２次圧を予
め定める値に調圧し、しかも第１油圧室側の余分の圧油
をタンクに戻す減圧弁とを含むことを特徴とする油圧過
負荷防止装置である。 また本発明のリリーフ弁は、電磁比例リリーフ弁である
ことを特徴とする。 また本発明の減圧弁は、電磁比例減圧弁であることを特
徴とする。 また本発明のアキュムレータは、圧油室とガス室とを仕
切る部材が、剛性容器内で変形可能または移動可能であ
る構成を有し、その圧油室が第１油圧室に接続されるこ
とを特徴とする。 また本発明は、（ａ）一方の型を、シリンダを介して往
復駆動源に連結し、前記一方の型と他方の型との間で被
加工物をプレス加工するプレス装置本体と、（ｂ）油圧
過負荷防止装置であって、（ｂ１）弁体であって、弁体
の軸線方向一方端に第１受圧面を有する大径部と、この
大径部に弁体の軸線方向に連なりかつ弁体の軸線方向他
方端に第１受圧面よりも小さい第２受圧面を有する小径
部とを備え、第１受圧面と第２受圧面との間で弁体の軸
線方向に第２受圧面と同じ側で第１受圧面よりも小さい
第３受圧面を有する弁体と、（ｂ２）弁体を収納し、大
径部を案内し、かつ小径部が着座する弁座を有し、第１
受圧面が臨む第１油圧室と、弁体が弁座に着座している
状態で第２受圧面が臨む第２油圧室と、第３受圧面が臨
み弁座から小径部が離間して第２油圧室に連なる第３油
圧室とを形成し、過大な油圧の発生を防止すべき油圧回
路が、第２または第３油圧室のいずれか一方に接続さ
れ、第２または第３油圧室のいずれか他方にタンクが接
続されるケーシングと、（ｂ３）第１油圧室に接続され
るアキュムレータと、（ｂ４）圧油を供給する油圧源
と、（ｂ５）第１油圧室と油圧源との間に介在され、第
１油圧室側の２次圧を予め定める第１の値に調圧する減
圧弁と、（ｂ６）第１油圧室の油路に接続され、第１の
値未満の予め定める第２の値に設定圧が定められて余分
の圧油をタンクに戻すリリーフ弁とを備える油圧過負荷
防止装置とを含むプレス装置である。 さらに本発明は、（ａ）一方の金型を、シリンダを介し
て往復駆動源に連結し、前記一方の金型と他方の金型と
の間で被加工物をプレス加工するプレス装置本体と、
（ｂ）油圧過負荷防止装置であって、（ｂ１）弁体であ
って、弁体の軸線方向一方端に第１受圧面を有する大径
部と、この大径部に弁体の軸線方向に連なりかつ弁体の
軸線方向他方端に第１受圧面よりも小さい第２受圧面を
有する小径部とを備え、第１受圧面と第２受圧面との間
で弁体の軸線方向に第２受圧面と同じ側で第１受圧面よ
りも小さい第３受圧面を有する弁体と、（ｂ２）弁体を
収納し、大径部を案内し、かつ小径部が着座する弁座を
有し、第１受圧面が臨む第１油圧室と、弁体が弁座に着
座している状態で第２受圧面が臨む第２油圧室と、第３
受圧面が臨み弁座から小径部が離間して第２油圧室に連
なる第３油圧室とを形成し、過大な油圧の発生を防止す
べき油圧回路が、第２または第３油圧室のいずれか一方
に接続され、第２または第３油圧室のいずれか他方にタ
ンクが接続されるケーシングと、（ｂ３）第１油圧室に
接続されるアキュムレータと、（ｂ４）圧油を供給する
油圧源と、（ｂ５）第１油圧室と油圧源との間に介在さ
れ、第１油圧室側の２次圧を予め定める値に調圧し、し
かも第１油圧室側の余分の圧油をタンクに戻す減圧弁と
を備える油圧過負荷防止装置とを含むことを特徴とする
プレス装置である。According to the present invention, there is provided (a) a valve element, a large-diameter portion having a first pressure receiving surface at one end in the axial direction of the valve element, and an axial line of the valve element provided at the large-diameter portion. A small-diameter portion having a second pressure-receiving surface smaller than the first pressure-receiving surface at the other end in the axial direction of the valve body in the axial direction of the valve-body, between the first pressure-receiving surface and the second pressure-receiving surface. A valve body having a third pressure-receiving surface smaller than the first pressure-receiving surface on the same side as the second pressure-receiving surface; and (b) a valve seat that houses the valve body, guides the large-diameter portion, and seats the small-diameter portion. A first hydraulic chamber facing the first pressure receiving surface, a second hydraulic chamber facing the second pressure receiving surface in a state where the valve body is seated on the valve seat,
A third hydraulic chamber which faces the pressure receiving surface and has a small-diameter portion separated from the valve seat to form a third hydraulic chamber connected to the second hydraulic chamber, and a hydraulic circuit for preventing generation of excessive hydraulic pressure is provided in either the second or third hydraulic chamber. A casing connected to one of the second and third hydraulic chambers, and a tank connected to the other of the second and third hydraulic chambers; (c) an accumulator connected to the first hydraulic chamber; and (d) a hydraulic source for supplying pressure oil. (E) a pressure reducing valve interposed between the first hydraulic chamber and the hydraulic pressure source to regulate the secondary pressure on the first hydraulic chamber side to a first predetermined value, and (f) a pressure reducing valve for the first hydraulic chamber. A relief valve connected to the oil passage, the relief pressure valve being set to a predetermined second value less than the first value and returning excess pressure oil to the tank. . Also, the present invention provides (a) a valve body, a large-diameter portion having a first pressure-receiving surface at one end in the axial direction of the valve body, an axial line of the valve body connected to the large-diameter portion in the axial direction of the valve body. A small-diameter portion having a second pressure-receiving surface smaller than the first pressure-receiving surface at the other end in the direction,
In the axial direction of the valve body between the first pressure receiving surface and the second pressure receiving surface in the second direction,
A valve body having a third pressure-receiving surface smaller than the first pressure-receiving surface on the same side as the pressure-receiving surface, and (b) housing the valve body and guiding the large-diameter portion;
A first hydraulic chamber having a valve seat on which the small-diameter portion is seated and facing the first pressure receiving surface; a second hydraulic chamber facing the second pressure receiving surface while the valve element is seated on the valve seat; A third hydraulic chamber which faces the pressure receiving surface and has a small-diameter portion separated from the valve seat to form a third hydraulic chamber connected to the second hydraulic chamber, and a hydraulic circuit for preventing generation of excessive hydraulic pressure is provided in either the second or third hydraulic chamber. A casing connected to one of the second and third hydraulic chambers, and a tank connected to the other of the second and third hydraulic chambers; (c) an accumulator connected to the first hydraulic chamber; and (d) a hydraulic source for supplying pressure oil. And (e) interposed between the first hydraulic chamber and the hydraulic pressure source to regulate the secondary pressure on the first hydraulic chamber side to a predetermined value, and to supply excess pressure oil on the first hydraulic chamber side to the tank. And a return pressure reducing valve. Further, the relief valve according to the present invention is an electromagnetic proportional relief valve. The pressure reducing valve of the present invention is an electromagnetic proportional pressure reducing valve. The accumulator of the present invention has a configuration in which a member that separates the pressure oil chamber and the gas chamber is configured to be deformable or movable in a rigid container, and that the pressure oil chamber is connected to the first hydraulic chamber. Features. The present invention also provides (a) a press device main body for connecting one of the dies to a reciprocating drive source via a cylinder and pressing a workpiece between the one and the other dies; (B) a hydraulic pressure overload prevention device, (b1) a valve body, a large diameter portion having a first pressure receiving surface at one end in the axial direction of the valve body, and a large diameter portion connected to the large diameter portion in the axial direction of the valve body; And a small-diameter portion having a second pressure-receiving surface smaller than the first pressure-receiving surface at the other end in the axial direction of the valve body, and a second pressure-receiving portion in the axial direction of the valve body between the first pressure-receiving surface and the second pressure-receiving surface. A valve body having a third pressure receiving surface smaller than the first pressure receiving surface on the same side as the surface, and (b2) a valve seat that houses the valve body, guides the large diameter portion, and seats the small diameter portion, First
