JP6077342B2

JP6077342B2 - Fluid pressure control device

Info

Publication number: JP6077342B2
Application number: JP2013045362A
Authority: JP
Inventors: 嶋田　佳幸; 佳幸嶋田
Original assignee: Eagle Industry Co Ltd
Current assignee: Eagle Industry Co Ltd
Priority date: 2013-03-07
Filing date: 2013-03-07
Publication date: 2017-02-08
Anticipated expiration: 2033-03-07
Also published as: JP2014173642A

Description

本発明は、流体圧制御装置に関する。 The present invention relates to a fluid pressure control device.

従来より、油圧被供給回路に高圧油を供給する油圧制御装置（流体圧制御装置）では、油圧ポンプを用いて増圧装置に圧油を供給する構成が知られている（特許文献１）。図１０は、従来例に係る油圧制御装置の油圧回路図である。図１０に示す油圧制御装置では、駆動機構１と油圧ポンプ２からなる油圧発生回路部から吐出された圧油が、逆止弁１２、管路５、電磁切換弁６を通って増圧装置７に供給され、増圧装置７で増圧された高圧油が、直接あるいはアキュムレータ８に溜められ、油圧被供給回路４に供給される。 2. Description of the Related Art Conventionally, a hydraulic control device (fluid pressure control device) that supplies high-pressure oil to a hydraulic supplied circuit has been known to supply pressure oil to a pressure booster using a hydraulic pump (Patent Document 1). FIG. 10 is a hydraulic circuit diagram of a conventional hydraulic control apparatus. In the hydraulic control apparatus shown in FIG. 10, the pressure oil discharged from the hydraulic pressure generating circuit unit including the drive mechanism 1 and the hydraulic pump 2 passes through the check valve 12, the pipe line 5, and the electromagnetic switching valve 6, and the pressure booster 7. The high pressure oil that has been supplied to the pressure booster 7 and stored in the accumulator 8 is supplied to the hydraulic supplied circuit 4.

特開２０１１−８５２２６号公報JP 2011-85226 A

増圧装置７に圧油を供給する油圧発生回路部は、駆動機構１や油圧ポンプ２の他に、サクションフィルタ１１、逆止弁１２、さらにはリリーフ弁２０や各油圧機器に接続する配管部品などの多くの部品が必要となり、その分の設置スペースが必要になるとともに回路が複雑となる。また、駆動機構１、油圧ポンプ２、リリーフ弁２０は各々が個々に作動するため、いわゆるエネルギーロスが発生する可能性があり、装置全体の動作効率が悪くなることが懸念される。 In addition to the drive mechanism 1 and the hydraulic pump 2, the hydraulic pressure generating circuit that supplies the pressure oil to the pressure booster 7 includes a suction filter 11, a check valve 12, a relief valve 20, and piping components connected to each hydraulic device. As a result, many parts such as the above are required, and the installation space for that part is required, and the circuit becomes complicated. Moreover, since each of the drive mechanism 1, the hydraulic pump 2, and the relief valve 20 operates individually, there is a possibility that so-called energy loss may occur, and there is a concern that the operation efficiency of the entire apparatus is deteriorated.

本発明の目的は、構成の簡素化及び動作効率の向上を図ることができる流体圧制御装置を提供することにある。 An object of the present invention is to provide a fluid pressure control device capable of simplifying the configuration and improving the operation efficiency.

上記目的を達成するために、本発明における流体圧制御装置は、
流体供給部から供給される流体を増圧して被供給回路に供給する流体圧制御装置であって、
コイルへの通電によって往復動部材を往復移動させることにより、前記流体供給部から供給された流体を増圧して吐出する電磁圧力変換装置と、
前記電磁圧力変換装置から吐出された流体の流体圧により動作し、前記流体供給部から供給された流体を増圧して吐出する増圧装置と、
を備え、
前記増圧装置は、シリンダと、該シリンダ内を往復動するピストンを有し、前記電磁圧力変換装置から吐出された流体の流体圧が負荷されて前記ピストンが前記シリンダ内を移動することで、供給された流体を増圧して吐出する構成となっており、
前記増圧装置において前記流体圧が負荷される流体室の最大容積は、前記電磁圧力変換装置において前記往復動部材が往復移動における一方向の１回の最大移動時に押し出す容積の整数倍であることを特徴とする。 In order to achieve the above object, a fluid pressure control device according to the present invention provides:
A fluid pressure control device for increasing the pressure of a fluid supplied from a fluid supply unit and supplying the pressure to a supplied circuit,
An electromagnetic pressure converter for increasing and discharging the fluid supplied from the fluid supply unit by reciprocating a reciprocating member by energizing the coil;
A pressure increasing device that operates by the fluid pressure of the fluid discharged from the electromagnetic pressure conversion device, and increases and discharges the fluid supplied from the fluid supply unit;
With
The pressure increasing device has a cylinder and a piston that reciprocates in the cylinder, and the piston moves when the fluid pressure of the fluid discharged from the electromagnetic pressure conversion device is loaded. It is configured to increase the pressure of the supplied fluid and discharge it.
Maximum volume of the fluid chamber in which the fluid pressure is loaded in the pressure increasing device, Ru integral multiple der of the volume in which the reciprocating member in the electromagnetic pressure transducer pushes upon maximum movement in one direction of one of the reciprocating It is characterized by that.

