JPH0893708A - Hydraulic circuit - Google Patents
Hydraulic circuitInfo
- Publication number
- JPH0893708A JPH0893708A JP6228255A JP22825594A JPH0893708A JP H0893708 A JPH0893708 A JP H0893708A JP 6228255 A JP6228255 A JP 6228255A JP 22825594 A JP22825594 A JP 22825594A JP H0893708 A JPH0893708 A JP H0893708A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- oil
- valve
- increasing
- hydraulic
- 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.)
- Withdrawn
Links
Landscapes
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、例えば破砕機、プレ
ス、成形機または試験装置等における油圧アクチュエー
タ（油圧シリンダ、油圧モータ）を駆動する油圧回路に
適用され、増圧制御および増量制御を必要に応じて自動
的に行い得る油圧回路に関するものである。BACKGROUND OF THE INVENTION The present invention is applied to a hydraulic circuit for driving a hydraulic actuator (hydraulic cylinder, hydraulic motor) in, for example, a crusher, a press, a molding machine or a testing device, and requires pressure increase control and amount increase control. The present invention relates to a hydraulic circuit that can be automatically performed according to the above.
【０００２】[0002]
【従来の技術】図５は、建築物の解体等に使用される機
械を示し、母機としての油圧ショベル１のフロント作業
機系２の先端にアタッチメントとしての破砕機３が取付
けられ、この破砕機３の爪は、油圧アクチュエータとし
ての開閉シリンダ４により開閉される。2. Description of the Related Art FIG. 5 shows a machine used for dismantling a building or the like, in which a crusher 3 as an attachment is attached to the tip of a front working machine system 2 of a hydraulic excavator 1 as a mother machine. The claw 3 is opened / closed by an opening / closing cylinder 4 as a hydraulic actuator.
【０００３】図６に示されるように、従来の破砕機３の
油圧回路には増圧回路がなく、操作弁12の出力油路は開
閉シリンダ４の伸側油路32および縮側油路33に各々直接
接続され、操作弁12の切換えにより油圧ポンプ13から吐
出された高圧油が交互に開閉シリンダ４に供給されると
ともに、開閉シリンダ４からのリターン油がタンク31に
排出され、開閉動作を行っている。As shown in FIG. 6, the hydraulic circuit of the conventional crusher 3 does not have a pressure increasing circuit, and the output oil passage of the operation valve 12 is the expansion side oil passage 32 and the contraction side oil passage 33 of the opening / closing cylinder 4. The high pressure oil discharged from the hydraulic pump 13 is alternately supplied to the open / close cylinder 4 by switching the operation valve 12, and the return oil from the open / close cylinder 4 is discharged to the tank 31 to perform the open / close operation. Is going.
【０００４】[0004]
【発明が解決しようとする課題】破砕機の閉動作時に
は、鉄筋、コンクリート等を破砕、切断するための強力
な力を必要とする。しかし、破砕力は油圧力で決まるた
め、従来の油圧回路では破砕機を装着した母機（例えば
油圧ショベル）の定格圧力による破砕力しか発揮できな
い。そして、母機の定格圧力は母機の油圧システムの最
適な圧力に設定されているため、破砕機などの強力な油
圧力を必要とする場合には圧力が不足し、破砕機の能力
を最大限に活用できないという問題がある。The closing operation of the crusher requires a strong force for crushing and cutting rebar, concrete and the like. However, since the crushing force is determined by the hydraulic pressure, the conventional hydraulic circuit can exert only the crushing force based on the rated pressure of the mother machine (for example, a hydraulic excavator) equipped with the crusher. And since the rated pressure of the mother machine is set to the optimum pressure of the hydraulic system of the mother machine, the pressure will be insufficient when strong oil pressure such as a crusher is required, and the capacity of the crusher will be maximized. There is a problem that it cannot be used.
【０００５】その解決策としては、定格圧力を破砕機使
用時の高い圧力に設定しなおすことも考えられるが、こ
れは、母機の油圧システム全体に重大な影響を及ぼし、
母機の損傷や寿命を短くするという問題も生じ易い。A possible solution is to reset the rated pressure to a high pressure when the crusher is used, but this has a serious effect on the entire hydraulic system of the mother machine,
Problems such as damage to the mother machine and shortening its life are also likely to occur.
【０００６】さらに、閉動作時でも破砕対象物に接する
までは、負荷が軽いため定格圧力は必要でなく、大流量
すなわち閉動作速度が大きいことが望まれるが、油圧源
の圧力対流量は一定であるため速度の向上はできない。Furthermore, since the load is light and the rated pressure is not required until it comes into contact with the object to be crushed even during the closing operation, a large flow rate, that is, a high closing operation speed is desired, but the pressure versus flow rate of the hydraulic source is constant. Therefore, the speed cannot be improved.
【０００７】本発明は、このような点に鑑みなされたも
ので、油圧システムの定格圧力を再設定することなく、
必要な時に自動的に増圧または増量された油圧を得るこ
とができる油圧回路を提供することを目的とする。The present invention has been made in view of the above circumstances, and it is possible to set the rated pressure of the hydraulic system without resetting the rated pressure.
An object of the present invention is to provide a hydraulic circuit that can automatically obtain an increased or increased hydraulic pressure when needed.
【０００８】[0008]
【課題を解決するための手段】請求項１に記載された発
明は、油圧源と、この油圧源に接続された操作弁と、こ
の操作弁により方向制御された圧油により作動される油
圧アクチュエータとを備えた油圧回路において、前記操
作弁と油圧アクチュエータとの間の少なくとも高圧を要
求される側の油路に介在され、自己に供給される圧力で
一方の位置に切換えられ前記油路から圧油を取出し、反
対側の油路からのパイロット圧により他方の位置に切換
えられ油圧アクチュエータからの排油をタンクに連通す
る圧油取出用切換弁と、この圧油取出用切換弁が一方の
位置にあるときにその出口ポートからの圧油によりパイ
ロット圧切換を繰返し行うパイロット弁と、上記圧油取
出用切換弁が一方の位置にあるときにその出口ポートか
らの圧油を供給油圧として上記パイロット弁の出力油圧
で切換制御される分配弁と、上記圧油取出用切換弁が一
方の位置にあるときにその出口ポートからの圧油が所定
の圧力以上になったときに通過させるシーケンス弁と、
上記分配弁の出口ポートに接続され、一方の位置に切換
えるためのバネに抗して、上記シーケンス弁を通過した
圧油により他方の位置に切換えられ増圧モードと増量モ
ードとを選択する増圧増量モード切換弁と、この増圧増
量モード切換弁の出口ポートに接続される大径の駆動油
室と小径の増圧油室とを有し、上記分配弁および増圧増
量モード切換弁を介して給排される圧油により駆動され
る増圧増量シリンダと、前記増圧増量モード切換弁の増
圧増量出口ポートと油圧アクチュエータの高圧を要求さ
れる側との間の管路中に設けられ、油圧アクチュエータ
への給油を可能とする方向性のチェック弁とを具備した
構成の油圧回路である。The invention described in claim 1 is to provide a hydraulic power source, an operation valve connected to the hydraulic pressure source, and a hydraulic actuator operated by pressure oil whose direction is controlled by the operation valve. In the hydraulic circuit provided with, the oil passage is interposed between at least the high pressure side between the operation valve and the hydraulic actuator, and is switched to one position by the pressure supplied to itself and the pressure from the oil passage is changed. A pressure oil extraction switching valve that takes out oil and switches it to the other position by pilot pressure from the oil passage on the opposite side to communicate the oil discharged from the hydraulic actuator to the tank, and this pressure oil extraction switching valve is located at one position. When the pilot valve that repeatedly switches the pilot pressure by the pressure oil from its outlet port is in the position 1 and the pressure oil take-out switching valve is in one position, the pressure oil from the outlet port is supplied with oil. As a distribution valve, which is switched and controlled by the output hydraulic pressure of the pilot valve, and when the pressure oil from the outlet port of the pressure oil take-out switching valve is in one position, when the pressure oil exceeds a predetermined pressure Sequence valve,
A pressure booster that is connected to the outlet port of the distributor valve and resists a spring for switching to one position, and is switched to the other position by pressure oil that has passed through the sequence valve to select a pressure boosting mode and a boosting mode. It has a boosting mode switching valve, a large-diameter drive oil chamber and a small-diameter boosting oil chamber connected to the outlet port of this boosting and boosting mode switching valve, and through the distribution valve and boosting and boosting mode switching valve. Is installed in a pipe line between the pressure increasing / increasing cylinder driven by the pressure oil supplied and discharged, the pressure increasing / increasing outlet port of the pressure increasing / increasing mode switching valve, and the side of the hydraulic actuator where high pressure is required. A hydraulic circuit having a directional check valve capable of supplying oil to the hydraulic actuator.