A first hydraulic chamber facing the pressure receiving surface, a second hydraulic chamber facing the second pressure receiving surface in a state where the valve body is seated on the valve seat, and a second hydraulic chamber facing the third pressure receiving surface and the small diameter portion being separated from the valve seat; A third hydraulic chamber connected to the second hydraulic chamber is formed, and a hydraulic circuit for preventing generation of excessive hydraulic pressure is connected to one of the second and third hydraulic chambers. (B3) an accumulator connected to the first hydraulic chamber, (b4) a hydraulic source for supplying pressure oil, and (b5) a hydraulic source for the first hydraulic chamber and the hydraulic source. A pressure reducing valve interposed therebetween to regulate the secondary pressure on the first hydraulic chamber side to a predetermined first value; and (b6) a predetermined pressure less than the first value and connected to an oil passage of the first hydraulic chamber. A relief valve that sets a set pressure to a second value and returns excess pressurized oil to the tank. It is a device. Further, the present invention provides (a) a press device body for connecting one of the dies to a reciprocating drive source via a cylinder and pressing a workpiece between the one of the dies and the other of the dies. ,
(B) a hydraulic overload prevention device, (b1) a valve element, a large-diameter portion having a first pressure-receiving surface at one end in the axial direction of the valve element, and an axial direction of the valve element at the large-diameter portion; And a small-diameter portion having a second pressure-receiving surface smaller than the first pressure-receiving surface at the other end in the axial direction of the valve element, and a small-diameter portion having a second pressure-receiving surface smaller than the first pressure-receiving surface. (2) a valve body having a third pressure-receiving surface smaller than the first pressure-receiving surface on the same side as the pressure-receiving surface; A first hydraulic chamber facing the first pressure receiving surface, a second hydraulic chamber facing the second pressure receiving surface in a state where the valve body is seated on the valve seat,
A hydraulic circuit that faces the pressure receiving surface, forms a third hydraulic chamber connected to the second hydraulic chamber with the small diameter part separated from the valve seat, and prevents generation of excessive hydraulic pressure, is provided by either the second or third hydraulic chamber. A casing connected to one of the second and third hydraulic chambers, and a tank connected to the other of the second and third hydraulic chambers; (b3) an accumulator connected to the first hydraulic chamber; and (b4) a hydraulic source for supplying pressure oil. And (b5) interposed between the first hydraulic chamber and the hydraulic pressure source to regulate the secondary pressure on the first hydraulic chamber side to a predetermined value, and to supply excess pressure oil on the first hydraulic chamber side to the tank. A press device comprising: a hydraulic pressure overload prevention device including a return pressure reducing valve.
【００１３】本発明に従えば、ケーシングに収納される
弁体は、大径部と小径部とを有し、第２または第３油圧
室のいずれか一方は過大な油圧の発生を防止すべき油圧
回路に接続し、いずれか他方はタンクに接続し、大径部
の第１受圧面が臨む第１油圧室には、アキュムレータを
接続する。さらにこの第１油圧室には、油圧源から減圧
弁を経て作動油である圧油を供給し、リリーフ弁から
は、その第１油圧室側の余分の圧油をタンクに戻す。ま
たはこの減圧弁とリリーフ弁との組合わせの代わりに、
油圧源からの油圧を減圧するとともに、第１油圧室側の
余分の圧油をタンクに戻す構成を有する減圧弁を用いて
もよく、この減圧弁としてはたとえばバランスピストン
形減圧弁またはスプール形パイロット動作直動弁によっ
て実現することができる。 減圧弁またはリリーフ弁は、電磁比例形の構成として遠
隔制御することが容易に可能である。 本発明に従えば、リリーフ弁を用い、またはリリーフ機
能を有する減圧弁を用いることによって、第１油圧室内
の過大な圧力となった圧油をアキュムレータによって吸
収するとともに余分な圧油をタンクに戻すことによっ
て、アキュムレータは第１油圧室における弁体の変位に
よる言わばストロークボリウムを吸収することができる
程度の小容量であればよく、したがって弁体の質量を小
さくし、構成の小形化が図られ、設備を小さくすること
ができ、コストを低減することができる。また弁体が小
形であり、応答性を向上することができる。 さらに本発明のプレス装置に従えば、ポンチとダイスで
ある金型によるプレス加工時の過負荷の発生が防がれ、
プレス装置の破損を防ぐことができる。According to the present invention, the valve element housed in the casing has a large-diameter portion and a small-diameter portion, and one of the second and third hydraulic chambers should prevent the generation of excessive hydraulic pressure. An accumulator is connected to the hydraulic circuit, one of the other is connected to the tank, and the first hydraulic chamber facing the first pressure receiving surface of the large diameter portion. Further, the first hydraulic chamber is supplied with hydraulic oil as hydraulic oil from a hydraulic source via a pressure reducing valve, and the relief valve returns excess hydraulic oil on the first hydraulic chamber side to the tank. Or instead of this combination of pressure reducing valve and relief valve,
A pressure reducing valve configured to reduce the hydraulic pressure from the hydraulic pressure source and return excess pressure oil in the first hydraulic chamber to the tank may be used. As the pressure reducing valve, for example, a balance piston type pressure reducing valve or a spool type pilot valve may be used. The operation can be realized by a direct acting valve. The pressure reducing or relief valve can easily be remotely controlled as an electromagnetic proportional configuration. According to the present invention, by using a relief valve or a pressure-reducing valve having a relief function, the excessive pressure oil in the first hydraulic chamber is absorbed by the accumulator and excess pressure oil is returned to the tank. Accordingly, the accumulator may have a small capacity that can absorb the stroke volume due to the displacement of the valve element in the first hydraulic chamber. Therefore, the mass of the valve element is reduced, and the configuration is downsized. The equipment can be made smaller and the cost can be reduced. In addition, the valve body is small, and responsiveness can be improved. Furthermore, according to the press device of the present invention, occurrence of overload at the time of press working with a die that is a punch and a die is prevented,
The press device can be prevented from being damaged.
【００１４】[0014]
【発明の実施の形態】図１は、本発明の実施の一形態の
油圧回路図である。機械プレス装置本体において、過大
な油圧の発生を防止すべき油圧回路２９は、シリンダ３
０に収容されたピストン３１による油圧室３２に管路３
３が接続されて構成される。FIG. 1 is a hydraulic circuit diagram of an embodiment of the present invention. In the main body of the mechanical press device, the hydraulic circuit 29 for preventing the generation of excessive hydraulic pressure is
Line 3 in the hydraulic chamber 32 by the piston 31 housed in the
3 are connected.