本発明によれば、電磁圧力変換装置における往復動部材の往復移動により発生する流体圧によって増圧装置を動作させる構成とすることにより、回路構成の簡素化を図ることができる。すなわち、電磁圧力変換装置は、コイルへの通電を制御することにより動作させることができるので、従来の油圧ポンプを用いた構成のように、サクションフィルタや逆止弁、リリーフ弁さらに各油圧機器に接続する配管部品などが不要となり、省スペース化を図ることができる。また、増圧装置への圧油の供給を電磁圧力変換装置の動作のみによって行う構成となるので、従来のようなエネルギーロスの発生を抑制することができる。 According to the present invention, the circuit configuration can be simplified by adopting a configuration in which the pressure increasing device is operated by the fluid pressure generated by the reciprocating movement of the reciprocating member in the electromagnetic pressure conversion device. In other words, the electromagnetic pressure conversion device can be operated by controlling the energization of the coil, so that the suction filter, the check valve, the relief valve, and each hydraulic device, as in the configuration using the conventional hydraulic pump. Piping parts to be connected are not necessary, and space can be saved. In addition, since the pressure oil is supplied to the pressure increasing device only by the operation of the electromagnetic pressure conversion device, the conventional energy loss can be suppressed.

これにより、電磁圧力変換装置が往復動部材の１回の移動により吐き出す流体の流量を無駄なく増圧装置の動作に利用することができ、増圧した流体の供給を効率的に行うことができる。 Thus, the flow rate of the fluid discharged by the electromagnetic pressure conversion device by one movement of the reciprocating member can be used for the operation of the pressure increasing device without waste, and the increased fluid can be supplied efficiently. .

前記増圧装置が吐出した流体の流体圧を蓄圧し、かつ蓄圧した流体圧を下流側に供給可能な蓄圧部を備えるとよい。 It is good to provide the pressure accumulation part which can accumulate the fluid pressure of the fluid which the said pressure booster discharged, and can supply the accumulated fluid pressure to the downstream.

これにより、増圧装置で繰り返し発生する高流体圧を蓄圧部で溜めることにより、定常的な高流体圧の供給が可能となる。 As a result, the high fluid pressure that is repeatedly generated by the pressure booster is accumulated in the pressure accumulator, so that a steady high fluid pressure can be supplied.

前記蓄圧部と、前記蓄圧部で蓄圧された流体圧の供給先と、の間に逆止弁を備えるとよい。 A check valve may be provided between the pressure accumulating unit and the supply destination of the fluid pressure accumulated in the pressure accumulating unit.

蓄圧部と高流体圧供給先との間に逆止弁を設けることで、逆止弁から流体圧供給先側と、逆止弁から蓄圧部側（上流側）とで系を分けることができる。これにより、流体圧供給先側が高圧仕様の場合でも蓄圧部側の各要素を高圧仕様にせずに高流体圧の供給が可能となる。 By providing a check valve between the pressure accumulating unit and the high fluid pressure supply destination, the system can be divided between the check valve and the fluid pressure supply side, and from the check valve to the pressure accumulating unit side (upstream side). . As a result, even when the fluid pressure supply side is a high pressure specification, it is possible to supply a high fluid pressure without making each element on the pressure accumulating unit side a high pressure specification.

本発明によれば、流体圧制御装置の構成の簡素化及び動作効率の向上を図ることができる。 According to the present invention, the configuration of the fluid pressure control device can be simplified and the operation efficiency can be improved.

本発明の実施例に係る流体圧制御装置の油圧回路図Hydraulic circuit diagram of fluid pressure control device according to an embodiment of the present invention 本発明の実施例における電磁圧力変換装置の模式的断面図Typical sectional drawing of the electromagnetic pressure converter in the Example of this invention 本発明の実施例における可動部材（往復動部材）の模式的断面図Typical sectional drawing of the movable member (reciprocating member) in the Example of this invention 可動部材のストロークと可動部材に働く力の関係を示す図The figure which shows the relationship of the force which acts on the stroke of a movable member, and a movable member コイルと電磁切換弁のＯＮ／ＯＦＦのタイミング図Coil and electromagnetic switching valve ON / OFF timing diagram 本発明の変形例に係る流体圧制御装置の油圧回路図Hydraulic circuit diagram of a fluid pressure control device according to a modification of the present invention 本発明の変形例における電磁圧力変換装置の模式的断面図Typical sectional drawing of the electromagnetic pressure converter in the modification of this invention 本発明の変形例における可動部材（往復動部材）の模式的断面図Typical sectional drawing of the movable member (reciprocating member) in the modification of this invention コイルと電磁切換弁のＯＮ／ＯＦＦのタイミング図Coil and electromagnetic switching valve ON / OFF timing diagram 従来例に係る流体圧制御装置の油圧回路図Hydraulic circuit diagram of fluid pressure control device according to conventional example

以下に図面を参照して、この発明を実施するための形態を、実施例に基づいて例示的に詳しく説明する。ただし、この実施例に記載されている構成部品の寸法、材質、形状、その相対配置などは、特に特定的な記載がない限りは、この発明の範囲をそれらのみに限定する趣旨のものではない。 DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention will be exemplarily described in detail with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention only to those unless otherwise specified. .

＜実施例＞
図１は、本発明の実施例に係る油圧制御装置（流体圧制御装置）の油圧回路図である。本実施例に係る油圧制御装置は、例えば、普通乗用車や、トラック、油圧ショベル、フォークリフト、クレーン、ごみ収集車、プレス機械等におけるブレーキ、ステアリング、トランスミッション等の油圧装置に適用可能である。なお、図１に示す油圧回路は、本発明
の流体圧制御装置の流体圧回路のあくまで１例であり、図１の構成に限定されるものではない。 <Example>
FIG. 1 is a hydraulic circuit diagram of a hydraulic control device (fluid pressure control device) according to an embodiment of the present invention. The hydraulic control apparatus according to the present embodiment can be applied to hydraulic apparatuses such as brakes, steerings, transmissions and the like in ordinary passenger cars, trucks, hydraulic excavators, forklifts, cranes, garbage trucks, press machines, and the like. The hydraulic circuit shown in FIG. 1 is merely an example of the fluid pressure circuit of the fluid pressure control device of the present invention, and is not limited to the configuration of FIG.