【０００９】請求項２に記載された発明は、請求項１記
載の油圧回路において、パイロット弁として、圧油取出
用切換弁が一方の位置にあるときにその出口ポートから
の圧油で駆動される油圧モータにより減速機を介して回
転される回転型パイロット弁を設けた構成の油圧回路で
ある。The invention described in claim 2 is, in the hydraulic circuit according to claim 1, driven by the pressure oil from the outlet port of the pilot oil valve when the pressure oil discharge switching valve is in one position. 2 is a hydraulic circuit having a rotary pilot valve that is rotated by a hydraulic motor via a speed reducer.
【００１０】請求項３に記載された発明は、請求項１記
載の油圧回路において、増圧増量シリンダの駆動油室お
よび増圧油室に対しメイクアップポンプがチェック弁を
介し接続された構成の油圧回路である。According to a third aspect of the invention, in the hydraulic circuit according to the first aspect, a makeup pump is connected to the drive oil chamber and the pressure increasing oil chamber of the pressure increasing cylinder by a check valve. It is a hydraulic circuit.
【００１１】[0011]
【作用】請求項１に記載された発明は、操作弁が中立状
態では、油圧源の吐出圧が閉じられているので油圧アク
チュエータは停止している。操作弁を一側に切換えて油
圧源の吐出圧を圧油取出用切換弁に送ると、同弁は自己
圧力で一方の位置を選択し、圧油がパイロット弁、分配
弁およびシーケンス弁に供給される。In the invention described in claim 1, when the operation valve is in the neutral state, the discharge pressure of the hydraulic pressure source is closed, so that the hydraulic actuator is stopped. When the operation valve is switched to one side and the discharge pressure of the hydraulic pressure source is sent to the pressure oil discharge switching valve, the valve selects one position by its own pressure and the pressure oil is supplied to the pilot valve, distribution valve and sequence valve. To be done.
【００１２】パイロット弁は繰返し切換作動して、その
制御圧力が分配弁の切換え駆動用圧力となり、分配弁を
左右に繰返し駆動する。分配弁が非中立位置に切換わる
と、その出力段に設けた増圧増量モード切換弁の流路を
経て、増圧増量シリンダに圧油が給油されるとともに排
出される。The pilot valve is repeatedly switched and the control pressure thereof becomes the switching drive pressure of the distribution valve, and the distribution valve is repeatedly driven left and right. When the distribution valve is switched to the non-neutral position, the pressure oil is supplied to the pressure increasing cylinder through the passage of the pressure increasing mode switching valve provided at the output stage and is discharged.
【００１３】増圧増量モード切換弁が一方の位置にある
時は増量モードであって、駆動油圧は増圧増量シリンダ
の増圧油室に入り、駆動油室から吐出された圧油により
油圧アクチュエータを例えば伸側に作動する。このとき
は、増圧増量シリンダの増圧油室（断面積が小さい）に
供給油が入ってピストン等の可動体を作動するので、駆
動油室（断面積が大きい）からは断面積比に比例した多
量の圧油が送り出され、油圧アクチュエータの伸び速度
を高めることができる。When the pressure increasing / increasing mode switching valve is in one position, it is in the pressure increasing mode, the drive oil pressure enters the pressure increasing oil chamber of the pressure increasing / increasing cylinder, and the hydraulic oil is discharged by the pressure oil discharged from the drive oil chamber. To the extension side, for example. At this time, the supply oil enters the pressure increasing oil chamber (having a small cross-sectional area) of the pressure increasing cylinder to actuate the movable body such as the piston. A proportionally large amount of pressure oil is sent out, and the extension speed of the hydraulic actuator can be increased.
【００１４】一方、油圧アクチュエータの伸側動作で負
荷が大きくなると、増圧増量シリンダに供給される圧力
も高くなり、この圧力がシーケンス弁で設定した圧力よ
り高くなると、シーケンス弁が連通作用して増圧増量モ
ード切換弁に切換用パイロット圧を供給し、増圧増量モ
ード切換弁を他方の位置に切換える。この状態を増圧モ
ードと呼ぶ。On the other hand, when the load increases due to the expansion side operation of the hydraulic actuator, the pressure supplied to the pressure boosting cylinder also increases, and when this pressure becomes higher than the pressure set by the sequence valve, the sequence valve operates in communication. The switching pilot pressure is supplied to the pressure boosting mode switching valve to switch the pressure boosting mode switching valve to the other position. This state is called a pressure increasing mode.
【００１５】この増圧モードでは、分配弁で制御された
圧油が増圧増量シリンダのピストン大径部（受圧面積が
大きい）に臨む駆動油室に導かれるので、ピストンが作
動すると、ピストン小径部（受圧面積が小さい）に臨む
増圧油室から受圧面積比に反比例する高圧の圧油が押し
出されて油圧アクチュエータを伸側に強力に作動するこ
ととなる。In this pressure boosting mode, the pressure oil controlled by the distribution valve is guided to the drive oil chamber facing the piston large diameter portion (having a large pressure receiving area) of the pressure boosting and increasing cylinder. The high pressure oil inversely proportional to the pressure receiving area ratio is pushed out from the pressure increasing oil chamber facing the portion (the pressure receiving area is small), and the hydraulic actuator is strongly operated toward the extension side.
【００１６】操作弁を他側に切換えると、油圧アクチュ
エータの縮側に圧油が送られると同時に、圧油取出用切
換弁にパイロット圧が送られて、同弁を他方の位置に作
動させるので、油圧アクチュエータの伸側の油はタンク
に排油される。When the operation valve is switched to the other side, the pressure oil is sent to the compression side of the hydraulic actuator, and at the same time, the pilot pressure is sent to the pressure oil take-out switching valve to operate the valve to the other position. The oil on the extension side of the hydraulic actuator is discharged to the tank.
【００１７】請求項２に記載された発明は、圧油取出用
切換弁にて一方の位置が選択されると、この切換弁を経
た圧油が油圧モータおよび回転型パイロット弁に同時に
供給され、油圧モータが回転されて減速機を介し回転型
パイロット弁が回転されることにより、この弁から出力
されるパイロット圧が繰返し切換えられる。According to the second aspect of the invention, when one position is selected by the pressure oil take-out switching valve, the pressure oil passing through this switching valve is simultaneously supplied to the hydraulic motor and the rotary pilot valve, When the hydraulic motor is rotated and the rotary pilot valve is rotated through the speed reducer, the pilot pressure output from this valve is repeatedly switched.
【００１８】請求項３に記載された発明は、増圧増量シ
リンダにて供給、吐出に関与しないため余剰油が発生す
る二つの油室から排油系統へ余剰油が排出されるが、そ
のために不足油が発生する油室にはメイクアップポンプ
からチェック弁を経た油が補充される。In the invention described in claim 3, the surplus oil is discharged from the two oil chambers where the surplus oil is generated because it does not participate in the supply and discharge by the pressure boosting / increasing cylinder. The makeup chamber is replenished with oil that has passed through a check valve in the oil chamber where insufficient oil is generated.