【００１５】この管路３３は、油圧過負荷防止装置３４
のケーシング３５に接続される。ケーシング３５は直円
筒状の内周面を有する部分３６とその下部に連なる大略
的に中空円錐状の部分３７とを含む。円錐状の部分３７
は、弁座３８を構成する。The pipeline 33 is provided with a hydraulic overload prevention device 34.
Is connected to the casing 35. The casing 35 includes a portion 36 having a right cylindrical inner peripheral surface and a substantially hollow conical portion 37 connected to a lower portion thereof. Conical part 37
Constitutes the valve seat 38.
【００１６】ケーシング３５に収納される弁体３９は、
直円筒状の部分３６に案内される大径部４０と、この大
径部４０に固定される小径部４１とを含む。大径部４０
と小径部４１とは、弁体３９の軸線４２上に軸線を有す
る。大径部４０は、弁体３９の軸線４２の方向の一方端
（図１の上方端）に第１受圧面４３を有する。小径部４
１は、軸線４２方向の他方端（図１の下方端）に、第１
受圧面４３よりも小さい第２受圧面４４を有する。弁体
３９の大径部４０にはまた、第１受圧面４３と第２受圧
面４４との間で軸線４２方向に第２受圧面４４と同じ側
で大径部４０の図１における下方に臨んで第３受圧面４
５を有する。第３受圧面４５は、第１受圧面４３よりも
小さい。The valve body 39 housed in the casing 35 is
A large-diameter portion 40 guided by the right cylindrical portion 36 and a small-diameter portion 41 fixed to the large-diameter portion 40 are included. Large diameter part 40
The small diameter portion 41 has an axis on the axis 42 of the valve body 39. The large diameter portion 40 has a first pressure receiving surface 43 at one end (upper end in FIG. 1) in the direction of the axis 42 of the valve body 39. Small diameter part 4
1 is a first end at the other end in the direction of the axis 42 (a lower end in FIG. 1).
It has a second pressure receiving surface 44 smaller than the pressure receiving surface 43. The large-diameter portion 40 of the valve body 39 is also provided between the first pressure-receiving surface 43 and the second pressure-receiving surface 44 in the direction of the axis line 42 on the same side as the second pressure-receiving surface 44 in FIG. The third pressure receiving surface 4
5 The third pressure receiving surface 45 is smaller than the first pressure receiving surface 43.
【００１７】ケーシング３５は、第１受圧面４３が臨む
第１油圧室４７と、弁体３９の小径部４１の端面が弁座
３８に着座している状態で第２受圧面４４が臨む第２油
圧室４８と、第３受圧面４５が臨み弁座３８から小径部
４１が離間して第２油圧室４８に連なる第３油圧室４９
とを形成する。第２油圧室４８は、管路５０を経てタン
クに接続される。第３油圧室４９は管路３３に接続され
る。第３油圧室４９には油圧源５１から逆止弁５２を経
て、防止すべき過大な油圧未満の圧力で圧油が供給され
る。The casing 35 has a first hydraulic chamber 47 in which the first pressure receiving surface 43 faces, and a second hydraulic pressure chamber 44 in which the second pressure receiving surface 44 faces with the end surface of the small diameter portion 41 of the valve body 39 seated on the valve seat 38. The hydraulic chamber 48 and a third hydraulic chamber 49 in which the third pressure receiving surface 45 faces and the small-diameter portion 41 is separated from the valve seat 38 and communicates with the second hydraulic chamber 48.
And are formed. The second hydraulic chamber 48 is connected to the tank via a pipe 50. The third hydraulic chamber 49 is connected to the pipeline 33. Pressure oil is supplied to the third hydraulic chamber 49 from the hydraulic pressure source 51 via the check valve 52 at a pressure lower than an excessively high hydraulic pressure to be prevented.
【００１８】第１油圧室４７は、アキュムレータ５３に
接続されるとともに、管路５４に接続される。The first hydraulic chamber 47 is connected to the accumulator 53 and to a pipe 54.
【００１９】図２は、図１に示されるケーシング３５と
弁体３９とアキュムレータ５３との具体的な構成を示す
断面図である。アキュムレータ５３は、圧油室５５とガ
ス室５６とを仕切る部材５７が鋼などの剛性容器５８内
で変形可能に設けられて構成される。部材５７は、ゴム
などの伸縮可撓性を有する材料から成る。ガス室５６に
は、たとえばＮ2などの不活性ガスが充填される。容器
５８の図２における下部は、ケーシング３５に気密に固
定され、これによって第１油圧室４７はアキュムレータ
５３の圧油室５５と連通して接続される。ケーシング３
５には管路５４が接続されて第１油圧室４７に連通され
る。FIG. 2 is a sectional view showing a specific structure of the casing 35, the valve body 39 and the accumulator 53 shown in FIG. The accumulator 53 is configured such that a member 57 that partitions the pressure oil chamber 55 and the gas chamber 56 is provided so as to be deformable in a rigid container 58 such as steel. The member 57 is made of a material having elasticity such as rubber. The gas chamber 56 is filled with an inert gas such as N 2 . The lower portion of the container 58 in FIG. 2 is airtightly fixed to the casing 35, whereby the first hydraulic chamber 47 is connected to and connected to the pressure oil chamber 55 of the accumulator 53. Casing 3
A pipe 54 is connected to 5 and communicates with the first hydraulic chamber 47.
【００２０】本発明の実施の他の形態では、前記変形可
能な部材５７に代えて、容器５８が有底の直円筒状シリ
ンダによって実現され、そのシリンダ内に図２の上下に
移動可能な直円柱状ピストンが設けられ、このピストン
によって圧油室５５とガス室５６とを仕切るように構成
してもよく、さらにその他の構成であってもよい。In another embodiment of the present invention, instead of the deformable member 57, the container 58 is realized by a bottomed straight cylindrical cylinder, in which a vertical movable cylinder shown in FIG. A cylindrical piston may be provided, and the piston may separate the pressure oil chamber 55 and the gas chamber 56, or may have another configuration.
【００２１】第１〜第３受圧面４３〜４５の各受圧面積
Ｓ４３，Ｓ４４，Ｓ４５は、たとえば式１および式２の
ように定められる。Each of the pressure receiving areas S43, S44, S45 of the first to third pressure receiving surfaces 43 to 45 is determined, for example, as shown in equations (1) and (2).
【００２２】[0022]
【数１】 (Equation 1)
【００２３】第１油圧室４７に接続される管路５４に
は、油圧ポンプなどの油圧源６０から管路９８を経て、
減圧弁６１を介して圧油が供給される。管路５４には、
リリーフ弁６２が接続される。減圧弁６１は、管路５
４、したがって第１油圧室４７側の２次圧を、予め定め
る第１の値Ｐ１に調圧する。リリーフ弁６２は、第１の
値Ｐ１未満の予め定める第２の値Ｐ２（Ｐ１＞Ｐ２）に
開弁する設定圧が定められて、管路５４の余分の圧油を
タンクに戻す。The pipeline 54 connected to the first hydraulic chamber 47 is connected to a hydraulic source 60 such as a hydraulic pump via a pipeline 98 via a pipeline 98.
Pressure oil is supplied via the pressure reducing valve 61. In conduit 54,
The relief valve 62 is connected. The pressure reducing valve 61 is connected to the pipe 5
4, the secondary pressure on the first hydraulic chamber 47 side is adjusted to a predetermined first value P1. The set pressure at which the relief valve 62 opens to a predetermined second value P2 (P1> P2) smaller than the first value P1 is determined, and excess pressure oil in the pipeline 54 is returned to the tank.