（油圧制御装置の構成）
図１に示すように、本実施例に係る油圧制御装置は、概略、増圧装置７と、アキュムレータ８と、電磁圧力変換装置３０と、を備え、タンク（流体供給部）１０から供給される作動油の油圧をタンク圧よりも高い油圧に変換して、油圧被供給回路４に供給するものである。 (Configuration of hydraulic control device)
As shown in FIG. 1, the hydraulic control apparatus according to the present embodiment generally includes a pressure intensifying device 7, an accumulator 8, and an electromagnetic pressure conversion device 30, and is supplied from a tank (fluid supply unit) 10. The hydraulic pressure of the hydraulic oil is converted to a hydraulic pressure higher than the tank pressure and supplied to the hydraulic pressure supplied circuit 4.

タンク１０から管路３３、逆止弁３４を介して電磁圧力変換装置３０に供給された作動油は、電磁圧力変換装置３０で増圧されて吐出され、逆止弁３５、管路３６、電磁切換弁３１を介して増圧装置７に供給される。電磁切換弁３１は、３ポート２位置型の電磁切換弁であり、不図示のコントローラからの電気信号を受け取ることにより切り換わる。同コントローラは、電磁圧力変換装置３０における可動部材（往復動部材）の往復動もコイルへの通電によって制御し、これと同期させて電磁切換弁３１の切換を制御する。 The hydraulic fluid supplied from the tank 10 to the electromagnetic pressure conversion device 30 through the pipe line 33 and the check valve 34 is increased in pressure by the electromagnetic pressure conversion apparatus 30 and discharged, and the check valve 35, the pipe line 36, and the electromagnetic pressure are discharged. It is supplied to the pressure booster 7 through the switching valve 31. The electromagnetic switching valve 31 is a three-port two-position electromagnetic switching valve, and is switched by receiving an electrical signal from a controller (not shown). The controller also controls reciprocation of a movable member (reciprocating member) in the electromagnetic pressure conversion device 30 by energizing the coil, and controls switching of the electromagnetic switching valve 31 in synchronization with this.

タンク１０から管路１６、逆止弁１７を介して増圧装置７に供給された作動油（低圧油）は、増圧装置７で増圧されて吐出される。増圧装置７は、電磁圧力変換装置３０から供給される油圧によって動作する。詳細は後述するが、不図示のコントローラが電磁圧力変換装置３０のコイルの励磁、消磁を繰り返すことで、増圧装置７のピストンが往復動する。増圧装置７から吐出された高圧の作動油は、逆止弁１４、管路１５を介して、アキュムレータ（蓄圧部）８に一旦蓄圧されてから、あるいは直接、電磁切換弁９、逆止弁１８、管路１９を介して油圧被供給回路４に供給される。 The hydraulic oil (low pressure oil) supplied from the tank 10 to the pressure booster 7 through the pipe line 16 and the check valve 17 is increased in pressure by the pressure booster 7 and discharged. The pressure booster 7 is operated by the hydraulic pressure supplied from the electromagnetic pressure conversion device 30. Although details will be described later, a piston (not shown) repeats excitation and demagnetization of the coil of the electromagnetic pressure conversion device 30 so that the piston of the pressure increase device 7 reciprocates. The high-pressure hydraulic oil discharged from the pressure booster 7 is once accumulated in the accumulator (pressure accumulating portion) 8 via the check valve 14 and the pipe 15 or directly, or directly, the electromagnetic switching valve 9 and the check valve. 18, and supplied to the hydraulic supplied circuit 4 via the pipe line 19.

電磁切換弁９は、いわゆるノーマルクローズ型の２ポート２位置型の電磁切換弁であり、不図示のコントローラから電気信号を受け取ることにより切り換わる。電磁切換弁９が切り換わることにより、アキュムレータ８に蓄圧された圧油、あるいは増圧装置７から吐出された圧油が、逆止弁１８を介して油圧被供給回路４に供給される。ここで、アキュムレータ８と油圧被供給回路４との間に逆止弁１８を設けることで、逆止弁１８から油圧被供給回路４側と、逆止弁１８からアキュムレータ８側（上流側）とで系を分けることができる。したがって、油圧被供給回路４側が高圧仕様の場合でもアキュムレータ８側の各要素を高流体圧の供給先への回生に必要な最小限の圧力仕様にすることにより不必要な高圧仕様にせずに高圧流体の供給が可能となる。 The electromagnetic switching valve 9 is a so-called normally closed two-port two-position electromagnetic switching valve, and is switched by receiving an electrical signal from a controller (not shown). When the electromagnetic switching valve 9 is switched, the pressure oil accumulated in the accumulator 8 or the pressure oil discharged from the pressure increasing device 7 is supplied to the hydraulic supplied circuit 4 via the check valve 18. Here, by providing a check valve 18 between the accumulator 8 and the hydraulic supplied circuit 4, the check valve 18 is connected to the hydraulic supplied circuit 4 side, and the check valve 18 is connected to the accumulator 8 side (upstream side). You can divide the system. Therefore, even if the hydraulic supplied circuit 4 side has a high pressure specification, each element on the accumulator 8 side has a minimum pressure specification necessary for regeneration to a high fluid pressure supply destination, so that the high pressure specification is not required. Fluid can be supplied.

なお、増圧装置７によって増圧された作動油のうち、アキュムレータ８の容量が許容容量に達してアキュムレータ８に蓄圧されない余剰油は、管路１５から分岐する管路２３、リリーフ弁２４、管路２５を介してタンク１０に排出（回収）される。 Of the hydraulic oil that has been boosted by the pressure booster 7, surplus oil that does not accumulate in the accumulator 8 due to the capacity of the accumulator 8 reaching the allowable capacity is a pipe 23 that branches off from the pipe 15, a relief valve 24, a pipe It is discharged (collected) to the tank 10 via the path 25.