【００１９】[0019]
【実施例】以下、本発明の一実施例として図５に示され
た油圧ショベルの破砕機に適用される図１の増圧増量回
路を例にとって詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A detailed explanation will be given below by taking as an example the pressure increasing circuit of FIG. 1 applied to the crusher of a hydraulic excavator shown in FIG. 5 as one embodiment of the present invention.
【００２０】図５において、母機としての油圧ショベル
１のフロント作業機系２の先端にはアタッチメントとし
ての破砕機３が取付けられ、この破砕機３の爪は、油圧
アクチュエータとしての開閉シリンダ４により開閉され
る。該シリンダ４の伸び操作時には爪が閉じて対象物を
破砕するので、伸び操作時に強力な推力が必要となる。
これからは、開閉シリンダを油圧アクチュエータと言
う。In FIG. 5, a crusher 3 as an attachment is attached to the tip of a front working machine system 2 of a hydraulic excavator 1 as a mother machine, and a claw of the crusher 3 is opened / closed by an opening / closing cylinder 4 as a hydraulic actuator. To be done. During the extension operation of the cylinder 4, the claws close and the object is crushed, so a strong thrust force is required during the extension operation.
From now on, the open / close cylinder will be referred to as a hydraulic actuator.
【００２１】この種の油圧アクチュエータの油圧回路
は、図１に示されるように、油圧源としての油圧ポンプ
13と、この油圧ポンプ13に接続された操作弁12と、この
操作弁12により方向制御された圧油により伸縮作動され
る油圧アクチュエータ４とを基本的に備えている。As shown in FIG. 1, a hydraulic circuit of a hydraulic actuator of this type includes a hydraulic pump as a hydraulic source.
Basically, there are provided 13, an operation valve 12 connected to this hydraulic pump 13, and a hydraulic actuator 4 which is expanded and contracted by pressure oil whose direction is controlled by this operation valve 12.
【００２２】先ず、図１に示された油圧回路の概略を説
明すると、前記操作弁12と油圧アクチュエータ４との間
の少なくとも高圧を要求される側の油路60，61間に、自
己の圧力でＡ位置（増圧増量回路に圧油を取出す位置）
に、また反対側の油路からのパイロット圧によりＢ位置
（排油位置）に切換えられる圧油取出用切換弁８が介在
されている。First, the outline of the hydraulic circuit shown in FIG. 1 will be described. At least between the operation valve 12 and the hydraulic actuator 4 between the oil passages 60 and 61 on the side where high pressure is required, the self pressure is applied. At position A (position where pressure oil is taken out to the pressure booster circuit)
Further, there is a pressure oil extraction switching valve 8 which is switched to the B position (oil discharging position) by the pilot pressure from the oil passage on the opposite side.
【００２３】この圧油取出用切換弁８がＡ位置にあると
きの出口ポートに分配弁６、シーケンス弁７、回転型パ
イロット弁10および油圧モータ15がそれぞれ接続されて
いる。前記分配弁６には増圧増量モード切換弁17を介
し、この増圧増量モード切換弁17によって選択された増
量モード（Ｇ位置）または増圧モード（Ｈ位置）で作動
される複動形の増圧増量シリンダ５が接続されている。The distribution valve 6, the sequence valve 7, the rotary pilot valve 10 and the hydraulic motor 15 are connected to the outlet ports when the pressure oil take-out switching valve 8 is in the A position. The distribution valve 6 is of a double-acting type operated via a pressure increasing / increasing mode switching valve 17 and operated in the pressure increasing mode (G position) or pressure increasing mode (H position) selected by the pressure increasing / increasing mode switching valve 17. A pressure increasing cylinder 5 is connected.
【００２４】この増圧増量シリンダ５に増圧増量モード
切換弁17の増圧増量出口ポートｇ，ｊおよびチェック弁
35，36を経て油圧アクチュエータ４の伸側油室20が接続
されている。また、増圧増量シリンダ５の作動に伴って
油量が不足する油室48〜51に対し油を補給するメイクア
ップポンプ18がチェック弁37，38を介し接続されてい
る。The pressure boosting / increasing cylinder 5 has a pressure boosting / increasing mode switching valve 17 having pressure boosting / increasing outlet ports g, j and a check valve.
The expansion side oil chamber 20 of the hydraulic actuator 4 is connected via 35 and 36. Further, a makeup pump 18 for supplying oil to oil chambers 48 to 51 whose oil amount is insufficient due to the operation of the pressure increasing cylinder 5 is connected via check valves 37 and 38.
【００２５】次に、図１に示された各回路構成要素を個
別に説明する。Next, the circuit components shown in FIG. 1 will be individually described.
【００２６】前記操作弁12は、右側位置に切換えること
により前記油圧ポンプ13から吐出された高圧油を伸側油
路60および後述する増圧増量回路を経て油圧アクチュエ
ータ４の伸側油室20に、また左側位置に切換えることに
より前記高圧油を縮側油路24を経て油圧アクチュエータ
４の縮側油室21に供給する３位置４ポート切換弁であ
る。When the operation valve 12 is switched to the right side position, the high pressure oil discharged from the hydraulic pump 13 is transferred to the expansion side oil chamber 20 of the hydraulic actuator 4 through the expansion side oil passage 60 and a pressure increasing / increasing circuit which will be described later. A three-position four-port switching valve that supplies the high-pressure oil to the compression-side oil chamber 21 of the hydraulic actuator 4 via the compression-side oil passage 24 by switching to the left position.
【００２７】前記圧油取出用切換弁８は、伸側油路60に
圧油が立っているときは自己圧力を操作油室58に導きＡ
位置を保持して、圧油を前記油路60から分岐油路23を経
て増圧増量回路に取出すための２位置３ポート切換弁ま
たは２位置２方向切換弁である。また、操作弁12により
油圧アクチュエータ４を縮側操作したときは、縮側油路
24の圧力がパイロット油路９を経て操作油室59に導か
れ、圧油取出用切換弁８はＢ位置に切換わる。The pressure oil take-out switching valve 8 guides its own pressure to the operation oil chamber 58 when pressure oil is standing in the extension side oil passage 60.
A two-position three-port switching valve or a two-position two-way switching valve for holding the position and taking out the pressure oil from the oil passage 60 to the pressure increasing / increasing circuit via the branch oil passage 23. Further, when the hydraulic actuator 4 is operated by the operation valve 12 on the contraction side,
The pressure of 24 is introduced into the operation oil chamber 59 through the pilot oil passage 9, and the pressure oil extraction switching valve 8 is switched to the B position.
【００２８】前記油圧モータ15は、減速機16を介して回
転型パイロット弁10を回転させることにより、操作油路
43からこのパイロット弁10への圧油をパイロット油路4
4，42を経て分配弁６の操作油室56，57へ切換制御用の
パイロット圧として交互に供給する。また油圧モータ15
の供給口には絞り22を設けて油圧モータ15の回転数を制
限している。The hydraulic motor 15 causes the rotary pilot valve 10 to rotate through the speed reducer 16 to operate the operation oil passage.
The pressure oil from 43 to this pilot valve 10 is fed to the pilot oil passage 4
The pressure is alternately supplied to the operating oil chambers 56 and 57 of the distribution valve 6 via 4 and 42 as pilot pressure for switching control. Also hydraulic motor 15
A throttle 22 is provided at the supply port to limit the rotation speed of the hydraulic motor 15.
【００２９】次に、前記回転型パイロット弁10は、その
回転に伴ってＣ位置とＤ位置とに繰返し切換えられ、供
給圧力を２つのパイロット油路42，44に交互に供給する
２位置４ポート切換弁であり、このパイロット弁10から
給排されるパイロット圧により分配弁６を左右に繰返し
変位させる。この回転型パイロット弁10の模式図を図２
に示し、同断面Ｘ、Ｙ、Ｚを図３に示す。Next, the rotary pilot valve 10 is repeatedly switched between the C position and the D position according to the rotation thereof, and the two-position four-port system for supplying the supply pressure to the two pilot oil passages 42, 44 alternately. It is a switching valve, and the distribution valve 6 is repeatedly displaced left and right by the pilot pressure supplied and discharged from the pilot valve 10. A schematic diagram of this rotary pilot valve 10 is shown in FIG.