【００２４】油圧回路３９における油圧室３２および管
路３３内のたとえば油圧３００ｋｇ／ｃｍ2以上の過大
な油圧の発生を防止するには、弁体３９の第１〜第３受
圧面４３〜４５を前述の式１および式２のように定め、
これによって第１油圧室４７に管路５４を介して接続さ
れるリリーフ弁６２の設定圧はＰ２＝１００ｋｇ／ｃｍ
2に定め、減圧弁６１の２次圧Ｐ１は、設定圧Ｐ２より
も僅かに大きい値に定め、油圧源６０から減圧弁６１に
供給される圧油の圧力は、２次圧Ｐ１を超える値であっ
て、たとえば１１０〜１４０ｋｇ／ｃｍ2に定められ
る。こうして油圧室３２、管路３３および第３油圧室４
９の圧力Ｐ３に関して式３が成立するとき、リリーフ弁
６２が開く。In order to prevent the generation of an excessive oil pressure of, for example, 300 kg / cm 2 or more in the hydraulic chamber 32 and the pipeline 33 in the hydraulic circuit 39, the first to third pressure receiving surfaces 43 to 45 of the valve body 39 are required. Defined as in Equations 1 and 2 above,
As a result, the set pressure of the relief valve 62 connected to the first hydraulic chamber 47 via the pipe 54 is P2 = 100 kg / cm.
2 , the secondary pressure P1 of the pressure reducing valve 61 is set to a value slightly larger than the set pressure P2, and the pressure of the pressure oil supplied from the hydraulic pressure source 60 to the pressure reducing valve 61 is a value exceeding the secondary pressure P1. For example, 110 to 140 kg / cm 2 . Thus, the hydraulic chamber 32, the pipe line 33 and the third hydraulic chamber 4
When Expression 3 holds for the pressure P3 of No. 9, the relief valve 62 opens.
【００２５】 Ｐ３・Ｓ４５ ＞ Ｐ２・Ｓ１ …（３） したがって弁体３９は図１および図２の上方に移動して
小径部４１が弁座３８から離間する。したがって第３油
圧室４９の圧油は、第２油圧室４８から管路５０を経て
タンクに逃がされ、第３油圧室４９の圧力が制御され
る。このような弁体３９の弁座３８からの離間によるリ
リーフ機能は、たとえば３１．５ＭＰａ、流量１９００
０Ｌ／ｍｉｎであって高圧力、大流量に対応することが
できる。P3 · S45> P2 · S1 (3) Accordingly, the valve body 39 moves upward in FIGS. 1 and 2, and the small diameter portion 41 is separated from the valve seat 38. Therefore, the pressure oil in the third hydraulic chamber 49 is released from the second hydraulic chamber 48 to the tank via the conduit 50, and the pressure in the third hydraulic chamber 49 is controlled. Such a relief function by separating the valve body 39 from the valve seat 38 is, for example, 31.5 MPa and a flow rate of 1900.
It is 0 L / min and can correspond to a high pressure and a large flow rate.
【００２６】図３は図１および図２に示される油圧過負
荷防止装置３４に関連して実施される機械プレス装置本
体６３の縦断面図であり、図４は図３の切断面線ＩＶ−
ＩＶから見た断面図である。ハウジング７０内には上下
動するピストン３０を構成する移動体７１が配置され
る。水平な回転軸線まわりに駆動される駆動軸７３には
クランク７３ａが形成され、このクランク７３ａに偏心
部材７２が回転可能に嵌まり込んでクランク機構が構成
される。偏心部材７２にはピストン３１が固定される。
偏心部材７２の下部のピストン３０にはポンチである一
方の型が固定され、またハウジング７０の下部の支持体
６９にはダイスである他方の型が固定され、こうして打
抜きなどの剪断または絞りなどの成形加工などの塑性変
形プレス加工が行われる。FIG. 3 is a longitudinal sectional view of a main body 63 of the mechanical press implemented in connection with the hydraulic overload prevention device 34 shown in FIGS. 1 and 2, and FIG.
It is sectional drawing seen from IV. A moving body 71 constituting the piston 30 that moves up and down is arranged in the housing 70. A crank 73a is formed on a drive shaft 73 driven around a horizontal rotation axis, and an eccentric member 72 is rotatably fitted into the crank 73a to form a crank mechanism. The piston 31 is fixed to the eccentric member 72.
One type of punch is fixed to the lower piston 30 of the eccentric member 72, and the other type of die is fixed to the support 69 at the lower part of the housing 70. Thus, shearing such as punching or drawing. Plastic deformation press working such as forming is performed.
【００２７】移動体７１と偏心部材７２との相互間で、
駆動軸７３の軸線に垂直である図３の上下方向の相対的
な変位量を調整するために、偏心部材７２の上部にはね
じ棒７７が固定される。ねじ棒７７の上端部にはスプラ
イン軸７９が立設される。スプライン軸７９にはウォー
ムホイル８０が嵌合し、このウォームホイル８０にはウ
ォーム８２が螺合する。ウォーム８２を油圧モータ８１
によって回転駆動することによってウォームホイル８０
が回転され、偏心部材７２が図３の上下方向に変位して
調整することができる。ナット７８は偏心部材７１に固
定される。Between the moving body 71 and the eccentric member 72,
A screw rod 77 is fixed to the upper part of the eccentric member 72 in order to adjust the relative displacement in the vertical direction in FIG. 3 which is perpendicular to the axis of the drive shaft 73. A spline shaft 79 is provided upright at the upper end of the screw rod 77. A worm wheel 80 is fitted to the spline shaft 79, and a worm 82 is screwed to the worm wheel 80. Worm 82 is connected to hydraulic motor 81
Driven by the worm wheel 80
Is rotated, and the eccentric member 72 can be adjusted by being displaced in the vertical direction in FIG. The nut 78 is fixed to the eccentric member 71.
【００２８】上下動するピストン３０は、上述のクラン
ク機構だけでなくカム機構およびその他の手段によって
変位される構成であってもよい。The vertically moving piston 30 may be displaced not only by the above-described crank mechanism but also by a cam mechanism and other means.
【００２９】図５は、本発明の実施の他の形態において
用いられるバランスピストン形減圧弁８５の断面図であ
る。この減圧弁８５を、前述の実施の一形態における減
圧弁６１の代わりに用いることによって、リリーフ弁６
２を省略することができる。ケーシング８６にはバラン
スピストン８７が変位可能に油路８８，８９間に設けら
れている。管路５４、したがって油路８９の圧力が上昇
すると、その２次圧によって絞り９０を介してポペット
９１が弁座９２からばね９３のばね力に抗して開き、圧
油が油路９４を経てタンクに導かれる。絞り９０から２
次室９５へは、絞り９０の前後の圧力差によって、バラ
ンスピストン８７を２次室９５側（図５の上方）へ動か
す。これによって余分な圧油がタンクに戻される。ポペ
ット９１を弁座９２に押付けるばね９３のばね力はねじ
手段９６によって手動で調整することができる。バラン
スピストン８７はばね９７によってバランスピストン８
７が閉じる方向にばね力を与える。FIG. 5 is a sectional view of a balance piston type pressure reducing valve 85 used in another embodiment of the present invention. By using the pressure reducing valve 85 instead of the pressure reducing valve 61 in the above-described embodiment, the relief valve 6
2 can be omitted. In the casing 86, a balance piston 87 is displaceably provided between the oil passages 88 and 89. When the pressure in the pipe 54 and therefore the oil passage 89 increases, the poppet 91 opens from the valve seat 92 against the spring force of the spring 93 through the throttle 90 due to the secondary pressure, and the pressure oil passes through the oil passage 94. Guided to the tank. Aperture 90-2
The balance piston 87 is moved toward the secondary chamber 95 toward the secondary chamber 95 (upward in FIG. 5) by the pressure difference before and after the throttle 90. This returns excess pressurized oil to the tank. The spring force of the spring 93 pressing the poppet 91 against the valve seat 92 can be manually adjusted by the screw means 96. The balance piston 87 is moved by the spring 97 to the balance piston 8.