（増圧装置）
増圧装置７は、ケース７−３内にピストン７−５が内封されており、ケース内を摺動する。ピストン７−５は、大径部と小径部が軸方向に並んだ構成を有しており、所謂、パスカルの定理により、大径部が摺動する油室７−２内の負荷圧力により、その断面積の比の割合で、小径部が摺動する油室７−４内の圧力が増圧されるようになっている。 (Pressure booster)
The pressure booster 7 has a piston 7-5 enclosed in a case 7-3, and slides in the case. The piston 7-5 has a configuration in which a large diameter portion and a small diameter portion are arranged in the axial direction. According to the so-called Pascal's theorem, due to the load pressure in the oil chamber 7-2 in which the large diameter portion slides, The pressure in the oil chamber 7-4 where the small diameter portion slides is increased at a ratio of the ratio of the cross-sectional areas.

電磁切換弁３１がＯＮのとき、タンク１０からタンク圧の作動油が増圧装置７の油室７−１に流入し、ピストン７−５がスプリング７−６の付勢力によって図の右方向（縮み方向）に移動し、タンク１０内の作動油が管路１６、逆止弁１７を介して油室７−４内に流入するとともに、油室７−２内の作動油が電磁切換弁３１、管路３７、３３を通ってタンク１０に排出される。その結果、ピストン７−５は、図示のような縮みエンド位置となる。 When the electromagnetic switching valve 31 is ON, the hydraulic oil at tank pressure flows from the tank 10 into the oil chamber 7-1 of the pressure increasing device 7, and the piston 7-5 is moved in the right direction in the figure by the urging force of the spring 7-6 ( The hydraulic oil in the tank 10 flows into the oil chamber 7-4 via the pipe line 16 and the check valve 17, and the hydraulic oil in the oil chamber 7-2 moves to the electromagnetic switching valve 31. , Discharged through the pipes 37 and 33 to the tank 10. As a result, the piston 7-5 is in the contracted end position as illustrated.

電磁切換弁３１がＯＦＦになると、ソレノイドが励磁されることにより電磁圧力変換装置３０から圧油が油室７−２に流入する。このとき、油室７−１内の作動油がタンク１０に排出され、ピストン７−５がスプリング７−６の付勢力に抗して図の左方向（伸び方向）に移動する。これにより、油室７−４内の作動油が逆止弁１４、管路１５を通ってアキュムレータ８内に蓄圧される。再び電磁切換弁３１がＯＮになると、再びタンク１０から作動油が油室７−１、７−４内に流入し、油室７−２内の作動油はタンク１０に排出され、ピストン７−５が右方向（縮み方向）に移動する。 When the electromagnetic switching valve 31 is turned off, pressure oil flows from the electromagnetic pressure conversion device 30 into the oil chamber 7-2 by exciting the solenoid. At this time, the hydraulic oil in the oil chamber 7-1 is discharged to the tank 10, and the piston 7-5 moves in the left direction (extension direction) against the urging force of the spring 7-6. Thereby, the hydraulic oil in the oil chamber 7-4 is accumulated in the accumulator 8 through the check valve 14 and the pipe line 15. When the electromagnetic switching valve 31 is turned on again, the hydraulic oil again flows from the tank 10 into the oil chambers 7-1 and 7-4, the hydraulic oil in the oil chamber 7-2 is discharged to the tank 10, and the piston 7- 5 moves to the right (shrink direction).

（電磁圧力変換装置（ソレノイドバルブ）３０）
図２は、本実施例における電磁圧力変換装置３０の構造を示す模式的断面図である。図３は、本実施例における可動部材３０−３の構造を示す模式的断面図である。 (Electromagnetic pressure converter (solenoid valve) 30)
FIG. 2 is a schematic cross-sectional view showing the structure of the electromagnetic pressure transducer 30 in the present embodiment. FIG. 3 is a schematic cross-sectional view showing the structure of the movable member 30-3 in the present embodiment.

本実施例における電磁圧力変換装置３０は、往復動用のアクチュエータであるソレノイド部として、通電により磁界を発生するコイル３０−２と、コイル３０−２によって発生した磁界により磁気回路が形成されることでセンターポストの吸着面３０−５に磁気的に吸着される往復動部材としての可動部材（プランジャ）３０−３と、を備えている。可動部材３０−３は、円柱状の非磁性体部３０−３ａと磁性体部３０−３ｂからなり、非磁性体部３０−３ａの軸部の端面が、磁性体部３０−３ｂの端面に接合されている（接合部３０−３ｃ）。 The electromagnetic pressure conversion device 30 according to the present embodiment includes a coil 30-2 that generates a magnetic field by energization and a magnetic circuit formed by the magnetic field generated by the coil 30-2 as a solenoid unit that is an actuator for reciprocation. And a movable member (plunger) 30-3 as a reciprocating member that is magnetically attracted to the attracting surface 30-5 of the center post. The movable member 30-3 includes a cylindrical non-magnetic member 30-3a and a magnetic member 30-3b, and the end surface of the shaft portion of the non-magnetic member 30-3a is the end surface of the magnetic member 30-3b. It is joined (joining part 30-3c).

非磁性体部３０−３ａは、ケース３０−１内に内封されており、外周面Ａがケース３０−１の内周面と摺動可能に構成されている。非磁性体部３０−３ａは、コイル３０−２が消磁状態にある場合は、図示のように、スプリング３０−４の付勢力によってケース３０−１の内壁３０−１ａに押接される。 The nonmagnetic part 30-3a is enclosed in the case 30-1, and the outer peripheral surface A is configured to be slidable with the inner peripheral surface of the case 30-1. When the coil 30-2 is in a demagnetized state, the nonmagnetic member 30-3a is pressed against the inner wall 30-1a of the case 30-1 by the urging force of the spring 30-4 as shown in the figure.