3 and the same cross-sections X, Y and Z are shown in FIG.
【００３０】すなわち、回転型パイロット弁10は、図２
および図３に示されるように前記油圧モータ15および減
速機16を一端面に一体的に取付けてなる円筒形の弁本体
10aの内部に回転弁体10b を回転自在に嵌合する。That is, the rotary pilot valve 10 is shown in FIG.
And a cylindrical valve body in which the hydraulic motor 15 and the speed reducer 16 are integrally attached to one end surface as shown in FIG.
The rotary valve body 10b is rotatably fitted in the interior of 10a.
【００３１】弁本体10a には、タンク29への油路27に連
通する排油ポート27´と、圧油取出用切換弁８からの操
作油路43に連通する給油ポート43´と、前記パイロット
油路42，44と連通するパイロットポート42´，44´と
を、それぞれ半径方向に穿設する。In the valve body 10a, an oil discharge port 27 'which communicates with the oil passage 27 to the tank 29, an oil supply port 43' which communicates with the operation oil passage 43 from the pressure oil take-out switching valve 8, and the pilot Pilot ports 42 'and 44', which communicate with the oil passages 42 and 44, are provided in the radial direction.
【００３２】回転弁体10b には、前記パイロットポート
42´，44´に連通する二つの周方向溝10c ，10d と、一
方の周方向溝10c に臨む軸方向溝10e ，10f と、他方の
周方向溝10d に臨む軸方向溝10g ，10h とを設ける。The rotary valve body 10b has the pilot port
Two circumferential grooves 10c and 10d communicating with 42 'and 44', axial grooves 10e and 10f facing one circumferential groove 10c, and axial grooves 10g and 10h facing the other circumferential groove 10d. Set up.
【００３３】軸方向溝10f ，10g は角度によって操作油
路43からの給油ポート43´に連通し、さらに、軸方向溝
10e ，10h は角度によってタンク油路27への排油ポート
27´と連通し、この回転型パイロット弁10の排油を油路
27からタンク29へ排出する構造である。The axial grooves 10f and 10g communicate with the oil supply port 43 'from the operation oil passage 43 depending on the angle, and further, the axial grooves
10e and 10h are oil discharge ports to the tank oil passage 27 depending on the angle.
It communicates with 27 ', and the drain oil of this rotary pilot valve 10
It is a structure to discharge from 27 to the tank 29.
【００３４】そして、回転弁体10b が回転すると、給油
ポート43´が軸方向溝10f ，10g を経てパイロットポー
ト42´，44´の一方と交互に連通し、給油ポート43´と
連通しないパイロットポート42´，44´の他方は排油ポ
ート27´と連通する。Then, when the rotary valve body 10b rotates, the oil supply port 43 'alternately communicates with one of the pilot ports 42', 44 'through the axial grooves 10f, 10g, and does not communicate with the oil supply port 43'. The other of 42 'and 44' communicates with the oil drain port 27 '.
【００３５】次に、前記分配弁６は、分岐油路23および
供給油路25からの圧油を分配弁６のＥ位置、Ｆ位置にて
出力油路52または出力油路53に切換え送油する３位置４
ポート切換弁である。バネ14は中立保持のために設けて
いる。この分配弁６からの排油はタンク油路26およびチ
ェック弁11を経て、縮側油路24に送られる。Next, the distribution valve 6 switches the pressure oil from the branch oil passage 23 and the supply oil passage 25 to the output oil passage 52 or the output oil passage 53 at the E position and the F position of the distribution valve 6 and sends the oil. 3 position 4
It is a port switching valve. The spring 14 is provided to hold the neutral position. The oil discharged from the distribution valve 6 is sent to the compression side oil passage 24 via the tank oil passage 26 and the check valve 11.
【００３６】また、前記シーケンス弁７は、その一次側
が前記圧油取出用切換弁８のＡ位置出口ポートに連通さ
れ、二次側が増圧増量モード切換弁17の操作油室41に連
通されている。そして、一次側の負荷が大きい場合はこ
のシーケンス弁７を経て一次側から二次側に供給される
油圧をパイロット圧として増圧増量モード切換弁17を切
換え、上記増圧増量シリンダ５への流入および流出回路
を増量モードから増圧モードに切換える。The sequence valve 7 has its primary side communicated with the A-position outlet port of the pressure oil withdrawing switching valve 8 and its secondary side communicated with the operating oil chamber 41 of the pressure increasing / increasing mode switching valve 17. There is. When the load on the primary side is large, the hydraulic pressure supplied from the primary side to the secondary side via the sequence valve 7 is used as a pilot pressure to switch the pressure increasing / increasing mode switching valve 17 to flow into the pressure increasing / increasing cylinder 5. And switching the outflow circuit from the increasing mode to the increasing mode.
【００３７】次に、前記増圧増量モード切換弁17は、後
述するスプールの一側に圧縮バネ14が設けられ他側に操
作油室41が設けられ、バネ14の付勢力で一方のＧ位置
（増量モード）に切換わり、シーケンス弁７の二次圧力
が操作油路19を通って操作油室41に働くとバネ14の付勢
力に抗して他方のＨ位置（増圧モード）に切換わる２位
置10ポート切換弁または２位置６方向切換弁である。Next, the pressure increasing / increasing mode switching valve 17 is provided with a compression spring 14 on one side of a spool and an operating oil chamber 41 on the other side, which will be described later. When the secondary pressure of the sequence valve 7 acts on the operation oil chamber 41 through the operation oil passage 19 after switching to the (increase mode), it is switched to the other H position (pressure increase mode) against the biasing force of the spring 14. It is a 2-position 10-port switching valve or a 2-position 6-way switching valve to be replaced.
【００３８】この増圧増量モード切換弁17は、図４の模
式図に示されるように10個のポートａ〜ｊが設けられた
弁本体17a の軸孔内に、複数の周方向溝が設けられたス
プール17b を軸方向摺動自在に嵌合したものである。This pressure increasing / increasing mode switching valve 17 is provided with a plurality of circumferential grooves in the shaft hole of the valve body 17a having ten ports a to j as shown in the schematic view of FIG. The spool 17b is fitted so as to be slidable in the axial direction.
【００３９】下側の４つのポートｇ〜ｊは、ポートｇが
出力油路54と、ポートｈ，ｉが上記分配弁６からの制御
油路52，53と、ポートｊが出力油路55とそれぞれ接続さ
れている。前記出力油路54および出力油路55はそれぞれ
チェック弁35，36を介して増圧油路28に接続されてい
る。Of the lower four ports g to j, the port g is the output oil passage 54, the ports h and i are the control oil passages 52 and 53 from the distribution valve 6, and the port j is the output oil passage 55. Each is connected. The output oil passage 54 and the output oil passage 55 are connected to the boosting oil passage 28 via check valves 35 and 36, respectively.
【００４０】上側の６つのポートａ〜ｆは、ポートａと
ポートｃが高圧油路46と、ポートｂが中圧油路39と、ポ
ートｄとポートｆが中圧油路40と、ポートｅが高圧油路
47とそれぞれ接続されている。Among the upper six ports a to f, the ports a and c are the high pressure oil passage 46, the port b is the medium pressure oil passage 39, the ports d and f are the medium pressure oil passage 40, and the port e. High pressure oil passage
47 and each connected.
【００４１】そして、この増圧増量モード切換弁17がＧ
位置にあるときは、上記分配弁６からポートｈ，ｉへ交
互に供給された圧油がポートｃ，ｅを経て増圧増量シリ
ンダ５の左右対をなした断面積の小さな増圧油室50，51
の一方に供給されるとともに他方から排出され、ピスト
ン34が往復駆動される。The pressure increasing / increasing mode switching valve 17 is set to G
When in the position, the pressure oil alternately supplied from the distribution valve 6 to the ports h and i passes through the ports c and e and forms a left and right pair of the pressure boosting and increasing cylinders 5, and a pressure boosting oil chamber 50 having a small cross-sectional area is formed. ， 51
It is supplied to one side and discharged from the other side, and the piston 34 is reciprocally driven.
【００４２】このとき、断面積の大きな駆動油室48，49
から交互に吐出された多量の油（増圧油室50，51との断
面積比と比例する流量の油）が、増圧増量モード切換弁
17のポートｂ，ｆから増圧増量出口ポートｇ，ｊを経て
出力油路54，55に交互に供給される。At this time, the drive oil chambers 48, 49 having large cross-sectional areas
A large amount of oil (oil with a flow rate proportional to the cross-sectional area ratio with the pressure-increasing oil chambers 50 and 51) alternately discharged from the pressure-increasing / increasing mode switching valve
It is supplied alternately from the 17 ports b and f to the output oil passages 54 and 55 via the pressure increasing / increasing outlet ports g and j.
【００４３】一方、この増圧増量モード切換弁17がＨ位
置にあるときは、上記分配弁６からポートｈ，ｉへ交互
に供給された圧油が、ポートｂ，ｄから中圧油路39，40
の一方を経て、増圧増量シリンダ５の左右対をなした駆
動油室48，49に交互に供給され、ピストン34は駆動油室
48，49に臨む大径部（大きな受圧面積）に油圧を受けて
強力な力で往復駆動される。On the other hand, when the pressure increasing / increasing mode switching valve 17 is in the H position, the pressure oil alternately supplied from the distribution valve 6 to the ports h and i is the intermediate pressure oil passage 39 from the ports b and d. ， 40
Via one of them, the pressure increase cylinder 5 is alternately supplied to the left and right paired drive oil chambers 48 and 49, and the piston 34 is supplied to the drive oil chamber.
The large diameter part (large pressure receiving area) facing 48, 49 receives hydraulic pressure and is reciprocally driven with strong force.
【００４４】このとき、ピストン34の小径部（小さな受
圧面積）に臨む増圧油室50，51の一方には、ピストン大
径部との受圧面積比と反比例する高圧油が発生し、この
高圧油が、高圧油路46，47を経て増圧増量モード切換弁
17のポートａまたはｅから増圧増量出口ポートｇ，ｊに
供給される。At this time, in one of the pressure-increasing oil chambers 50, 51 facing the small diameter portion (small pressure receiving area) of the piston 34, high pressure oil which is inversely proportional to the pressure receiving area ratio with the piston large diameter portion is generated, and this high pressure oil is generated. Oil passes through high-pressure oil passages 46 and 47 to increase pressure and increase mode switching valve
It is supplied to the pressure increasing / increasing outlet port g, j from the port a or e of 17.
【００４５】この増圧増量モード切換弁17の増圧増量出
口ポートｇ，ｊは、チェック弁35，36を介して油圧アク
チュエータ４の伸側油室20に連通され、油圧アクチュエ
ータ４が伸方向に作動するときの速度増加あるいは出力
増加を可能としている。The pressure increasing / increasing outlet ports g, j of the pressure increasing / increasing mode switching valve 17 are communicated with the expansion side oil chamber 20 of the hydraulic actuator 4 via the check valves 35, 36, and the hydraulic actuator 4 is expanded in the extending direction. It is possible to increase the speed or output when operating.
【００４６】すなわち、前記シーケンス弁７が作動しな
い状態では、増圧増量モード切換弁17がバネ14の力によ
り図１に示された一方のＧ位置にあるので、増圧増量シ
リンダ５は増量モードで作用し、また、シーケンス弁７
が連通作動する高圧状態では、増圧増量モード切換弁17
は他方のＨ位置となり、増圧増量シリンダ５は増圧モー
ドで作用するように構成されている。That is, in the state where the sequence valve 7 is not operated, the pressure increasing / increasing mode switching valve 17 is in the one G position shown in FIG. And also the sequence valve 7
In the high pressure state in which the
Becomes the other H position, and the pressure increasing cylinder 5 is configured to operate in the pressure increasing mode.
【００４７】次に、前記複動形の増圧増量シリンダ５
は、中央に大径筒部が、その左右両側部に小径筒部がそ
れぞれ形成され、これらの筒部にピストン34が摺動自在
に嵌合され、大径筒部内のピストン両側に駆動油室48，
49が、また小径筒部内のピストン両側に増圧油室50，51
がそれぞれ設けられている。Next, the double acting pressure increasing cylinder 5
Has a large-diameter cylindrical portion formed in the center and small-diameter cylindrical portions formed on both left and right sides thereof, and a piston 34 is slidably fitted in these cylindrical portions, and a driving oil chamber is provided on both sides of the piston in the large-diameter cylindrical portion. 48,
49 also has pressure increasing oil chambers 50 and 51 on both sides of the piston in the small diameter cylinder.
Are provided respectively.
【００４８】前記駆動油室48，49は前記増圧増量モード
切換弁17の中圧油路39，40と接続され、前記増圧油室5
0，51は同じく増圧増量モード切換弁17の高圧油路46，4
7と接続されている。The drive oil chambers 48, 49 are connected to the medium pressure oil passages 39, 40 of the pressure increasing / increasing mode switching valve 17, and the pressure increasing oil chamber 5
Similarly, 0 and 51 are high pressure oil passages 46 and 4 of the pressure increase / increase mode switching valve 17, respectively.
Connected with 7.
【００４９】次に、前記メイクアップポンプ18は、吸入
側をタンク30に接続し、出口側を４つのチェック弁37，
38を経て前記中圧油路39，40および高圧油路46，47に接
続し、タンク30より吸込んだ油を増圧増量シリンダ５に
補給する。Next, the makeup pump 18 has its suction side connected to the tank 30 and its outlet side connected to the four check valves 37,
The intermediate pressure oil passages 39 and 40 and the high pressure oil passages 46 and 47 are connected via 38, and the oil sucked from the tank 30 is replenished to the pressure increasing cylinder 5.
【００５０】なお、図１に示されたタンク29，30，31は
説明の便宜上、異なる符号を付しているが、これらは共
通のタンクであることは言うまでもない。The tanks 29, 30, 31 shown in FIG. 1 are given different reference numerals for convenience of explanation, but it goes without saying that they are common tanks.
【００５１】次に、以上のように構成された破砕機用の
油圧回路の作動を説明する。Next, the operation of the hydraulic circuit for the crusher constructed as described above will be described.
【００５２】油圧アクチュエータ４の伸び操作（操作弁
12の右側位置）では、ポンプ13からの吐出圧油は伸側油
路60へ通じ、その圧力が切換弁８の操作油室58へ入るの
で、同弁をＡ位置に保持する。そのため、吐出圧油は分
岐油路23から操作油路43と供給油路25へ流れる。操作油
路43の圧油は、絞り22を経て油圧モータ15を回転すると
ともに、回転型パイロット弁10の供給圧となり、同弁の
作動でパイロット流路42，44に交互に供給され分配弁６
をＥ位置、Ｆ位置に繰返し切換える。Extension operation of the hydraulic actuator 4 (operation valve
At the position (right side of 12), the pressure oil discharged from the pump 13 flows to the expansion side oil passage 60, and the pressure thereof enters the operation oil chamber 58 of the switching valve 8, so that the valve is held at the A position. Therefore, the discharge pressure oil flows from the branch oil passage 23 to the operation oil passage 43 and the supply oil passage 25. The pressure oil in the operation oil passage 43 rotates the hydraulic motor 15 through the throttle 22 and also becomes the supply pressure of the rotary pilot valve 10, and is alternately supplied to the pilot passages 42, 44 by the operation of the valve and is distributed to the distribution valve 6
Is repeatedly switched to the E position and F position.
【００５３】分配弁６には供給油路25から圧油が供給さ
れているので、上記Ｅ位置では、圧油は制御油路53へ、
さらに増圧増量モード切換弁17はバネ14の力でＧ位置に
あるから切換弁17のポートｉ、ポートｅを通り、高圧油
路47を経て増圧増量シリンダ５の増圧油室51に流入す
る。そのためピストン34が左方に変位し、増圧油室50の
油は、高圧油路46、切換弁17のポートｃ、ポートｈ、制
御油路52、分配弁６、タンク油路26、チェック弁11およ
び操作弁12を経てタンク31に排出される。Since the distribution valve 6 is supplied with the pressure oil from the supply oil passage 25, the pressure oil is supplied to the control oil passage 53 at the position E.
Further, since the pressure increasing / increasing mode switching valve 17 is in the G position by the force of the spring 14, the pressure increasing / increasing mode switching valve 17 flows into the pressure increasing oil chamber 51 of the pressure increasing / increasing cylinder 5 through the port i and the port e of the switching valve 17 and the high pressure oil passage 47. To do. Therefore, the piston 34 is displaced to the left, and the oil in the pressure-increasing oil chamber 50 contains the high-pressure oil passage 46, the port c of the switching valve 17, the port h, the control oil passage 52, the distribution valve 6, the tank oil passage 26, and the check valve. It is discharged to the tank 31 through 11 and the operation valve 12.
【００５４】このようにして、ピストン34が左方へ変位
することにより、駆動油室48の油は圧縮されて中圧油路
39へ吐出される。その吐出量は増圧油室51への流入量と
比較して、ピストン34の小径部と大径部との断面積比に
比例して増量されている。In this way, the piston 34 is displaced to the left, whereby the oil in the drive oil chamber 48 is compressed and the medium pressure oil passage is formed.
It is discharged to 39. The discharge amount thereof is increased in proportion to the cross-sectional area ratio between the small diameter portion and the large diameter portion of the piston 34, as compared with the amount of flow into the booster oil chamber 51.
【００５５】この増量された流量は中圧油路39から切換
弁17のポートｂ、ポートｇ、出力油路54、チェック弁3
5、増圧油路28を経て、油圧アクチュエータ４の伸側油
室20へ流入し、油圧アクチュエータ４を伸側に作動す
る。このとき、駆動油室49にはメイクアップポンプ18か
らチェック弁38、中圧油路40を経て油が補給される。This increased flow rate is transmitted from the medium pressure oil passage 39 to the port b and port g of the switching valve 17, the output oil passage 54, and the check valve 3.
5. After passing through the pressure-increasing oil passage 28, it flows into the expansion side oil chamber 20 of the hydraulic actuator 4 and operates the hydraulic actuator 4 to the expansion side. At this time, the drive oil chamber 49 is replenished with oil from the makeup pump 18 through the check valve 38 and the medium pressure oil passage 40.
【００５６】油圧アクチュエータ４の縮側の油は、縮側
油路24でチェック弁11からの油と合流して操作弁12から
タンク31へ放出される。The oil on the compression side of the hydraulic actuator 4 merges with the oil from the check valve 11 in the compression oil passage 24 and is discharged from the operation valve 12 to the tank 31.
【００５７】同様に、分配弁６がＦ位置に切換わると、
増圧増量シリンダ５のピストン34が右方に変位する。Similarly, when the distribution valve 6 is switched to the F position,
The piston 34 of the pressure increasing cylinder 5 is displaced rightward.
【００５８】上記伸び動作中に、油圧アクチュエータ４
の負荷（爪の破砕力）が増加すると増圧油路28の圧力が
上昇し、増圧増量シリンダ５への高圧油路46，47の圧力
が上昇するので、分岐油路23の圧力も上昇する。During the extension operation, the hydraulic actuator 4
When the load (crushing force of the claw) increases, the pressure in the pressure-increasing oil passage 28 increases, and the pressure in the high-pressure oil passages 46, 47 to the pressure-increasing and increasing cylinder 5 increases, so the pressure in the branch oil passage 23 also increases. To do.
【００５９】分岐油路23の圧力が上昇して、シーケンス
弁７の設定圧力以上になると、操作油路19に圧力が立っ
て、操作油室41に作用する圧力で切換弁17がＨ位置に切
換わる。When the pressure in the branch oil passage 23 rises and becomes equal to or higher than the set pressure of the sequence valve 7, pressure is raised in the operation oil passage 19 and the switching valve 17 is moved to the H position by the pressure acting on the operation oil chamber 41. Switch.
【００６０】このように、回転型パイロット弁10および
分配弁６の作動は上記と同じく継続したままで、切換弁
17がＨ位置になると、分配弁６から制御油路53に出力さ
れた圧油は切換弁17のポートｉ、ポートｄ、中圧油路40
を経て増圧増量シリンダ５の駆動油室49へ流入し、ピス
トン34が左方に変位するので、駆動油室48の油は、中圧
油路39、切換弁17のポートｂ、ポートｈ、制御油路52お
よび分配弁６を経てタンクに放出される。In this way, the operation of the rotary pilot valve 10 and the distribution valve 6 remains the same as above, and the switching valve
When 17 is in the H position, the pressure oil output from the distribution valve 6 to the control oil passage 53 is the port i, the port d of the switching valve 17, and the intermediate pressure oil passage 40.
After that, the piston 34 is displaced leftward, so that the oil in the drive oil chamber 48 is stored in the medium pressure oil passage 39, the port b of the switching valve 17, the port h, and the like. It is discharged to the tank through the control oil passage 52 and the distribution valve 6.
【００６１】同時に、増圧油室50の油は圧縮されつつ高
圧油路46、切換弁17のポートａ、ポートｇ、出力油路5
4、チェック弁35、増圧油路28を経て油圧アクチュエー
タ４の伸側油室20へ送られる。At the same time, the oil in the pressure-increasing oil chamber 50 is being compressed while the high-pressure oil passage 46, the port a of the switching valve 17, the port g, and the output oil passage 5 are being compressed.
4, the check valve 35, and the pressure-increasing oil passage 28 are sent to the expansion side oil chamber 20 of the hydraulic actuator 4.
【００６２】この時、増圧増量シリンダ５のピストン大
径部に作用する流入圧力に対し、ピストン小径部から発
生する吐出圧力は、受圧面積比に反比例して増圧される
ので、油圧アクチュエータ４の出力が強大になる。At this time, since the discharge pressure generated from the small diameter portion of the piston is increased in inverse proportion to the pressure receiving area ratio with respect to the inflow pressure acting on the large diameter portion of the piston of the pressure increasing cylinder 5, the hydraulic actuator 4 The output of will be strong.
【００６３】増圧油室51の油はピストン34の変位分だけ
不足するのでメイクアップポンプ18およびチェック弁37
から補給される。Since the oil in the booster oil chamber 51 is insufficient by the displacement of the piston 34, the makeup pump 18 and the check valve 37
Will be supplied from.
【００６４】以上詳述したように、切換弁17がＧ位置に
あれば増量モード、Ｈ位置にあれば増圧モードとなり、
いずれの場合も回転型パイロット弁10及び分配弁６は連
続して作動しているので、増圧増量シリンダ５も往復動
作を繰り返しており、そして、油圧アクチュエータ４の
負荷の大きさとシーケンス弁７の動作が関連づけられる
ので、自動的に増圧増量モードが選択される。As described in detail above, when the switching valve 17 is in the G position, the increasing mode is set, and when it is in the H position, the pressure increasing mode is set.
In either case, since the rotary pilot valve 10 and the distribution valve 6 are continuously operating, the pressure increasing cylinder 5 also repeats the reciprocating motion, and the load of the hydraulic actuator 4 and the sequence valve 7 are not changed. Since the motions are related, the pressure increasing mode is automatically selected.
【００６５】一方、油圧アクチュエータ４の縮み操作
（操作弁12の左位置）では、油圧ポンプ13の吐出油が、
縮側油路24から油圧アクチュエータ４の縮側油室21に入
ると同時に、同圧力がパイロット油路９を経て、切換弁
８をＢ位置にするので、伸側油室20の油は伸側油路61、
切換弁８、伸側油路60を経てタンク31に放出される。On the other hand, in the contraction operation of the hydraulic actuator 4 (the left position of the operation valve 12), the oil discharged from the hydraulic pump 13 is
At the same time that the pressure enters the compression-side oil chamber 21 of the hydraulic actuator 4 from the compression-side oil passage 24, the same pressure passes through the pilot oil passage 9 to set the switching valve 8 to the B position, so that the oil in the expansion-side oil chamber 20 is expanded. Oil passage 61,
It is discharged to the tank 31 via the switching valve 8 and the expansion oil passage 60.
【００６６】なお、実施例では、油圧ショベルにおける
破砕機の場合について述べたが、このような増圧増量回
路は、プレス、射出形成機又は試験装置等で使用される
油圧シリンダ、油圧モータ等を駆動する油圧回路で部分
的に高圧又は流量増加が必要な場合においても利用でき
る。In the embodiment, the case of the crusher in the hydraulic excavator has been described, but such a pressure increasing / increasing circuit includes a hydraulic cylinder, a hydraulic motor, etc. used in a press, an injection molding machine, a test apparatus or the like. It can be used even when the hydraulic circuit to be driven requires a partial high pressure or an increase in flow rate.
【００６７】[0067]
【発明の効果】請求項１に記載された発明によれば、シ
ーケンス弁と増圧増量モード切換弁との組合せにより、
増量モードと増圧モードとを自動的に切換え、負荷に高
圧力が要求されない増量モードの場合は、負荷をより早
く動かすことができ、また、負荷に高速度が要求されな
い増圧モードの場合は、油圧アクチュエータに母機の定
格圧力よりも高い圧力を連続的に供給して強力な荷重を
発生させることができる効果を有する。According to the invention described in claim 1, by the combination of the sequence valve and the pressure increase / increase mode switching valve,
It automatically switches between boost mode and boost mode, and in the boost mode where high pressure is not required for the load, the load can be moved faster, and in the boost mode where high speed is not required for the load. Further, it is possible to continuously supply a pressure higher than the rated pressure of the mother machine to the hydraulic actuator and generate a strong load.
【００６８】請求項２に記載された発明によれば、油圧
モータにて減速機を介し回転される回転型パイロット弁
によって、分配弁を繰返し切換えるためのパイロット圧
を交互に出力するパイロット圧切換手段を比較的簡単に
構成できる。According to the invention described in claim 2, the pilot pressure switching means for alternately outputting the pilot pressure for repeatedly switching the distribution valve by the rotary pilot valve rotated by the hydraulic motor through the speed reducer. Can be configured relatively easily.
【００６９】請求項３に記載された発明によれば、メイ
クアップポンプからチェック弁を経て増圧増量シリンダ
へ油を補充することにより、増圧増量シリンダでの不足
油の発生を防止でき、増圧増量シリンダでの増圧機能お
よび増量機能を損なうおそれを防止できる。According to the third aspect of the present invention, by supplying oil from the makeup pump to the pressure increasing / increasing cylinder through the check valve, it is possible to prevent the occurrence of insufficient oil in the pressure increasing / increasing cylinder. It is possible to prevent the pressure increasing function of the pressure increasing cylinder and the risk of impairing the pressure increasing function.
【図１】本発明に係る油圧回路の一実施例を示す回路図
である。FIG. 1 is a circuit diagram showing an embodiment of a hydraulic circuit according to the present invention.
【図２】同上油圧回路における回転型パイロット弁の模
式断面図である。FIG. 2 is a schematic cross-sectional view of a rotary pilot valve in the above hydraulic circuit.
【図３】（Ｘ）は図２のＸ線断面、（Ｙ）は図２のＹ線
断面、（Ｚ）は図２のＺ線断面の断面図である。3 (X) is a cross-sectional view taken along the line X of FIG. 2, (Y) is a cross section taken along the line Y of FIG. 2, and (Z) is a cross-sectional view taken along the line Z of FIG.
【図４】同上油圧回路における増圧増量モード切換弁の
模式断面図である。FIG. 4 is a schematic cross-sectional view of a pressure increasing / increasing mode switching valve in the hydraulic circuit.
【図５】破砕機を装置した油圧ショベルの側面図であ
る。FIG. 5 is a side view of a hydraulic excavator equipped with a crusher.
【図６】従来の破砕機用油圧回路を示す回路図である。FIG. 6 is a circuit diagram showing a conventional hydraulic circuit for a crusher.
４ 油圧アクチュエータとしての開閉シリンダ ５ 増圧増量シリンダ ６ 分配弁 ７ シーケンス弁 ８ 圧油取出用切換弁 10 回転型パイロット弁 12 操作弁 13 油圧源としての油圧ポンプ 14 バネ 15 油圧モータ 16 減速機 17 増圧増量モード切換弁 18 メイクアップポンプ 34 ピストン 35，36 チェック弁 37，38 チェック弁 48，49 駆動油室 50，51 増圧油室 4 Opening / closing cylinder as hydraulic actuator 5 Boosting / increasing cylinder 6 Distribution valve 7 Sequence valve 8 Pressure oil take-out switching valve 10 Rotary pilot valve 12 Operation valve 13 Hydraulic pump as hydraulic source 14 Spring 15 Hydraulic motor 16 Reducer 17 Increase Pressure increase mode switching valve 18 Makeup pump 34 Piston 35, 36 Check valve 37, 38 Check valve 48, 49 Drive oil chamber 50, 51 Pressure oil chamber
───────────────────────────────────────────────────── フロントページの続き (72)発明者 井上 俊一 兵庫県神戸市兵庫区和田宮通七丁目１番14 号 西菱エンジニアリング株式会社内 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Shunichi Inoue 7-14 Wadamiyadori, Hyogo-ku, Hyogo-Ken Nishiryo Engineering Co., Ltd.
Claims (3)
弁と、この操作弁により方向制御された圧油により作動
される油圧アクチュエータとを備えた油圧回路におい
て、 前記操作弁と油圧アクチュエータとの間の少なくとも高
圧を要求される側の油路に介在され、自己に供給される
圧力で一方の位置に切換えられ前記油路から圧油を取出
し、反対側の油路からのパイロット圧により他方の位置
に切換えられ油圧アクチュエータからの排油をタンクに
連通する圧油取出用切換弁と、 この圧油取出用切換弁が一方の位置にあるときにその出
口ポートからの圧油によりパイロット圧切換を繰返し行
うパイロット弁と、 上記圧油取出用切換弁が一方の位置にあるときにその出
口ポートからの圧油を供給油圧として上記パイロット弁
の出力油圧で切換制御される分配弁と、 上記圧油取出用切換弁が一方の位置にあるときにその出
口ポートからの圧油が所定の圧力以上になったときに通
過させるシーケンス弁と、 上記分配弁の出口ポートに接続され、一方の位置に切換
えるためのバネに抗して上記シーケンス弁を通過する圧
油により他方の位置に切換えられ増圧モードと増量モー
ドとを選択する増圧増量モード切換弁と、 この増圧増量モード切換弁の出口ポートに接続される大
径の駆動油室と小径の増圧油室とを有し、上記分配弁お
よび増圧増量モード切換弁を介して給排される圧油によ
り駆動される増圧増量シリンダと、 前記増圧増量モード切換弁の増圧増量出口ポートと油圧
アクチュエータの高圧を要求される側との間の管路中に
設けられ、油圧アクチュエータへの給油を可能とする方
向性のチェック弁とを具備したことを特徴とする油圧回
路。1. A hydraulic circuit comprising a hydraulic pressure source, an operation valve connected to the hydraulic pressure source, and a hydraulic actuator operated by pressure oil whose direction is controlled by the operation valve, wherein the operation valve and the hydraulic actuator are provided. Between at least one high-pressure side oil passage, which is switched to one position by the pressure supplied to itself to take out pressure oil from the oil passage, and by the pilot pressure from the opposite-side oil passage A pilot oil pressure switching valve that is switched to the other position and connects the oil discharged from the hydraulic actuator to the tank, and when this pressure oil extraction switching valve is in one position, the pilot oil pressure When the pilot valve that repeats switching and the pressure oil take-out switching valve are in one position, pressure oil from the outlet port of the pilot valve is used as the supply hydraulic pressure and is controlled by the output hydraulic pressure of the pilot valve. Control valve, a sequence valve that allows the pressure oil from the outlet port to pass when the pressure oil take-out switching valve is at one position, and a sequence valve that passes when the pressure oil is at a predetermined pressure or more, and an outlet of the distribution valve. A pressure increasing / increasing mode switching valve that is connected to the port and is switched to the other position by the pressure oil that passes through the sequence valve against the spring for switching to one position and selects the pressure increasing mode and the pressure increasing mode; It has a large-diameter drive oil chamber and a small-diameter pressure-increasing oil chamber that are connected to the outlet port of the pressure-increasing / increasing mode switching valve, and the pressure supplied and discharged via the distribution valve and the pressure-increasing / increasing mode switching valve. A pressure increasing cylinder driven by oil, a pressure increasing cylinder provided between a pressure increasing outlet port of the pressure increasing mode switching valve and a side of the hydraulic actuator where high pressure is required to supply oil to the hydraulic actuator. Direction that enables A hydraulic circuit characterized by having a sex check valve.
が一方の位置にあるときにその出口ポートからの圧油で
駆動される油圧モータにより減速機を介して回転される
回転型パイロット弁を設けたことを特徴とする請求項１
記載の油圧回路。2. As the pilot valve, a rotary pilot valve that is rotated through a speed reducer by a hydraulic motor driven by pressure oil from the outlet port of the pressure oil take-out switching valve when the switching valve is in one position. It is provided, The claim 1 characterized by the above-mentioned.
Hydraulic circuit described.
油室に対しメイクアップポンプがチェック弁を介し接続
されたことを特徴とする請求項１記載の油圧回路。3. The hydraulic circuit according to claim 1, wherein a makeup pump is connected to the drive oil chamber and the pressure increasing oil chamber of the pressure increasing cylinder by a check valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6228255A JPH0893708A (en) | 1994-09-22 | 1994-09-22 | Hydraulic circuit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6228255A JPH0893708A (en) | 1994-09-22 | 1994-09-22 | Hydraulic circuit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0893708A true JPH0893708A (en) | 1996-04-09 |
Family
ID=16873606
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6228255A Withdrawn JPH0893708A (en) | 1994-09-22 | 1994-09-22 | Hydraulic circuit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0893708A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007298073A (en) * | 2006-04-28 | 2007-11-15 | Hokuto Kenki Service Kk | Hydraulic driving unit, and pinching treatment device equipped with it |
| JP2007298072A (en) * | 2006-04-28 | 2007-11-15 | Hokuto Kenki Service Kk | Hydraulic drive unit, and pinching treatment device equipped with it |
| JP2012067917A (en) * | 2011-09-30 | 2012-04-05 | Hokuto Kenki Service Kk | Hydraulic drive device, and pinching treatment apparatus with the same |
| KR101497976B1 (en) * | 2013-07-30 | 2015-03-03 | 군산대학교산학협력단 | Automatic reciprocating motion control device for reciprocatable double acting booster |
| CN107061385A (en) * | 2015-10-02 | 2017-08-18 | 林德液压两合公司 | The fluid pressure type constant pressure system of mobile work machines |
| CN107745020A (en) * | 2017-11-16 | 2018-03-02 | 安徽德系重工科技有限公司 | A kind of hydraulic system of four-roller ripple veneer reeling machine |
| CN110005648A (en) * | 2019-04-08 | 2019-07-12 | 浙江大学 | A kind of pressure stabilizing hydraulic circuit based on marine tidal-current energy generator group |
| CN113883130A (en) * | 2021-05-08 | 2022-01-04 | 山东金利液压科技有限公司 | Manufacturing method of oil cylinder simulation test combined experiment platform |
-
1994
- 1994-09-22 JP JP6228255A patent/JPH0893708A/en not_active Withdrawn
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007298073A (en) * | 2006-04-28 | 2007-11-15 | Hokuto Kenki Service Kk | Hydraulic driving unit, and pinching treatment device equipped with it |
| JP2007298072A (en) * | 2006-04-28 | 2007-11-15 | Hokuto Kenki Service Kk | Hydraulic drive unit, and pinching treatment device equipped with it |
| JP2012067917A (en) * | 2011-09-30 | 2012-04-05 | Hokuto Kenki Service Kk | Hydraulic drive device, and pinching treatment apparatus with the same |
| KR101497976B1 (en) * | 2013-07-30 | 2015-03-03 | 군산대학교산학협력단 | Automatic reciprocating motion control device for reciprocatable double acting booster |
| CN107061385A (en) * | 2015-10-02 | 2017-08-18 | 林德液压两合公司 | The fluid pressure type constant pressure system of mobile work machines |
| CN107745020A (en) * | 2017-11-16 | 2018-03-02 | 安徽德系重工科技有限公司 | A kind of hydraulic system of four-roller ripple veneer reeling machine |
| CN107745020B (en) * | 2017-11-16 | 2023-08-01 | 安徽德系重工科技有限公司 | Hydraulic system of four-roller corrugated plate bending machine |
| CN110005648A (en) * | 2019-04-08 | 2019-07-12 | 浙江大学 | A kind of pressure stabilizing hydraulic circuit based on marine tidal-current energy generator group |
| CN110005648B (en) * | 2019-04-08 | 2020-08-18 | 浙江大学 | Pressure stabilizing hydraulic circuit based on tidal current energy generator set |
| CN113883130A (en) * | 2021-05-08 | 2022-01-04 | 山东金利液压科技有限公司 | Manufacturing method of oil cylinder simulation test combined experiment platform |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4833971A (en) | Self-regulated hydraulic control system | |
| US6715403B2 (en) | Independent and regenerative mode fluid control system | |
| US5048292A (en) | Dual pump traverse and feed system | |
| JPS6344513B2 (en) | ||
| JPH05272464A (en) | On-off high pressure cutoff control system | |
| JPH0893708A (en) | Hydraulic circuit | |
| KR102482814B1 (en) | Hydraulic systems for construction machinery | |
| US6050091A (en) | Brake device for oil hydraulic motor | |
| US6758128B2 (en) | Hydraulic circuit for working machine | |
| JPS6058338B2 (en) | Construction machinery engine control device | |
| US20180119389A1 (en) | Hydraulic Systems for Construction Machinery | |
| JPH0755031A (en) | Directional control valve for flow rate assistance | |
| JPH07127601A (en) | Intensifying circuit for oil pressure | |
| US3579986A (en) | Device for controlling pumps for operating hydraulic motors equipment | |
| US20040000142A1 (en) | High-pressure and low-pressure selecting valve and swash-plate type hydraulic motor system | |
| US6701822B2 (en) | Independent and regenerative mode fluid control system | |
| JP2001027206A (en) | Control device for hydraulic actuator | |
| JP4901291B2 (en) | Hydraulic drive device and pinch processing device equipped with the same | |
| JPS59226288A (en) | Hydraulic pressure operating device of piston pump for sending fluid body by pressure | |
| JPS6225529B2 (en) | ||
| JPH11148463A (en) | Capacity control device for hydraulic pump | |
| JP5211216B2 (en) | Hydraulic drive device and pinch processing device equipped with the same | |
| JP3143773B2 (en) | Concrete pumping equipment | |
| JPS62297508A (en) | Boost controlled cylinder device | |
| RU2219379C2 (en) | Grain harvester hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Withdrawal of application because of no request for examination |
Free format text: JAPANESE INTERMEDIATE CODE: A300 Effective date: 20020115 |