7 applies a spring force in the closing direction.
【００３０】ねじ手段９６に代えて、電磁ソレノイドを
用い、この電磁ソレノイドの励磁電流によって、ばね９
３によるポペット弁９１に作用するばね力、したがって
設定圧力を調整するようにして遠隔制御のための電磁比
例バランスピストン形減圧弁を構成してもよい。An electromagnetic solenoid is used in place of the screw means 96, and the spring 9 is driven by the exciting current of the electromagnetic solenoid.
By adjusting the spring force acting on the poppet valve 91 according to 3 and therefore the set pressure, an electromagnetic proportional balance piston type pressure reducing valve for remote control may be configured.
【００３１】本発明の実施のさらに他の形態では、図１
の実施の形態において、リリーフ弁６２の設定圧を、電
磁力によって調整して電磁比例リリーフ弁を構成して遠
隔制御を行うようにしてもよい。In still another embodiment of the present invention, FIG.
In this embodiment, the set pressure of the relief valve 62 may be adjusted by an electromagnetic force to form an electromagnetic proportional relief valve to perform remote control.
【００３２】図６は、本発明の実施のさらに他の形態に
おいて用いられる電磁比例パイロット減圧弁９７の断面
図である。この減圧弁９７は、前述の図１に示される実
施の一形態における減圧弁６１の代わりに用いられ、こ
のときリリーフ弁６２は省略される。図６に示される電
磁比例パイロット減圧弁９７の油圧記号は、たとえば図
７のように示すことができる。弁本体１０１にはスリー
ブ１０２がその軸線方向に変位可能にばね１０３によっ
てばね力が与えられる。スリーブ１０２内にはスプール
１０４がその軸線方向に相互に変位可能に収納される。
スプール１０４は、ばね１０５によってばね力が与えら
れる。FIG. 6 is a sectional view of an electromagnetic proportional pilot pressure reducing valve 97 used in still another embodiment of the present invention. This pressure reducing valve 97 is used in place of the pressure reducing valve 61 in the embodiment shown in FIG. 1 described above, and at this time, the relief valve 62 is omitted. The hydraulic pressure symbol of the electromagnetic proportional pilot pressure reducing valve 97 shown in FIG. 6 can be shown, for example, as shown in FIG. A spring 102 is applied to the valve body 101 by a spring 103 so that the sleeve 102 can be displaced in the axial direction. A spool 104 is accommodated in the sleeve 102 so as to be mutually displaceable in the axial direction.
The spool 104 is provided with a spring force by a spring 105.
【００３３】このスプール１０４は、電磁プランジャ１
０６のプランジャ１０７によってばね１０５のばね力に
抗して変位可能である。電磁プランジャ１０６では、プ
ランジャ１０７を囲んでソレノイド１０８が形成され、
このソレノイド１０８に供給される励磁電流を調整する
ことによって、プランジャ１０７の軸線方向の位置、し
たがってスプール１０４の位置を調整することができ
る。ソレノイド１０８の直流励磁電流を調整し、ばね１
０５のばね力に抗してスプール１０４のランド１０９を
変位することによって、管路５４，９８に接続される油
路１１０，１１２に連通するスプール１０２との間の流
路断面積を調整して、管路５４の２次圧を励磁電流に対
応した値に連続的に調整することができる。管路５４の
油圧が上昇するとリーブ１０２が図６の右方に変位して
流路断面積が大きくなって、余分な圧油がタンクに戻さ
れてリリーフ機能が達成される。The spool 104 is provided with the electromagnetic plunger 1
The plunger 107 is displaceable against the spring force of the spring 105. In the electromagnetic plunger 106, a solenoid 108 is formed around the plunger 107,
By adjusting the exciting current supplied to the solenoid 108, the position of the plunger 107 in the axial direction, that is, the position of the spool 104 can be adjusted. The DC excitation current of the solenoid 108 is adjusted, and the spring 1
By displacing the land 109 of the spool 104 against the spring force of 05, the cross-sectional area of the flow passage between the spool 102 and the oil passages 110 and 112 connected to the conduits 54 and 98 is adjusted. , The secondary pressure of the conduit 54 can be continuously adjusted to a value corresponding to the exciting current. When the oil pressure in the conduit 54 rises, the leave 102 is displaced rightward in FIG. 6 to increase the cross-sectional area of the flow path, and excess pressure oil is returned to the tank to achieve the relief function.
【００３４】図８は、本発明の実施のさらに他の形態に
おいて用いられる油圧回路１１４の油圧回路図である。
この油圧回路１１４は、前述の図１に示される実施の一
形態において減圧弁６１とリリーフ弁６１との組合わせ
の代わりに用いられる。弁箱１１５内には図８の上下に
変位可能に弁体１１６がばね１１７によって閉弁方向に
ばね力が与えられ、油圧源６０から管路９８を経て圧油
が供給され、その２次圧は油圧室１１８から管路５４に
供給される。管路５４には絞り１１９を介してパイロッ
ト管路１２０が接続され、弁本体１１５のばね１１７の
収納された油圧室１２１にもまた管路１２２を介して接
続される。管路１２０，１２２は、電磁比例リリーフ弁
１２３に接続される。管路５４に過負荷時の大きな圧力
が作用したとき、リリーフ弁１２３が開き、これによっ
て油圧室１２１の圧油がタンクに逃がされ、これに応じ
て弁体１１６がばね１１７のばね力に抗して図８の上方
に変位して油圧源６０から管路９８を経て油圧室１１８
に供給される圧油が絞られる。FIG. 8 is a hydraulic circuit diagram of a hydraulic circuit 114 used in still another embodiment of the present invention.
This hydraulic circuit 114 is used in place of the combination of the pressure reducing valve 61 and the relief valve 61 in the embodiment shown in FIG. In the valve box 115, a valve body 116 is displaced up and down in FIG. 8 by a spring 117 to apply a spring force in a valve closing direction, and hydraulic oil is supplied from a hydraulic source 60 via a pipe 98, and the secondary pressure is Is supplied from the hydraulic chamber 118 to the pipeline 54. A pilot pipe 120 is connected to the pipe 54 via a throttle 119, and also connected to a hydraulic chamber 121 of the valve body 115 in which a spring 117 is housed via a pipe 122. The pipes 120 and 122 are connected to an electromagnetic proportional relief valve 123. When a large pressure at the time of overload acts on the conduit 54, the relief valve 123 opens, whereby the pressure oil in the hydraulic chamber 121 is released to the tank, and the valve body 116 responds to the spring force of the spring 117. 8 is displaced upward in FIG.
The pressure oil supplied to the tank is throttled.