磁性体部３０−３ｂは、コイル３０−２と、コイル３０−２両端に設けられた磁性部材からなるプレートとによって形成される空間内に内封されており、外周面Ａがコイル３０−２の収容ケースの内周面と対向し、軸方向に移動可能に構成されている。磁性体部３０−３ｂは、コイル３０−２が励磁状態になると、コイル３０−２によって発生した磁界により磁気回路が形成されることで、センターポストの吸着面３０−５に磁気的に吸引される。 The magnetic body 30-3b is enclosed in a space formed by the coil 30-2 and plates made of magnetic members provided at both ends of the coil 30-2, and the outer peripheral surface A is the coil 30-2. This is opposed to the inner peripheral surface of the housing case and is configured to be movable in the axial direction. When the coil 30-2 is in an excited state, the magnetic part 30-3b is magnetically attracted to the attracting surface 30-5 of the center post by forming a magnetic circuit by the magnetic field generated by the coil 30-2. The

コイル３０−２が励磁されると、磁性体部３０−３ｂは、磁力Ｆｍによりスプリング３０−４の付勢力Ｆｓと非磁性体部３０−３ａ端部に働く油圧力Ｆｐに打ち勝って吸着面３０−５に吸着されるまで図の左方に移動する。ここで、磁性体部３０−３ｂに働く磁力Ｆｍと、スプリング３０−４の付勢力Ｆｓと、非磁性体部３０−３ａ端部に働く油圧力Ｆｐと、の関係は、図４に示すように、常に磁力Ｆｍがスプリング付勢力Ｆｓと油圧力Ｆｐの合力よりも大きくなるように構成される。図４は、可動部材３０−３のストロークと可動部材に働く力との関係を示す図である。なお、図中の距離Ｘは、コイル３０−２が消磁状態における、磁性体部３０−３ｂ端部と吸着面３０−５との間の距離である。 When the coil 30-2 is excited, the magnetic member 30-3b overcomes the urging force Fs of the spring 30-4 and the oil pressure Fp acting on the end of the non-magnetic member 30-3a by the magnetic force Fm. Move to the left in the figure until it is attracted to -5. Here, the relationship between the magnetic force Fm acting on the magnetic body portion 30-3b, the urging force Fs of the spring 30-4, and the oil pressure Fp acting on the end of the nonmagnetic body portion 30-3a is as shown in FIG. In addition, the magnetic force Fm is always configured to be larger than the resultant force of the spring biasing force Fs and the oil pressure Fp. FIG. 4 is a diagram showing the relationship between the stroke of the movable member 30-3 and the force acting on the movable member. The distance X in the figure is the distance between the end of the magnetic body 30-3b and the attracting surface 30-5 when the coil 30-2 is in a demagnetized state.

電磁圧力変換装置３０は、ケース３０−１のスプリング３０−４が配置された空間内に、タンク１０から管路３３、逆止弁３４を介して低圧（タンク圧）の作動油が流入する。タンク１０から電磁圧力変換装置３０に流入した作動油は、コイル３０−２の励磁によって可動部材３０−３が移動することにより、逆止弁３５、管路３６、電磁切換弁３１を介して増圧装置７の油室７−２に押し込まれる。これにより、上述したように、ピストン７−５が図の左方に移動し、増圧された作動油がアキュムレータ８に蓄圧される。また、電磁切換弁３１を励磁してＯＮ状態に切り換えると、増圧装置７の油室７−２が管路３７、３３を介してタンク１０に導通する状態となり、ピストン７−５がスプリング７−６の付
勢力により図の右方に移動することで油室７−２内の作動油はタンク１０に排出される。 In the electromagnetic pressure conversion device 30, low-pressure (tank pressure) hydraulic oil flows from the tank 10 through the conduit 33 and the check valve 34 into the space where the spring 30-4 of the case 30-1 is disposed. The hydraulic oil that has flowed into the electromagnetic pressure conversion device 30 from the tank 10 increases via the check valve 35, the pipe line 36, and the electromagnetic switching valve 31 when the movable member 30-3 is moved by the excitation of the coil 30-2. It is pushed into the oil chamber 7-2 of the pressure device 7. As a result, as described above, the piston 7-5 moves to the left in the figure, and the pressurized hydraulic oil is accumulated in the accumulator 8. Further, when the electromagnetic switching valve 31 is excited and switched to the ON state, the oil chamber 7-2 of the pressure increasing device 7 is brought into conduction with the tank 10 through the pipe lines 37 and 33, and the piston 7-5 is moved to the spring 7. The hydraulic oil in the oil chamber 7-2 is discharged to the tank 10 by moving to the right in the figure by the -6 biasing force.

本実施例は、増圧装置７の油室７−２の最大容積、すなわちピストン７−５の大径部が油室７−１端部まで移動したときの容積をＶｂとし、電磁圧力変換装置３０の可動部材３０−３の非磁性体部３０−３ａが最大移動時に押し出す容積をＶｍとしたとき、以下の関係を満たすように構成されている。
Ｖｂ＝ｎ×Ｖｍ（ｎ：整数） In this embodiment, the maximum volume of the oil chamber 7-2 of the pressure booster 7, that is, the volume when the large diameter portion of the piston 7-5 moves to the end of the oil chamber 7-1 is Vb, and the electromagnetic pressure conversion device When the volume that the nonmagnetic body portion 30-3a of the 30 movable members 30-3 pushes out at the time of maximum movement is Vm, the following relationship is satisfied.
Vb = n × Vm (n: integer)

図５は、本実施例におけるコイル３０−２の通電のＯＮ／ＯＦＦ（励磁／消磁）と、電磁切換弁３１のコイルの通電のＯＮ／ＯＦＦのタイミング図である。すなわち、本実施例では、増圧装置７においてピストン７−５の１回の移動に必要とする電磁圧力変換装置３０からの作動油の流入量を、電磁圧力変換装置３０において可動部材３０−３の１回の移動による作動油の吐出量の整数倍とし、電磁切換弁３１及び電磁圧力変換装置３０のコイルの励磁／消磁パターンを、図５に示すようなパターンとしている。こうすることにより、可動部材３０−３の非磁性体部３０−３ａが最大移動時に押し出す容積を無駄なく増圧装置７の油室７−２に押し込むことができ、アキュムレータ８に効率的に油圧を蓄圧することができる。したがって、余剰油の発生をなくすことが可能となり、従来技術のように管路３６上に発生する異常高圧の発生を防止するためのリリーフ弁を設置する必要がなくなる。これにより、回路構成の簡素化を図ることができる。 FIG. 5 is a timing chart of ON / OFF (excitation / demagnetization) of energization of the coil 30-2 and ON / OFF of energization of the coil of the electromagnetic switching valve 31 in the present embodiment. That is, in this embodiment, the inflow amount of hydraulic oil from the electromagnetic pressure conversion device 30 required for one movement of the piston 7-5 in the pressure increasing device 7 is converted into the movable member 30-3 in the electromagnetic pressure conversion device 30. As shown in FIG. 5, the excitation / demagnetization pattern of the coils of the electromagnetic switching valve 31 and the electromagnetic pressure conversion device 30 is set to be an integral multiple of the discharge amount of the hydraulic oil by one movement of. By doing so, the volume that the non-magnetic member 30-3a of the movable member 30-3 pushes out at the time of maximum movement can be pushed into the oil chamber 7-2 of the pressure increasing device 7 without waste, and the hydraulic pressure can be efficiently applied to the accumulator 8. Can be accumulated. Therefore, it is possible to eliminate the generation of surplus oil, and there is no need to install a relief valve for preventing the occurrence of abnormal high pressure that occurs on the pipe line 36 as in the prior art. As a result, the circuit configuration can be simplified.

（変形例）
図６〜図９を参照して、上述の電磁圧力変換装置３０の構成を変更した、本実施例の変形例について説明する。図６は、変形例に係る油圧制御装置（流体圧制御装置）の油圧回路図である。図７は、変形例における電磁圧力変換装置４０の構造を示す模式的断面図である。図８は、変形例における可動部材４０−４の構造を示す模式的断面図である。図９は、変形例におけるコイル４０−２、４０−３の通電のＯＮ／ＯＦＦ（励磁／消磁）と、電磁切換弁３１のコイルの通電のＯＮ／ＯＦＦのタイミング図である。 (Modification)
With reference to FIGS. 6-9, the modification of a present Example which changed the structure of the above-mentioned electromagnetic pressure converter 30 is demonstrated. FIG. 6 is a hydraulic circuit diagram of a hydraulic control device (fluid pressure control device) according to a modification. FIG. 7 is a schematic cross-sectional view showing the structure of the electromagnetic pressure transducer 40 in a modified example. FIG. 8 is a schematic cross-sectional view showing the structure of the movable member 40-4 in the modification. FIG. 9 is a timing chart of ON / OFF (excitation / demagnetization) of energization of the coils 40-2 and 40-3 and ON / OFF of energization of the coil of the electromagnetic switching valve 31 in the modification.

変形例における電磁圧力変換装置４０は、ソレノイド部のコイルとして、可動部材４０−４の往復動の一方のストローク用のコイル４０−２と、他方のストローク用のコイル４０−３の２種類のコイルが設けられている。コイル４０−２は、作動油を増圧装置７に吐出する際の可動部材４０−４のストロークに用いられ、通電により可動部材４０−４をセンターポストの吸着面４０−５に磁気的に吸着させる磁気回路を形成する。コイル４０−３は、作動油をタンク１０から吸入する際の可動部材４０−４のストロークに用いられ、通電により可動部材４０−４をセンターポストの吸着面４０−６に磁気的に吸着させる磁気回路を形成する。 The electromagnetic pressure conversion device 40 according to the modified example has two types of coils: a coil 40-2 for one stroke of the reciprocating movement of the movable member 40-4 and a coil 40-3 for the other stroke, as coils of the solenoid part. Is provided. The coil 40-2 is used for the stroke of the movable member 40-4 when discharging the hydraulic oil to the pressure booster 7, and magnetically attracts the movable member 40-4 to the attracting surface 40-5 of the center post by energization. A magnetic circuit is formed. The coil 40-3 is used for the stroke of the movable member 40-4 when sucking the hydraulic oil from the tank 10, and magnetically attracts the movable member 40-4 to the attracting surface 40-6 of the center post by energization. Form a circuit.

変形例における可動部材４０−４は、それぞれ円柱状の、非磁性体部４０−４ａと、磁性体部４０−４ｂと、非磁性体部４０−４ｃと、磁性体部４０−４ｄと、が軸方向に並んだ構成を有している。非磁性体部４０−４ａは軸部の端面が磁性体部４０−４ｂの端面に接合されており（接合部４０−４ｅ）、非磁性体部４０−４ｃは、一方の端面が磁性体部４０−４ｂの端面に接合され（接合部４０−４ｆ）、他方の端面が磁性体部４０−４ｄの端面に接合されている（接合部４０−４ｇ）。 The movable member 40-4 in the modified example has a columnar nonmagnetic body portion 40-4a, a magnetic body portion 40-4b, a nonmagnetic body portion 40-4c, and a magnetic body portion 40-4d. It has the structure arranged in the axial direction. The nonmagnetic body portion 40-4a has the end face of the shaft portion joined to the end face of the magnetic body portion 40-4b (joint portion 40-4e), and the nonmagnetic body portion 40-4c has one end face that is a magnetic body portion. It is joined to the end face of 40-4b (joint part 40-4f), and the other end face is joined to the end face of the magnetic part 40-4d (joint part 40-4g).

非磁性体部４０−４ａは、ケース４０−１内に内封されており、外周面Ｃがケース４０−１の内周面と摺動可能に構成されている。磁性体部４０−４ｂ、非磁性体部４０−４ｃ及び磁性体部４０−４ｄは、収容ケースが軸方向に互いに気密に接合されたコイル４０−２、４０−３と、その両端に設けられた磁性部材からなるプレートとによって形成される空間内に内封されている。磁性体部４０−４ｂ、非磁性体部４０−４ｃ及び磁性体部４０−４ｄは、磁性体部４０−４ｂの外周面Ｄがコイル４０−２の収容ケースの内周面と対向
し、磁性体部４０−４ｄの外周面Ｅがコイル４０−３の収容ケースの内周面と対向し、軸方向に移動可能に構成されている。 The nonmagnetic part 40-4a is enclosed in the case 40-1, and the outer peripheral surface C is configured to be slidable with the inner peripheral surface of the case 40-1. The magnetic body portion 40-4b, the non-magnetic body portion 40-4c, and the magnetic body portion 40-4d are provided at both ends of the coils 40-2 and 40-3 in which the housing case is airtightly joined to each other in the axial direction. It is enclosed in a space formed by a plate made of a magnetic member. The magnetic body portion 40-4b, the non-magnetic body portion 40-4c, and the magnetic body portion 40-4d are such that the outer peripheral surface D of the magnetic body portion 40-4b faces the inner peripheral surface of the housing case of the coil 40-2. The outer peripheral surface E of the body part 40-4d faces the inner peripheral surface of the housing case of the coil 40-3, and is configured to be movable in the axial direction.

コイル４０−２が励磁されると、磁性体部４０−４ｂが磁力Ｆｍａにより４０−４ａ端部に働く油圧力Ｆｐに打ち勝って吸着面４０−５に吸着されるまで図の左方に移動する。また、コイル４０−３が励磁されると、磁性体部４０−４ｄが磁力Ｆｍｂにより吸着面４０−６に吸着されるまで図の右方に移動する。したがって、コイル４０−２及びコイル４０−３を交互に励磁することで、可動部材４０−４がケース内を往復動する。 When the coil 40-2 is excited, the magnetic body portion 40-4b moves to the left in the figure until it overcomes the oil pressure Fp acting on the end of the 40-4a by the magnetic force Fma and is attracted to the attracting surface 40-5. . Further, when the coil 40-3 is excited, the magnetic body portion 40-4d moves to the right in the drawing until it is attracted to the attracting surface 40-6 by the magnetic force Fmb. Therefore, the movable member 40-4 reciprocates in the case by alternately exciting the coils 40-2 and 40-3.

電磁圧力変換装置４０は、可動部材４０−４の往復動により、電磁圧力変換装置３０と同様、タンク１０より管路３３、逆止弁３４を通って流入した低圧油を逆止弁３５、管路３６、電磁切換弁３１を介して増圧装置７の油室７−２に増圧して押し込むことができる。これにより、増圧装置７においてピストン７−５が図の左方に移動し、上述したように、タンク圧から増圧された作動油がアキュムレータ８に蓄圧される。 The electromagnetic pressure conversion device 40 reciprocates the movable member 40-4 so that the low-pressure oil that has flowed from the tank 10 through the pipe line 33 and the check valve 34 by the reciprocating movement of the movable member 40-4 is supplied to the check valve 35 and the pipe. The pressure can be increased and pushed into the oil chamber 7-2 of the pressure increasing device 7 via the path 36 and the electromagnetic switching valve 31. Thereby, the piston 7-5 moves to the left in the figure in the pressure increasing device 7, and the hydraulic oil increased from the tank pressure is accumulated in the accumulator 8, as described above.

本変形例においても、上記実施例と同様、増圧装置７の油室７−２の最大容積、すなわちピストン７−５の大径部が油室７−１端部まで移動したときの容積をＶｂとし、電磁圧力変換装置４０の可動部材４０−４の非磁性体部４０−４ａが最大移動時に押し出す容積をＶｍとしたとき、以下の関係を満たすように構成されている。
Ｖｂ＝ｎ×Ｖｍ（ｎ：整数） Also in this modified example, the maximum volume of the oil chamber 7-2 of the pressure increasing device 7, that is, the volume when the large diameter portion of the piston 7-5 moves to the end of the oil chamber 7-1 is the same as in the above embodiment. When Vb is Vm, and the volume that the nonmagnetic body portion 40-4a of the movable member 40-4 of the electromagnetic pressure conversion device 40 pushes out during maximum movement is Vm, the following relationship is satisfied.
Vb = n × Vm (n: integer)

また、本実施例においても、上記実施例と同様、増圧装置７においてピストン７−５の１回の移動に必要とする電磁圧力変換装置４０からの作動油の流入量を、電磁圧力変換装置４０において可動部材４０−４の１回の移動による作動油の吐出量の整数倍とし、電磁切換弁３１及び電磁圧力変換装置４０のコイルの励磁／消磁パターンを、図９に示すようなパターンとしている。こうすることにより、可動部材４０−４の非磁性体部４０−４ａが最大移動時に押し出す容積を無駄なく増圧装置７の油室７−２に押し込むことができ、アキュムレータ８に効率的に圧油を蓄圧することができる。 Also in this embodiment, similarly to the above embodiment, the amount of hydraulic oil flowing from the electromagnetic pressure conversion device 40 required for one movement of the piston 7-5 in the pressure increase device 7 is expressed as an electromagnetic pressure conversion device. 40, an integral multiple of the amount of hydraulic fluid discharged by a single movement of the movable member 40-4, and the excitation / demagnetization pattern of the coils of the electromagnetic switching valve 31 and the electromagnetic pressure conversion device 40 are as shown in FIG. Yes. By doing so, the volume that the nonmagnetic body portion 40-4a of the movable member 40-4 pushes out at the time of maximum movement can be pushed into the oil chamber 7-2 of the pressure increasing device 7 without waste, and the accumulator 8 can be efficiently pressurized. Oil can be accumulated.

（本実施例の優れた点）
図１０に示すように、油圧発生部から油圧被供給回路４へ圧油を供給せずに増圧装置７及びアキュムレータ８からの圧油のみを油圧被供給回路４に供給する場合において、従来技術では、増圧装置７に供給する油圧を発生させるためのみに駆動機構１や油圧ポンプ２、サクションフィルタ１１、逆止弁１２、さらにはリリーフ弁２０などを設ける必要があった。本実施例によれば、電磁圧力変換装置３０における可動部材３０−３の往復移動により発生する流体圧によって増圧装置７を動作させる構成とすることにより、回路構成の簡素化を図ることができる。すなわち、電磁圧力変換装置３０は、コイル３０−２への通電を制御することにより動作させることができるので、図１０に示すような従来構成のように、サクションフィルタ１１や逆止弁１２、リリーフ弁２０さらに各油圧機器に接続する配管部品などが不要となり、シンプルな回路構成、省スペース化、コンパクト化を図ることができる。 (Excellent points of this example)
As shown in FIG. 10, in the case where only the pressure oil from the pressure intensifier 7 and the accumulator 8 is supplied to the hydraulic supplied circuit 4 without supplying the hydraulic oil from the hydraulic pressure generating unit to the hydraulic supplied circuit 4. Therefore, it is necessary to provide the drive mechanism 1, the hydraulic pump 2, the suction filter 11, the check valve 12, and the relief valve 20 only to generate the hydraulic pressure supplied to the pressure booster 7. According to the present embodiment, the circuit configuration can be simplified by adopting a configuration in which the pressure increasing device 7 is operated by the fluid pressure generated by the reciprocating movement of the movable member 30-3 in the electromagnetic pressure conversion device 30. . That is, since the electromagnetic pressure conversion device 30 can be operated by controlling the energization to the coil 30-2, the suction filter 11, the check valve 12, the relief, as in the conventional configuration shown in FIG. Valves 20 and piping parts connected to each hydraulic device are not necessary, and a simple circuit configuration, space saving, and compactness can be achieved.

また、従来技術では、駆動機構１や油圧ポンプ２及びリリーフ弁２０が設けられているために、各々が作動することによる所謂、エネルギーのロスが発生していたが、本実施例では、増圧装置７への圧油の供給を電磁圧力変換装置３０のソレノイド部の動作のみによって行う構成となるので、従来のようなエネルギーロスの発生を抑制することができる。したがって、装置全体の動作効率を著しく向上させることができる。 In the prior art, since the drive mechanism 1, the hydraulic pump 2, and the relief valve 20 are provided, so-called energy loss occurs due to the operation of each of them. Since the supply of the pressure oil to the device 7 is performed only by the operation of the solenoid unit of the electromagnetic pressure conversion device 30, the occurrence of energy loss as in the conventional case can be suppressed. Therefore, the operating efficiency of the entire apparatus can be significantly improved.

上記実施例では、作動流体として、作動油を例に挙げて説明したが、油以外の液体（流体）を用いる流体圧制御装置においても本発明が適用できることは言うまでもない。また
、増圧装置の構成も、上記実施例のようなピストン、シリンダによる構成に限定されるものではない。さらに電磁圧力変換装置の構成も、上記実施例のような電磁圧力変換装置の構成に限定されるものではない。 In the above embodiment, the working oil has been described as an example of the working fluid. However, it goes without saying that the present invention can also be applied to a fluid pressure control device using a liquid (fluid) other than oil. Further, the configuration of the pressure increasing device is not limited to the configuration of the piston and the cylinder as in the above embodiment. Further, the configuration of the electromagnetic pressure transducer is not limited to the configuration of the electromagnetic pressure transducer as in the above embodiment.

４油圧被供給回路（被供給回路）
７増圧装置
８アキュムレータ
９電磁切換弁
１０タンク（流体供給部）
３０電磁圧力変換装置
３１電磁切換弁 4 Hydraulic supplied circuit (supplied circuit)
7 Booster 8 Accumulator 9 Electromagnetic switching valve 10 Tank (fluid supply part)
30 Electromagnetic pressure transducer 31 Electromagnetic switching valve

Claims

A fluid pressure control device for increasing the pressure of a fluid supplied from a fluid supply unit and supplying the pressure to a supplied circuit,
An electromagnetic pressure converter for increasing and discharging the fluid supplied from the fluid supply unit by reciprocating a reciprocating member by energizing the coil;
A pressure increasing device that operates by the fluid pressure of the fluid discharged from the electromagnetic pressure conversion device, and increases and discharges the fluid supplied from the fluid supply unit;
With
The pressure increasing device has a cylinder and a piston that reciprocates in the cylinder, and the piston moves when the fluid pressure of the fluid discharged from the electromagnetic pressure conversion device is loaded. It is configured to increase the pressure of the supplied fluid and discharge it.
Maximum volume of the fluid chamber in which the fluid pressure is loaded in the pressure increasing device, Ru integral multiple der of the volume in which the reciprocating member in the electromagnetic pressure transducer pushes upon maximum movement in one direction of one of the reciprocating A fluid pressure control device.

The said electromagnetic pressure converter is provided with the 1st coil for one stroke in the reciprocating movement of the said reciprocating member, and the 2nd coil for the other stroke. The fluid pressure control apparatus described.

3. The fluid pressure control device according to claim 1, further comprising: a pressure accumulating unit capable of accumulating the fluid pressure of the fluid discharged from the pressure increasing device and supplying the accumulated fluid pressure to the downstream side.

The fluid pressure control device according to claim 3, further comprising a check valve between the pressure accumulating unit and a supply destination of the fluid pressure accumulated in the pressure accumulating unit.