【００３５】リリーフ弁６２、ポペット弁９１およびリ
リーフ弁１２３は、常時開かれて油圧源６０からの圧油
をタンクに戻すように構成してもよい。The relief valve 62, the poppet valve 91 and the relief valve 123 may be configured to be always opened to return the pressure oil from the hydraulic pressure source 60 to the tank.
【００３６】図９は、本発明の実施のさらに他の形態の
ケーシング３５と弁体３９とを示す断面図である。この
実施の一形態では、プレス装置本体２９における管路３
３は、第２油圧室４８に接続される。第３油圧室４９は
管路５０を経てタンクに接続される。管路３３または第
２油圧室４８には、油圧源５１から逆止弁５２を経て圧
油が供給される。その他の構成は前述の実施例と同様で
ある。このような図９に示される構成もまた、本発明の
精神に含まれる。FIG. 9 is a sectional view showing a casing 35 and a valve body 39 according to still another embodiment of the present invention. In this embodiment, the pipe 3
3 is connected to the second hydraulic chamber 48. The third hydraulic chamber 49 is connected to the tank via a pipe 50. Pressure oil is supplied to the pipeline 33 or the second hydraulic chamber 48 from a hydraulic source 51 via a check valve 52. Other configurations are the same as those of the above-described embodiment. Such a configuration shown in FIG. 9 is also included in the spirit of the present invention.
【００３７】[0037]
【発明の効果】以上のように本発明によれば、弁体の小
径部側に、過大な油圧の発生を防止すべき油圧回路が接
続され、その弁体の大径部側の第１油圧室にアキュムレ
ータが接続されるとともに、油圧源から減圧弁を経て油
圧が供給されて第１油圧室の圧力が常に一定の圧力に調
圧され、その第１油圧室の圧油は、リリーフ弁を介し
て、または減圧弁に備えられているリリーフ機能を介し
て、余分な圧油がタンクに戻されるので、アキュムレー
タを小形化することができ、また弁体の質量を小さくす
ることができ、設備を小形化し、コストを低減すること
ができるようになる。As described above, according to the present invention, the hydraulic circuit for preventing the generation of excessive hydraulic pressure is connected to the small diameter side of the valve body, and the first hydraulic pressure on the large diameter side of the valve body is connected. While the accumulator is connected to the chamber, the hydraulic pressure is supplied from the hydraulic pressure source via the pressure reducing valve, and the pressure in the first hydraulic chamber is constantly adjusted to a constant pressure. The excess pressurized oil is returned to the tank via the or a relief function provided in the pressure reducing valve, so that the accumulator can be downsized, and the mass of the valve body can be reduced, Can be reduced in size and cost can be reduced.
【００３８】また本発明によれば、弁体を小形化するこ
とができるので、応答性を向上することができるように
なる。したがって過大な油圧の発生を防止すべき油圧回
路の過大な圧力上昇を小さく抑えることができるように
なる。Further, according to the present invention, since the valve body can be downsized, responsiveness can be improved. Therefore, it is possible to suppress an excessive increase in pressure of the hydraulic circuit in which generation of excessive hydraulic pressure should be prevented.
【００３９】さらに本発明によれば、リリーフ弁および
減圧弁の少なくともいずれか一方を電磁比例形とし、遠
隔制御によって過負荷防止特性を高精度で調整すること
ができる。Further, according to the present invention, at least one of the relief valve and the pressure reducing valve is of an electromagnetic proportional type, and the overload prevention characteristic can be adjusted with high precision by remote control.
【００４０】このように本発明によれば、第１油圧室の
圧油の低いパイロット圧力で、前記油圧回路の高い圧力
を制御することができるようになり、しかもその油圧回
路の大流量を制御することができるようになる。As described above, according to the present invention, the high pressure of the hydraulic circuit can be controlled by the low pilot pressure of the hydraulic oil in the first hydraulic chamber, and the large flow rate of the hydraulic circuit can be controlled. Will be able to
【図１】本発明の実施の一形態の油圧回路図である。FIG. 1 is a hydraulic circuit diagram of one embodiment of the present invention.
【図２】図１に示されるケーシング３５と弁体３９とア
キュムレータ５３との具体的な構成を示す断面図であ
る。FIG. 2 is a sectional view showing a specific configuration of a casing 35, a valve body 39, and an accumulator 53 shown in FIG.
【図３】図１および図２に示される油圧過負荷防止装置
３４に関連して実施される機械プレス装置本体６３の縦
断面図である。FIG. 3 is a longitudinal sectional view of a main body 63 of the mechanical press implemented in connection with the hydraulic overload prevention device 34 shown in FIGS. 1 and 2;
【図４】図３の切断面線ＩＶ−ＩＶから見た断面図であ
る。FIG. 4 is a cross-sectional view taken along the line IV-IV of FIG. 3;
【図５】本発明の実施の他の形態において用いられるバ
ランスピストン形減圧弁８５の断面図である。FIG. 5 is a cross-sectional view of a balance piston type pressure reducing valve 85 used in another embodiment of the present invention.
【図６】本発明の実施のさらに他の形態において用いら
れる電磁比例パイロット減圧弁９７の断面図である。FIG. 6 is a sectional view of an electromagnetic proportional pilot pressure reducing valve 97 used in still another embodiment of the present invention.
【図７】図６の減圧弁９７の油圧回路図である。FIG. 7 is a hydraulic circuit diagram of the pressure reducing valve 97 of FIG.
【図８】本発明の実施のさらに他の形態において用いら
れる油圧回路１１４の油圧回路図である。FIG. 8 is a hydraulic circuit diagram of a hydraulic circuit 114 used in still another embodiment of the present invention.
【図９】本発明の実施のさらに他の形態のケーシング３
５と弁体３９とを示す断面図である。FIG. 9 shows a casing 3 according to still another embodiment of the present invention.
5 is a cross-sectional view showing a valve body 5 and a valve body 39. FIG.
【図１０】先行技術の簡略化された図である。FIG. 10 is a simplified diagram of the prior art.
【図１１】他の先行技術の簡略化された図である。FIG. 11 is a simplified diagram of another prior art.
【図１２】さらに他の先行技術の簡略化された図であ
る。FIG. 12 is a simplified diagram of yet another prior art.
【図１３】他の先行技術の簡略化された図である。FIG. 13 is a simplified diagram of another prior art.
３４ 油圧過負荷防止装置 ３５ ケーシング ３６，３７ 部分 ３８ 弁座 ３９ 弁体 ４０ 大径部 ４１ 小径部 ４２ 軸線 ４３ 第１受圧面 ４４ 第２受圧面 ４５ 第３受圧面 ４７ 第１油圧室 ４８ 第２油圧室 ４９ 第３油圧室 ５０，５４ 管路 ５１，６０ 油圧源 ５２ 逆止弁 ５３ アキュムレータ ５５ 圧油室 ５６ ガス室 ５７ 部材 ５８ 容器 ６１，８５ 減圧弁 ６２ リリーフ弁 ６３ 機械プレス装置本体 ８６ ケーシング ８７ バランスピストン ８８，８９，９４ 油路 ９０ 絞り ９１ ポペット ９３ ばね ９５ ２次室 34 Hydraulic overload prevention device 35 Casing 36, 37 part 38 Valve seat 39 Valve element 40 Large diameter portion 41 Small diameter portion 42 Axis 43 First pressure receiving surface 44 Second pressure receiving surface 45 Third pressure receiving surface 47 First hydraulic chamber 48 Second Hydraulic chamber 49 Third hydraulic chamber 50, 54 Pipe line 51, 60 Hydraulic source 52 Check valve 53 Accumulator 55 Pressure oil chamber 56 Gas chamber 57 Member 58 Container 61, 85 Pressure reducing valve 62 Relief valve 63 Machine press unit main body 86 Casing 87 Balance piston 88, 89, 94 Oil passage 90 Throttle 91 Poppet 93 Spring 95 Secondary chamber
Claims (7)
方端に第１受圧面を有する大径部と、この大径部に弁体
の軸線方向に連なりかつ弁体の軸線方向他方端に第１受
圧面よりも小さい第２受圧面を有する小径部とを備え、
第１受圧面と第２受圧面との間で弁体の軸線方向に第２
受圧面と同じ側で第１受圧面よりも小さい第３受圧面を
有する弁体と、 （ｂ）弁体を収納し、大径部を案内し、かつ小径部が着
座する弁座を有し、第１受圧面が臨む第１油圧室と、弁
体が弁座に着座している状態で第２受圧面が臨む第２油
圧室と、第３受圧面が臨み弁座から小径部が離間して第
２油圧室に連なる第３油圧室とを形成し、過大な油圧の
発生を防止すべき油圧回路が、第２または第３油圧室の
いずれか一方に接続され、第２または第３油圧室のいず
れか他方にタンクが接続されるケーシングと、 （ｃ）第１油圧室に接続されるアキュムレータと、 （ｄ）圧油を供給する油圧源と、 （ｅ）第１油圧室と油圧源との間に介在され、第１油圧
室側の２次圧を予め定める第１の値に調圧する減圧弁
と、 （ｆ）第１油圧室の油路に接続され、第１の値未満の予
め定める第２の値に設定圧が定められて余分の圧油をタ
ンクに戻すリリーフ弁とを含むことを特徴とする油圧過
負荷防止装置。(A) A valve element, a large-diameter portion having a first pressure-receiving surface at one end in the axial direction of the valve element, and an axial line of the valve element connected to the large-diameter portion in the axial direction of the valve element. A small-diameter portion having a second pressure-receiving surface smaller than the first pressure-receiving surface at the other end in the direction,
In the axial direction of the valve body between the first pressure receiving surface and the second pressure receiving surface in the second direction,
A valve body having a third pressure-receiving surface smaller than the first pressure-receiving surface on the same side as the pressure-receiving surface; and (b) a valve seat that houses the valve body, guides the large-diameter portion, and seats the small-diameter portion. A first hydraulic chamber facing the first pressure receiving surface, a second hydraulic chamber facing the second pressure receiving surface while the valve body is seated on the valve seat, and a small diameter portion facing the third pressure receiving surface facing the valve seat. And a third hydraulic chamber connected to the second hydraulic chamber, and a hydraulic circuit for preventing generation of excessive hydraulic pressure is connected to one of the second and third hydraulic chambers. (C) an accumulator connected to the first hydraulic chamber, (d) a hydraulic source for supplying pressure oil, (e) a first hydraulic chamber and hydraulic pressure A pressure reducing valve interposed between the pressure source and the pressure source to adjust the secondary pressure on the first hydraulic chamber side to a predetermined first value; and (f) connected to an oil passage of the first hydraulic chamber. Is the hydraulic overload protection device which comprises a relief valve to return the first extra pressure oil set pressure to the second value is defined the predetermined of less than a value in the tank.
方端に第１受圧面を有する大径部と、この大径部に弁体
の軸線方向に連なりかつ弁体の軸線方向他方端に第１受
圧面よりも小さい第２受圧面を有する小径部とを備え、
第１受圧面と第２受圧面との間で弁体の軸線方向に第２
受圧面と同じ側で第１受圧面よりも小さい第３受圧面を
有する弁体と、 （ｂ）弁体を収納し、大径部を案内し、かつ小径部が着
座する弁座を有し、第１受圧面が臨む第１油圧室と、弁
体が弁座に着座している状態で第２受圧面が臨む第２油
圧室と、第３受圧面が臨み弁座から小径部が離間して第
２油圧室に連なる第３油圧室とを形成し、過大な油圧の
発生を防止すべき油圧回路が、第２または第３油圧室の
いずれか一方に接続され、第２または第３油圧室のいず
れか他方にタンクが接続されるケーシングと、 （ｃ）第１油圧室に接続されるアキュムレータと、 （ｄ）圧油を供給する油圧源と、 （ｅ）第１油圧室と油圧源との間に介在され、第１油圧
室側の２次圧を予め定める値に調圧し、しかも第１油圧
室側の余分の圧油をタンクに戻す減圧弁とを含むことを
特徴とする油圧過負荷防止装置。2. A valve body, a large diameter portion having a first pressure receiving surface at one end in the axial direction of the valve body, and an axial line of the valve body connected to the large diameter portion in the axial direction of the valve body. A small-diameter portion having a second pressure-receiving surface smaller than the first pressure-receiving surface at the other end in the direction,
In the axial direction of the valve body between the first pressure receiving surface and the second pressure receiving surface in the second direction,
A valve body having a third pressure-receiving surface smaller than the first pressure-receiving surface on the same side as the pressure-receiving surface; and (b) a valve seat that houses the valve body, guides the large-diameter portion, and seats the small-diameter portion. A first hydraulic chamber facing the first pressure receiving surface, a second hydraulic chamber facing the second pressure receiving surface while the valve body is seated on the valve seat, and a small diameter portion facing the third pressure receiving surface facing the valve seat. And a third hydraulic chamber connected to the second hydraulic chamber, and a hydraulic circuit for preventing generation of excessive hydraulic pressure is connected to one of the second and third hydraulic chambers. (C) an accumulator connected to the first hydraulic chamber, (d) a hydraulic source for supplying pressure oil, (e) a first hydraulic chamber and hydraulic pressure Between the pressure source and the pressure source to regulate the secondary pressure on the first hydraulic chamber side to a predetermined value, and to reduce excess hydraulic oil on the first hydraulic chamber side to the tank. A hydraulic overload prevention device comprising a pressure valve.
ることを特徴とする請求項１記載の油圧過負荷防止装
置。3. The hydraulic overload prevention device according to claim 1, wherein the relief valve is an electromagnetic proportional relief valve.
特徴とする請求項２記載の油圧過負荷防止装置。4. The hydraulic overload prevention device according to claim 2, wherein the pressure reducing valve is an electromagnetic proportional pressure reducing valve.
仕切る部材が、剛性容器内で変形可能または移動可能で
ある構成を有し、その圧油室が第１油圧室に接続される
ことを特徴とする請求項１〜４のうちの１つに記載の油
圧過負荷防止装置。5. The accumulator has a configuration in which a member that separates a pressure oil chamber and a gas chamber is deformable or movable in a rigid container, and the pressure oil chamber is connected to the first hydraulic chamber. The hydraulic overload prevention device according to any one of claims 1 to 4, wherein:
復駆動源に連結し、前記一方の型と他方の型との間で被
加工物をプレス加工するプレス装置本体と、 （ｂ）油圧過負荷防止装置であって、（ｂ１）弁体であ
って、弁体の軸線方向一方端に第１受圧面を有する大径
部と、この大径部に弁体の軸線方向に連なりかつ弁体の
軸線方向他方端に第１受圧面よりも小さい第２受圧面を
有する小径部とを備え、第１受圧面と第２受圧面との間
で弁体の軸線方向に第２受圧面と同じ側で第１受圧面よ
りも小さい第３受圧面を有する弁体と、（ｂ２）弁体を
収納し、大径部を案内し、かつ小径部が着座する弁座を
有し、第１受圧面が臨む第１油圧室と、弁体が弁座に着
座している状態で第２受圧面が臨む第２油圧室と、第３
受圧面が臨み弁座から小径部が離間して第２油圧室に連
なる第３油圧室とを形成し、過大な油圧の発生を防止す
べき油圧回路が、第２または第３油圧室のいずれか一方
に接続され、第２または第３油圧室のいずれか他方にタ
ンクが接続されるケーシングと、（ｂ３）第１油圧室に
接続されるアキュムレータと、（ｂ４）圧油を供給する
油圧源と、（ｂ５）第１油圧室と油圧源との間に介在さ
れ、第１油圧室側の２次圧を予め定める第１の値に調圧
する減圧弁と、（ｂ６）第１油圧室の油路に接続され、
第１の値未満の予め定める第２の値に設定圧が定められ
て余分の圧油をタンクに戻すリリーフ弁とを備える油圧
過負荷防止装置とを含むプレス装置。6. A press machine body for connecting one of the dies to a reciprocating drive source via a cylinder and pressing a workpiece between the one and the other dies. (B) a hydraulic pressure overload prevention device, (b1) a valve body, a large diameter portion having a first pressure receiving surface at one end in the axial direction of the valve body, and a large diameter portion connected to the large diameter portion in the axial direction of the valve body; A small-diameter portion having a second pressure-receiving surface smaller than the first pressure-receiving surface at the other end in the axial direction of the valve body, and a second pressure-receiving portion between the first pressure-receiving surface and the second pressure-receiving surface in the axial direction of the valve body. A valve body having a third pressure receiving surface smaller than the first pressure receiving surface on the same side as the surface, and (b2) a valve seat that houses the valve body, guides the large diameter portion, and seats the small diameter portion, A first hydraulic chamber facing the first pressure receiving surface, a second hydraulic chamber facing the second pressure receiving surface in a state where the valve element is seated on the valve seat,
A third hydraulic chamber which faces the pressure receiving surface and has a small-diameter portion separated from the valve seat to form a third hydraulic chamber connected to the second hydraulic chamber, and a hydraulic circuit for preventing generation of excessive hydraulic pressure is provided in either the second or third hydraulic chamber. A casing connected to one of the second and third hydraulic chambers, and a tank connected to the other of the second and third hydraulic chambers; (b3) an accumulator connected to the first hydraulic chamber; and (b4) a hydraulic source for supplying pressure oil. (B5) a pressure reducing valve interposed between the first hydraulic chamber and the hydraulic pressure source to regulate the secondary pressure on the first hydraulic chamber side to a predetermined first value; and (b6) a pressure reducing valve for the first hydraulic chamber. Connected to the oilway,
A hydraulic pressure overload prevention device comprising: a relief valve having a set pressure set to a predetermined second value less than the first value and returning excess pressure oil to the tank.
往復駆動源に連結し、前記一方の金型と他方の金型との
間で被加工物をプレス加工するプレス装置本体と、 （ｂ）油圧過負荷防止装置であって、（ｂ１）弁体であ
って、弁体の軸線方向一方端に第１受圧面を有する大径
部と、この大径部に弁体の軸線方向に連なりかつ弁体の
軸線方向他方端に第１受圧面よりも小さい第２受圧面を
有する小径部とを備え、第１受圧面と第２受圧面との間
で弁体の軸線方向に第２受圧面と同じ側で第１受圧面よ
りも小さい第３受圧面を有する弁体と、（ｂ２）弁体を
収納し、大径部を案内し、かつ小径部が着座する弁座を
有し、第１受圧面が臨む第１油圧室と、弁体が弁座に着
座している状態で第２受圧面が臨む第２油圧室と、第３
受圧面が臨み弁座から小径部が離間して第２油圧室に連
なる第３油圧室とを形成し、過大な油圧の発生を防止す
べき油圧回路が、第２または第３油圧室のいずれか一方
に接続され、第２または第３油圧室のいずれか他方にタ
ンクが接続されるケーシングと、（ｂ３）第１油圧室に
接続されるアキュムレータと、（ｂ４）圧油を供給する
油圧源と、（ｂ５）第１油圧室と油圧源との間に介在さ
れ、第１油圧室側の２次圧を予め定める値に調圧し、し
かも第１油圧室側の余分の圧油をタンクに戻す減圧弁と
を備える油圧過負荷防止装置とを含むことを特徴とする
プレス装置。7. A press machine body for connecting one of the dies to a reciprocating drive source via a cylinder and pressing a workpiece between the one of the dies and the other of the dies. (B) a hydraulic overload prevention device, (b1) a valve body having a large-diameter portion having a first pressure-receiving surface at one end in the axial direction of the valve body; A small-diameter portion having a second pressure-receiving surface smaller than the first pressure-receiving surface at the other end in the axial direction of the valve body in the axial direction of the valve-body, between the first pressure-receiving surface and the second pressure-receiving surface. A valve body having a third pressure-receiving surface smaller than the first pressure-receiving surface on the same side as the second pressure-receiving surface; and (b2) a valve seat that houses the valve body, guides the large-diameter portion, and seats the small-diameter portion. A first hydraulic chamber facing the first pressure receiving surface, a second hydraulic chamber facing the second pressure receiving surface in a state where the valve body is seated on the valve seat,
A third hydraulic chamber which faces the pressure receiving surface and has a small-diameter portion separated from the valve seat to form a third hydraulic chamber connected to the second hydraulic chamber, and a hydraulic circuit for preventing generation of excessive hydraulic pressure is provided in either the second or third hydraulic chamber. A casing connected to one of the second and third hydraulic chambers, and a tank connected to the other of the second and third hydraulic chambers; (b3) an accumulator connected to the first hydraulic chamber; and (b4) a hydraulic source for supplying pressure oil. And (b5) interposed between the first hydraulic chamber and the hydraulic pressure source, regulates the secondary pressure on the first hydraulic chamber side to a predetermined value, and supplies excess pressure oil on the first hydraulic chamber side to the tank. A press device comprising: a hydraulic overload prevention device including a return pressure reducing valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8077092A JP2723882B2 (en) | 1996-03-29 | 1996-03-29 | Hydraulic overload prevention device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8077092A JP2723882B2 (en) | 1996-03-29 | 1996-03-29 | Hydraulic overload prevention device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09267199A JPH09267199A (en) | 1997-10-14 |
| JP2723882B2 true JP2723882B2 (en) | 1998-03-09 |
Family
ID=13624148
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8077092A Expired - Fee Related JP2723882B2 (en) | 1996-03-29 | 1996-03-29 | Hydraulic overload prevention device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2723882B2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6164147A (en) * | 1999-02-05 | 2000-12-26 | The Minster Machine Company | Adjustable link motion press |
| JP2010137318A (en) * | 2008-12-10 | 2010-06-24 | Niigata Machine Techno Co Ltd | Apparatus and method for adjusting pressure fluctuation of machine tool |
| CN104985861A (en) * | 2015-06-18 | 2015-10-21 | 合肥合锻机床股份有限公司 | Automatic regulating device for precision of hydraulic machine sliding block |
| KR102381039B1 (en) * | 2018-03-15 | 2022-03-31 | 두산공작기계(주) | Load reduction device for vertical axis of machine tool |
-
1996
- 1996-03-29 JP JP8077092A patent/JP2723882B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH09267199A (en) | 1997-10-14 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |