JP3396728B2 - Speed-up valve unit for work equipment grip device - Google Patents
Speed-up valve unit for work equipment grip deviceInfo
- Publication number
- JP3396728B2 JP3396728B2 JP05227794A JP5227794A JP3396728B2 JP 3396728 B2 JP3396728 B2 JP 3396728B2 JP 05227794 A JP05227794 A JP 05227794A JP 5227794 A JP5227794 A JP 5227794A JP 3396728 B2 JP3396728 B2 JP 3396728B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- oil passage
- hydraulic cylinder
- valve unit
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Operation Control Of Excavators (AREA)
- Working Measures On Existing Buildindgs (AREA)
- Fluid-Pressure Circuits (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、作業機械例えば油圧シ
ョベルなどの建設車両へ装着して、木材などを挾持した
り、コンクリート製ブロックなどを挾持・破砕するグリ
ップ装置の開閉動作を短時間にショックレスに行うよう
にした増速弁ユニットに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is capable of quickly opening and closing a grip device mounted on a construction machine such as a work machine such as a hydraulic excavator to hold wood or to hold and crush concrete blocks. The present invention relates to a speed increasing valve unit designed to be shockless.
【０００２】[0002]
【従来の技術】油圧ショベルなどで木材などを移載する
には力強く確実に挾持する必要がある。またコンクリー
トブロックなどを破砕するには極めて大きな挾持力を必
要とする。したがって、これらのグリップ装置に用いら
れる油圧シリンダは大径となり、単純な油圧回路では迅
速な動作のためには油圧源からの大流量を必要とする。
しかし、これらのグリップ装置において強大な出力を必
要とするのは、グリップ装置の爪あるいはアームが被挾
持物を確実に挾持してからであり、その前の挾持が終わ
るまでは油圧シリンダとしては低負荷といえる。この点
に着目した増速弁ユニットとして、実公平５−４０１２
６号公報に記載された図１３、図１４に示すような装置
がある。2. Description of the Related Art In order to transfer wood or the like on a hydraulic excavator or the like, it is necessary to firmly and firmly hold it. In addition, crushing concrete blocks and the like requires an extremely large holding force. Therefore, the hydraulic cylinders used in these grip devices have a large diameter, and a simple hydraulic circuit requires a large flow rate from the hydraulic source for quick operation.
However, in these grip devices, a strong output is required only after the claws or arms of the grip devices securely hold the object to be held, and the hydraulic cylinder is low until the previous holding is completed. It can be said to be a load. As a speed increasing valve unit focusing on this point,
There is a device as shown in FIG. 13 and FIG.
【０００３】図１３の増速弁ユニット５０では、油圧シ
リンダ１のロッド側油室２に接続した油路４とヘッド側
油室３に接続した油路５とを連通する合流用のバイパス
油路５１に低圧側圧力調整弁５２と逆止弁５３をシリー
ズに設けていることから、合流増速時に主に低圧側圧力
調整弁５２の流路抵抗によってバイパス油路５１の油の
流れが悪くなり、増速効果が十分でないという問題があ
った。図中、６は切替弁、７は油圧ポンプ、８はタン
ク、５４、５５は油路４に並列に設けられた高圧側圧力
調整弁と逆止弁である。In the speed increasing valve unit 50 of FIG. 13, a bypass bypass oil passage for connecting an oil passage 4 connected to the rod side oil chamber 2 of the hydraulic cylinder 1 and an oil passage 5 connected to the head side oil chamber 3 to each other. Since the low pressure side pressure adjusting valve 52 and the check valve 53 are provided in series in 51, the flow of oil in the bypass oil passage 51 is deteriorated mainly due to the flow passage resistance of the low pressure side pressure adjusting valve 52 at the time of merging and accelerating. However, there was a problem that the speed-up effect was not sufficient. In the figure, 6 is a switching valve, 7 is a hydraulic pump, 8 is a tank, and 54 and 55 are high pressure side pressure regulating valves and check valves provided in parallel with the oil passage 4.
【０００４】図１４の増速弁ユニット６０では、合流用
のバイパス油路６１にパイロット切り替え式のスプール
弁６２とさらに逆止弁６３が設けられており、流量確保
のためにこれらは比較的大形の逆止弁と大径のスプール
となっている。図中、６４はシャトル弁、６５は圧力調
整弁、６６は逆止弁である。しかし、このような構造で
は、スプールの摺動性を良くするためスプールを収納す
るブロック６７は例えば鋳鉄製となり、また摺動孔の加
工は精密に行わなければならず、重く、大きく、高価に
なる欠点があった。さらに低圧損の防止のためスプール
は大径でかつ長いストロークとなり、そのため応答が遅
く、また差動切り替えのタイミング調整が難しく、ショ
ックが大きかった。またスプールのカジリなどの事故の
場合の修理では高価なブロックの交換もあり、重く、大
きいことからサービス性がよくなかった。In the speed increasing valve unit 60 of FIG. 14, a pilot switching spool valve 62 and a check valve 63 are provided in a bypass oil passage 61 for merging, and these are relatively large in order to secure a flow rate. Shape check valve and large diameter spool. In the figure, 64 is a shuttle valve, 65 is a pressure adjusting valve, and 66 is a check valve. However, in such a structure, the block 67 for accommodating the spool is made of, for example, cast iron in order to improve the slidability of the spool, and the processing of the sliding hole must be performed precisely, which is heavy, large, and expensive. There was a drawback. Furthermore, in order to prevent low pressure loss, the spool has a large diameter and a long stroke, which slows the response and makes it difficult to adjust the timing of differential switching, resulting in a large shock. Also, in the case of an accident such as a scraping of a spool, expensive blocks have to be replaced, and since it is heavy and large, serviceability is poor.
【０００５】また、本出願人はグリップ装置の一つであ
る、破砕機として、実願平４−７７０９２号において図
１５に示すような増速弁ユニット７０の例を提案した。Further, the present applicant has proposed an example of a speed increasing valve unit 70 as shown in FIG. 15 in Japanese Patent Application No. 4-77092 as a crusher which is one of grip devices.
【０００６】この増速弁ユニット７０は、油圧シリンダ
１のロッド側油室２に接続した油路４に逆止弁７１と開
閉弁７２を並列に設け、油路４と油路５を連通する合流
用のバイパス油路７３にロジック弁からなる開閉弁７４
を設け、この開閉弁７４の作動制御のために、油路５の
パイロット油路７５の途中に検知弁７６とシャトル弁７
７を設けたものである。In this speed increasing valve unit 70, a check valve 71 and an on-off valve 72 are provided in parallel in an oil passage 4 connected to the rod-side oil chamber 2 of the hydraulic cylinder 1 so that the oil passage 4 and the oil passage 5 communicate with each other. An on-off valve 74 consisting of a logic valve in the bypass oil passage 73 for merging
A control valve is provided in the middle of the pilot oil passage 75 of the oil passage 5 for controlling the operation of the opening / closing valve 74.
7 is provided.
【０００７】この増速弁ユニット７０の動作の概要を説
明する。グリップ装置の開動作すなわち油圧シリンダ１
のロッド引き込み動作は切替弁６を左方へ切り替えるこ
とにより、圧油が油路４の逆止弁７１を経由して油圧シ
リンダ１のロッド側油室２に流入し、ヘッド側油室３か
らは油が排出される。開閉弁７４はパイロット油路７８
からシャトル弁７７を経由した供給側圧力が作用し閉鎖
されているので、油圧シリンダ１のピストンロッド１１
は高速で引き込まれる。なおここで、２個の圧力調整弁
すなわち、検知弁７６と開閉弁７２とが差動切り替えを
スムーズに行うために設定圧力が調整されている。例え
ば油圧源の設定圧力が２００ｋｇｆ／ｃｍ2 の場合、差
動切り替えを１５０ｋｇｆ／ｃｍ2 で行う場合には検知
弁７６の設定圧力を１５０ｋｇｆ／ｃｍ2、開閉弁７２
の設定圧力をそれよりやや低い値の１４５ｋｇｆ／ｃｍ
2 に設定される。The outline of the operation of the speed increasing valve unit 70 will be described. Opening operation of the grip device, that is, the hydraulic cylinder 1
In the rod retraction operation, the switching valve 6 is switched to the left, whereby the pressure oil flows into the rod side oil chamber 2 of the hydraulic cylinder 1 via the check valve 71 in the oil passage 4, and from the head side oil chamber 3. Oil is drained. The on-off valve 74 is a pilot oil passage 78.
Since the supply side pressure from the shuttle valve 77 acts to close the piston rod 11 of the hydraulic cylinder 1,
Is drawn in at high speed. Here, the set pressure is adjusted so that the two pressure adjusting valves, that is, the detection valve 76 and the opening / closing valve 72 smoothly perform the differential switching. For example, when the set pressure of the hydraulic source of 200kgf / cm 2, 150kgf / cm 2 the set pressure of the sensing valve 76 when performing differential switch with 150 kgf / cm 2, on-off valve 72
145kgf / cm which is a little lower than the set pressure of
Set to 2 .
【０００８】油圧シリンダ１のロッド突き出し動作で
は、まず圧油が油路５からヘッド側油室３に流入する。
この時、油圧シリンダ１のピストンロッド１１ではグリ
ップ装置の爪あるいは挾持アームが被挾持物を挾持しき
っていないので、低負荷状態にある。したがって、油路
５の圧力は低く、検知弁７６、開閉弁７２ともに切り替
わっておらず、開閉弁７４のパイロットポート７４Ｐは
シャトル弁７７を介してタンク８に連通し、開閉弁７４
は全開状態にあり、油路４と油路５とを連通状態とす
る、いわゆる差動状態となり、ピストンロッド１１を高
速で突き出す。そしてグリップ装置の爪あるいは挾持ア
ームが被挾持物を挟むと、開閉弁７４を開いたまま、油
路４、油路５の圧力は上昇していく。そしてその圧力が
まず開閉弁７２の設定圧力１４５ｋｇｆ／ｃｍ2 になる
と開閉弁７２が開き、ロッド側油室２から圧油の排出を
始め、ついで１５０ｋｇｆ／ｃｍ2 になると検知弁７６
が切り替わり、シャトル弁７７を経由して開閉弁７４を
閉鎖し、差動動作を解除する。そして開閉弁７２からの
圧抜きと開閉弁７４による差動の解除は開閉弁７２、検
知弁７６の圧力調整により行われる。In the rod ejecting operation of the hydraulic cylinder 1, first, pressure oil flows from the oil passage 5 into the head side oil chamber 3.
At this time, in the piston rod 11 of the hydraulic cylinder 1, the claw of the grip device or the holding arm does not hold the object to be held, so that the load is low. Therefore, the pressure in the oil passage 5 is low, neither the detection valve 76 nor the opening / closing valve 72 has been switched, and the pilot port 74P of the opening / closing valve 74 communicates with the tank 8 via the shuttle valve 77.
Is in a fully opened state, and is in a so-called differential state in which the oil passage 4 and the oil passage 5 are in communication with each other, and the piston rod 11 is ejected at high speed. Then, when the claw of the grip device or the holding arm sandwiches the object to be held, the pressures of the oil passages 4 and 5 increase with the opening / closing valve 74 kept open. When the pressure reaches the set pressure 145 kgf / cm 2 of the on-off valve 72, the on-off valve 72 opens, the pressure oil starts to be discharged from the rod side oil chamber 2, and when it reaches 150 kgf / cm 2 , the detection valve 76
, The on-off valve 74 is closed via the shuttle valve 77, and the differential operation is released. The pressure release from the on-off valve 72 and the differential release by the on-off valve 74 are performed by adjusting the pressures of the on-off valve 72 and the detection valve 76.
【０００９】しかしながら、開閉弁７２、検知弁７６の
圧力設定値はかなり近寄っており、かつ両者の差が切り
替え動作に大きく影響する。例えば開閉弁７２の設定圧
力を検知弁７６より少し高くしてしまうと、開閉弁７２
が開く前に開閉弁７４が閉じてしまうことになり、ロッ
ド側油室２は油圧シリンダ１の面積差により増圧され、
ついで開閉弁７２が開くこと、そしてこのシステムでは
油路５の圧力はますます上昇していくので、開閉弁７２
は加速度的に開き、急激かつ大きな圧抜きとなるため、
大きなショック音を発生してしまう。However, the pressure set values of the on-off valve 72 and the detection valve 76 are very close to each other, and the difference between the two greatly affects the switching operation. For example, if the set pressure of the open / close valve 72 is made slightly higher than the detection valve 76, the open / close valve 72
The on-off valve 74 will be closed before the open position, and the rod-side oil chamber 2 is increased in pressure due to the area difference of the hydraulic cylinder 1.
Then the on-off valve 72 opens, and in this system, the pressure in the oil passage 5 rises more and more, so the on-off valve 72
Opens at an accelerating rate, resulting in rapid and large pressure relief.
A loud shock noise is generated.
【００１０】逆に、開閉弁７２の設定圧力を最適状態よ
り低く設定してしまうと、早めに圧抜きが始まってしま
い、開閉弁７４が開いているので、そこから油圧シリン
ダ１をバイパスすることになり、油圧源からの１００％
の流量が差動動作の突き出し速度にならず、速度が低下
する。また開閉弁７２の設定圧力を更に低くすると、検
知弁７６の切り替え圧力に達する前に、ポンプ流量はそ
の全量が開閉弁７４を経由して開閉弁７２から流出して
しまい、差動が解除されないという現象が起きる。すな
わち両者の差の許容値が非常に小さく、条件が少し変わ
ると、ショック等の不具合現象が発生するという問題が
あった。On the other hand, if the set pressure of the on-off valve 72 is set lower than the optimum state, depressurization will start early and the on-off valve 74 will be open, so the hydraulic cylinder 1 should be bypassed from there. Becomes 100% from the hydraulic source
The flow rate does not become the protruding speed of the differential operation, and the speed decreases. Further, if the set pressure of the opening / closing valve 72 is further lowered, the entire pump flow rate will flow out of the opening / closing valve 72 via the opening / closing valve 74 before the switching pressure of the detection valve 76 is reached, and the differential will not be released. The phenomenon occurs. That is, there is a problem that the allowable value of the difference between the two is very small, and if the conditions are slightly changed, a trouble phenomenon such as a shock occurs.
【００１１】また、被挾持物が変われば、油圧源の供給
圧力とともに差動切り替え圧力も変えなければならず、
そのたびに非常に苦労して設定圧力の調整をしていた。Further, if the object to be held changes, the supply pressure of the hydraulic source and the differential switching pressure must be changed,
Every time, I had a very hard time adjusting the set pressure.
【００１２】[0012]
【発明が解決しようとする課題】本発明は、上記のよう
な問題点を解決するためになされたもので、急激な圧抜
きを防止するとともに、差動動作中は検知弁の設定圧力
ぎりぎりまでポンプ流量を差動状態で送り込むように
し、圧力調整の容易さと、多少条件が変わっても、動作
の変わらない安定性・応答性の高い増速弁ユニットを提
供することを目的とする。本発明の他の目的は、シンプ
ルな油圧回路とするとともに、小型・軽量とし、グリッ
プ装置の大から小まで適用範囲の拡大を可能にした増速
弁ユニットを提供することにある。SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and prevents sudden depressurization, and during the differential operation, up to the set pressure of the detection valve. An object of the present invention is to provide a speed increasing valve unit which is configured to send a pump flow rate in a differential state, has an easy pressure adjustment, and has a stable operation and a high responsiveness that does not change even if conditions are changed a little. Another object of the present invention is to provide a speed increasing valve unit which has a simple hydraulic circuit, is small and lightweight, and can be applied to a wide range of small and large grip devices.
【００１３】[0013]
【課題を解決するための手段】本発明に係る作業機械の
グリップ装置用増速弁ユニットは、作業機械のグリップ
装置を開閉駆動する油圧シリンダと該油圧シリンダの操
作用切替弁との間に接続される増速弁ユニットにおい
て、前記油圧シリンダのロッド側油室に通じるロッド側
油路に設けられた、該油室に向かってのみ流れを許す逆
止弁と、前記逆止弁と並列に接続された圧抜き弁と、前
記逆止弁より下流側の前記ロッド側油路と前記油圧シリ
ンダのヘッド側油室に通じるヘッド側油路とを連通させ
るバイパス油路に設けられたパイロット操作形の開閉弁
と、前記ヘッド側油路のパイロット油路に設けられ、前
記圧抜き弁より高い圧力設定値を有する検知弁と、前記
検知弁の開動作時の出力接続口と前記開閉弁のパイロッ
ト接続口を接続した油路と、前記検知弁の閉動作時の出
力接続口と前記逆止弁より上流側の前記ロッド側油路を
接続した油路と、を備え、 前記圧抜き弁が絞りであるこ
とを特徴とする。A speed increasing valve unit for a grip device of a working machine according to the present invention is connected between a hydraulic cylinder for driving a grip device of a working machine to open and close and a switching valve for operating the hydraulic cylinder. In the speed increasing valve unit, a check valve provided in a rod-side oil passage communicating with the rod-side oil chamber of the hydraulic cylinder and allowing a flow only toward the oil chamber is connected in parallel with the check valve. Of the pilot-operated type provided in the bypass oil passage that connects the pressure release valve, the rod-side oil passage downstream of the check valve, and the head-side oil passage communicating with the head-side oil chamber of the hydraulic cylinder. An on-off valve, a detection valve provided in the pilot oil passage of the head side oil passage and having a higher pressure setting value than the pressure relief valve, an output connection port at the time of opening operation of the detection valve, and a pilot connection of the on-off valve Connected mouth Comprising a road, and a fluid passage connecting the upstream side the rod side oil passage than the check valve and the output connection port during closing operation of the sensing valve, this said depressurization valves is squeezed <br / > And.
【００１４】圧抜き弁は絞りのみで構成するか、または
絞りとパイロット操作形の第２の開閉弁とをシリーズに
接続した構成とし、該第２の開閉弁のパイロット接続口
を前記開閉弁（第１の開閉弁）のパイロット接続口に接
続した構成とする。The pressure relief valve is composed of only a throttle, or the throttle and a pilot operated second on-off valve are connected in series, and the pilot connection port of the second on-off valve is the on-off valve ( The first opening / closing valve) is connected to the pilot connection port.
【００１５】また、検知弁の圧力設定値に対し、第２の
開閉弁の圧力設定値を３／４以下とする。さらに、第１
の開閉弁はシート形する。Further, the pressure set value of the second on-off valve is set to 3/4 or less of the pressure set value of the detection valve. Furthermore, the first
The on-off valve is a seat type.
【００１６】本発明の増速弁ユニットは、ブロックを有
し、該ブロックに前記の各々の弁をねじ込みやカバー止
め挿入方式などの挿入式ユニット形で構成する。また、
ブロックの材質は軽量かつ高強度のアルミ合金もしくは
エンジニアリングプラスチックまたはチタンとする。The speed increasing valve unit of the present invention has a block, and each of the above valves is formed in an insertion type unit type such as a screwing type or a cover fixing insertion type. Also,
The material of the block is lightweight and high strength aluminum alloy or engineering plastic or titanium.
【００１７】[0017]
【作用】本発明においては、１個の圧力検知弁でパイロ
ット操作形の第１の開閉弁の差動切り替えを行い、圧抜
きは絞り（可変絞りでも固定絞りでも良い）にて徐々に
行わせることで、急激な圧抜きを防止し、差動動作中は
検知弁の設定圧力ぎりぎりまでポンプ流量を差動状態で
送り込むようにしている。In the present invention, the differential switching of the pilot operated first on-off valve is performed by one pressure detection valve, and the pressure release is gradually performed by the throttle (variable throttle or fixed throttle may be used). This prevents sudden pressure relief, and during differential operation, the pump flow rate is sent in a differential state up to the set pressure of the detection valve.
【００１８】また、検知弁の圧力設定値は、圧抜き弁ま
たは圧抜き弁を構成する第２の開閉弁に比べて大幅に高
いため、圧力の調整が容易である。Further, since the pressure set value of the detection valve is much higher than that of the pressure relief valve or the second on-off valve which constitutes the pressure relief valve, the pressure can be easily adjusted.
【００１９】第１の開閉弁をシート形することで、油圧
シリンダの差動動作時における大流量の開閉をスムーズ
に行い、開閉動作が安定するとともに応答性が向上す
る。By forming the first opening / closing valve in a seat shape, a large flow rate is smoothly opened / closed during the differential operation of the hydraulic cylinder, the opening / closing operation is stabilized, and the responsiveness is improved.
【００２０】また、本増速弁ユニットを構成する各々の
弁を挿入式のユニット形とすることで、交換や取扱いが
容易となり、ブロックの軽量・小型化も可能になる。Further, since each valve constituting the speed increasing valve unit is of an insertable unit type, replacement and handling are facilitated, and the block can be made lightweight and compact.
【００２１】[0021]
【実施例】以下、本発明の実施例を図に従って説明す
る。Embodiments of the present invention will be described below with reference to the drawings.
【００２２】（実施例１）図１は本発明の実施例１に係
る増速弁ユニットの油圧回路図である。本実施例の増速
弁ユニット２０は、油圧シリンダ１のロッド側油室２に
切替弁６を介して接続したロッド側油路４に、ロッド側
油室２に向かってのみ圧油の流れを許す逆止弁２１を設
け、逆止弁２１と並列に、絞り２２と第２の開閉弁２３
をシリーズに接続した構成からなる圧抜き弁２４を設
け、油圧シリンダ１のヘッド側油室３に接続したヘッド
側油路５と逆止弁２１より下流側の油路４ｂとを合流用
のバイパス油路２５で接続し、このバイパス油路２５に
ロジック弁からなるパイロット操作形の第１の開閉弁２
６を設け、油路５に接続したパイロット油路２７に第２
の開閉弁２３より圧力設定値の高い検知弁２８を設け、
検知弁２８の開動作時の出力ポート２８ａと第１の開閉
弁２６のパイロットポート２６Ｐを油路２９で接続し、
また検知弁２８の閉動作時の出力ポート２８ｂを逆止弁
２１より上流側の油路４ａに油路３０で接続し、油路２
９と第２の開閉弁２３のパイロットポート２３Ｐを油路
３１で接続する構成としたものである。図中、１０は油
圧ポンプ７、タンク８からなる油圧源、Ｃ1 、Ｃ2 は増
速弁ユニット２０を構成するブロック３５と油圧シリン
ダ１との接続口、Ｖ1 、Ｖ2 はブロック３５と切替弁６
との接続口である。(Embodiment 1) FIG. 1 is a hydraulic circuit diagram of a speed increasing valve unit according to Embodiment 1 of the present invention. The speed increasing valve unit 20 of the present embodiment allows the flow of pressure oil only toward the rod side oil chamber 2 in the rod side oil passage 4 connected to the rod side oil chamber 2 of the hydraulic cylinder 1 via the switching valve 6. A non-return valve 21 is provided, and the throttle 22 and the second on-off valve 23 are provided in parallel with the non-return valve 21.
Is provided in series to connect the head side oil passage 5 connected to the head side oil chamber 3 of the hydraulic cylinder 1 and the oil passage 4b downstream of the check valve 21 to a bypass for merging. The pilot-operated first on-off valve 2 which is connected by an oil passage 25, and is composed of a logic valve in the bypass oil passage 25
6 is provided and the pilot oil passage 27 connected to the oil passage 5 is provided with a second
A detection valve 28 having a higher pressure setting value than the open / close valve 23 of
The output port 28a at the time of opening operation of the detection valve 28 and the pilot port 26P of the first on-off valve 26 are connected by an oil passage 29,
Further, the output port 28b during the closing operation of the detection valve 28 is connected to the oil passage 4a upstream of the check valve 21 by the oil passage 30, and the oil passage 2
9 and the pilot port 23P of the second on-off valve 23 are connected by the oil passage 31. In the figure, 10 is a hydraulic pressure source consisting of a hydraulic pump 7 and a tank 8, C1 and C2 are connection ports between the block 35 and the hydraulic cylinder 1 that constitute the speed increasing valve unit 20, and V1 and V2 are blocks 35 and a switching valve 6.
It is a connection port with.
【００２３】図２は油圧ショベル４０における上記の各
要素１、２０、６、１０の搭載位置を示す概要図で、増
速弁ユニット２０はブーム４１の先端のグリップ装置４
２に装着されている。４４、４５はそれぞれ油路４、５
の一部を構成するホースである。増速弁ユニット２０の
取付位置は、差動動作からの切り替えを速やかに行うに
は応答性を遅らせる大きな要因である圧縮性の影響を小
さくするため容積を最小にするように、油圧シリンダ以
外に無駄な容積を持ちたくないということから、増速弁
ユニット２０はグリップ装置４２に取り付けられ、この
図の例では増速弁ユニット２０と油圧シリンダ１とは最
短長さのホース４４，４５で接続することとしている。FIG. 2 is a schematic view showing the mounting positions of the above-mentioned respective elements 1, 20, 6, 10 in the hydraulic excavator 40. The speed increasing valve unit 20 is a grip device 4 at the tip of the boom 41.
It is attached to 2. 44 and 45 are oil passages 4 and 5, respectively
Is a hose that forms part of the. The mounting position of the speed increasing valve unit 20 is not limited to that of the hydraulic cylinder so that the volume is minimized in order to reduce the influence of the compressibility, which is a major factor that delays the responsiveness in order to quickly switch from the differential operation. The speed increasing valve unit 20 is attached to the grip device 42 because it does not want to have a wasteful volume, and in the example of this figure, the speed increasing valve unit 20 and the hydraulic cylinder 1 are connected by hoses 44 and 45 of the shortest length. I am going to do it.
【００２４】切替弁６は操作者の近くに置かれるのが一
般的であり、したがって切替弁６と増速弁ユニット２０
との距離は比較的離れており、図示しないホースで接続
される。切替弁６は電磁式あるいは手動式のいずれでも
良い。The switching valve 6 is generally placed near the operator, and therefore the switching valve 6 and the speed increasing valve unit 20 are arranged.
Are relatively distant from each other and are connected by a hose (not shown). The switching valve 6 may be either an electromagnetic type or a manual type.
【００２５】図３〜図７は増速弁ユニット２０の動作を
より明瞭化するため各動作時毎の各弁の状態を示す説明
図である。また図１の油圧回路における各弁の構造の概
要を示している。なお、各弁の形状は後記するごとく外
形部においてネジ部を有し、増速弁ユニット装着用のブ
ロックにねじ込んで収納している。3 to 7 are explanatory views showing the state of each valve at each operation in order to clarify the operation of the speed increasing valve unit 20. Further, an outline of the structure of each valve in the hydraulic circuit of FIG. 1 is shown. As will be described later, the shape of each valve has a threaded portion in the outer shape, and is screwed into a block for mounting the speed increasing valve unit to be housed.
【００２６】図３は停止状態を示し、例えば後記の図７
の油圧シリンダ１の戻り動作完了後からの停止状態であ
る。図７に対しては逆止弁２１が閉じている点が異な
る。FIG. 3 shows a stopped state, for example, FIG. 7 described later.
It is a stopped state after the return operation of the hydraulic cylinder 1 is completed. 7 is different from FIG. 7 in that the check valve 21 is closed.
【００２７】グリップ装置４２としての開閉動作は次の
動作が連続して行われる。停止（グリップ装置の開状
態、図３）→差動による閉じ動作（図４）→差動から圧
砕への移行動作（図５）→差動動作の解除（図５）→強
挾持動作（図６）→（圧砕）→グリップ装置の開き動作
（図７）操作者は開、閉、停止の３操作を行う。The opening and closing operations of the grip device 42 are performed as follows. Stop (open state of grip device, Fig. 3) → Closing motion by differential (Fig. 4) → Transition motion from differential to crushing (Fig. 5) → Release of differential motion (Fig. 5) → Strong holding motion (Fig. 6) → (crushing) → grip device opening operation (FIG. 7) The operator performs three operations of opening, closing, and stopping.
【００２８】本実施例の増速弁ユニット２０は、図４の
差動動作や図７の開き動作が操作者の切り替え動作に遅
れなく速やかに追従し、図４〜図６の油路内圧力により
自動的に行われる切り替えは、油圧システム的に速やか
に、ショックレスに行うことを可能にしたものである。In the speed increasing valve unit 20 of this embodiment, the differential operation of FIG. 4 and the opening operation of FIG. 7 quickly follow the switching operation of the operator without delay, and the pressure in the oil passage of FIGS. The switching automatically performed by means of the hydraulic system can be performed promptly and shocklessly in terms of a hydraulic system.
【００２９】図４は差動状態であり、低負荷状態でのグ
リップ装置の閉じ動作を示す。この状態ではこの動作の
前が何であれ、またシステム的にどんな状態にあったと
しても低負荷（検知弁２８が切り替わらない状態）で切
替弁６が本図の状態ならば確実に油圧シリンダ１は直ち
に差動動作すなわち高速の突き出し動作を行う。FIG. 4 is a differential state and shows a closing operation of the grip device in a low load state. In this state, no matter what the state is before this operation, and even if the system is in any state, if the switching valve 6 is in the state shown in this figure with a low load (the state where the detection valve 28 does not switch), the hydraulic cylinder 1 can be reliably operated. Immediately, a differential operation, that is, a high speed ejection operation is performed.
【００３０】供給圧力は切替弁６を右方へ切り替えるこ
とにより油路５へ入り、油路４ａはタンク８に接続され
る。検知弁２８は油路２９、３０を、タンク８に連通し
ている油路４ａに接続させるので、第１の開閉弁２６は
油路５および油路４ｂの圧力により全開し、油路４ｂと
油路５とはバイパス路２５により連通する。したがっ
て、ロッド側油室２からの排出油は白抜きの矢印ｂで示
すごとく全量、ヘッド側油室３に流入し、油圧源１０か
らの供給流量（白抜きの矢印ａ）と合算してヘッド側油
室３に流入する。いわゆる差動動作である。この差動動
作は検知弁２８が切り替わらない高圧（設定圧力）に至
るまで継続される。The supply pressure enters the oil passage 5 by switching the switching valve 6 to the right, and the oil passage 4a is connected to the tank 8. Since the detection valve 28 connects the oil passages 29 and 30 to the oil passage 4a communicating with the tank 8, the first opening / closing valve 26 is fully opened by the pressure of the oil passage 5 and the oil passage 4b, and the oil passage 4b and the oil passage 4b. A bypass 25 communicates with the oil passage 5. Therefore, the total amount of the oil discharged from the rod-side oil chamber 2 flows into the head-side oil chamber 3 as shown by the outlined arrow b, and is summed with the flow rate supplied from the hydraulic power source 10 (the outlined arrow a) to produce the head. It flows into the side oil chamber 3. This is so-called differential operation. This differential operation is continued until the detection valve 28 reaches a high pressure (set pressure) at which it does not switch.
【００３１】本実施例における第１の開閉弁２６はシー
トとポペット円錐面とにより開閉動作を行ういわゆるロ
ジック弁であるため、開動作はスプール弁に見られるよ
うなオーバラップ分の無駄時間や、スプール弁であるた
めの弁内油路狭さの問題からどうしても大形になるこ
と、そして大形になると応答が遅くなることなどの問題
がなく、小型で大流量の開閉が高応答でできる。Since the first opening / closing valve 26 in this embodiment is a so-called logic valve that opens and closes by the seat and the conical surface of the poppet, the opening operation is a dead time for the overlap as seen in the spool valve, Since it is a spool valve, there is no problem that it becomes large due to the problem of the narrow oil passage in the valve, and when it becomes large, there is no problem such as slow response, and it is small and can open and close a large flow rate with high response.
【００３２】本実施例において、油圧源１０、検知弁２
８、第２の開閉弁２３の設定圧力をそれぞれ２００ｋｇ
ｆ／ｃｍ2 、１５０ｋｇｆ／ｃｍ2 、５０ｋｇｆ／ｃｍ
2 として、動作を説明する。In this embodiment, the hydraulic pressure source 10 and the detection valve 2
8, the set pressure of the second on-off valve 23 is 200 kg each
f / cm 2 , 150 kgf / cm 2 , 50 kgf / cm
The operation will be described as 2 .
【００３３】図５は差動動作から被挾持物の圧砕へ移行
する動作を示している。すなわち、グリップ装置４２の
爪あるいはアームが被挾持物を挟み始め、その反力が増
加する。しかし、油圧シリンダ１では第１の開閉弁２６
がまだ開いたままであるので油圧シリンダ１の両油室
２、３の圧力は同じ値で上昇していき、例えばその圧力
が検知弁２８の設定圧力１５０ｋｇｆ／ｃｍ2 に到達し
たとき検知弁２８が切り替わり、油路５の圧力が破線の
矢印ｃで示すごとくパイロット油路２７から油路２９に
流入し、油路２９の圧力を上昇させている状態である。FIG. 5 shows the operation of shifting from the differential operation to the crushing of the object to be held. That is, the claws or arms of the grip device 42 start to pinch the object to be held, and the reaction force thereof increases. However, in the hydraulic cylinder 1, the first opening / closing valve 26
Is still open, the pressure in both oil chambers 2 and 3 of the hydraulic cylinder 1 rises at the same value. For example, when the pressure reaches the set pressure of the detection valve 28 of 150 kgf / cm 2 , the detection valve 28 This is a state in which the pressure in the oil passage 5 is switched to flow from the pilot oil passage 27 into the oil passage 29 as shown by the dashed arrow c to increase the pressure in the oil passage 29.
【００３４】第２の開閉弁２３の設定圧力を検知弁２８
より低い値、例えば５０ｋｇｆ／ｃｍ2 にしておくと、
油路２９の圧力が５０ｋｇｆ／ｃｍ2 に至ったとき第２
の開閉弁２３が開くので、ロッド側油室２の圧油は油路
４ｂから絞り２２、第２の開閉弁２３を経由してタンク
８に徐々に排出される。一方、油路２９の圧力上昇は続
いており、その圧力が設定圧力１５０ｋｇｆ／ｃｍ2 を
超え、油路５と同圧に近づくことにより、またロッド側
油室２の圧力低下による第１の開閉弁２６における開き
力の減少により、スプリング力を含む閉鎖力が開き力に
打ち勝ち、第１の開閉弁２６が閉鎖する。これにより差
動動作を解除する。The set pressure of the second opening / closing valve 23 is detected by the detection valve 28.
If it is set to a lower value, for example 50 kgf / cm 2 ,
When the pressure in the oil passage 29 reaches 50 kgf / cm 2 , the second
Since the open / close valve 23 is opened, the pressure oil in the rod side oil chamber 2 is gradually discharged from the oil passage 4b to the tank 8 via the throttle 22 and the second open / close valve 23. On the other hand, the pressure in the oil passage 29 continues to rise, the pressure exceeds the set pressure of 150 kgf / cm 2 , approaches the same pressure as the oil passage 5, and the first opening / closing due to the pressure drop in the rod side oil chamber 2 also occurs. Due to the decrease in the opening force of the valve 26, the closing force including the spring force overcomes the opening force, and the first opening / closing valve 26 is closed. This cancels the differential operation.
【００３５】この差動動作において、被挾持物を挾持し
きるまでは、被挾持物が高負荷で変形しやすいもの、例
えば１５０ｋｇｆ／ｃｍ2 より少し低い圧力で変形が進
むものなら、１５０ｋｇｆ／ｃｍ2 の設定圧力に至らな
いので、挾持しきるまでは差動動作によるポンプ流量は
１００％（油圧源の設定圧力は２００ｋｇｆ／ｃｍ2な
ので、それまではポンプ流量は１００％油圧シリンダに
送られる）使った高速で変形する。被挾持物の変形が終
了して、圧力が１５０ｋｇｆ／ｃｍ2 に至ると上記のよ
うに差動動作は解除される。なお、最終的な油圧力は油
圧源１０の設定圧力２００ｋｇｆ／ｃｍ2 まで上昇す
る。[0035] In the differential operation, until partition pinching the object to be clamped object, which object to be clamped object tends to deform at high load, if for example 150 kgf / cm 2 than that progresses deformed slightly lower pressure, 150 kgf / cm 2 Since it does not reach the set pressure of 100%, the pump flow rate by differential operation is 100% until it is fully held (the set pressure of the hydraulic source is 200 kgf / cm 2, so the pump flow rate is 100% until that time is sent to the hydraulic cylinder). It transforms at high speed. When the deformation of the object to be held is completed and the pressure reaches 150 kgf / cm 2 , the differential operation is canceled as described above. The final hydraulic pressure rises to the set pressure of the hydraulic power source 10 of 200 kgf / cm 2 .
【００３６】図６は油圧力を１００％油圧シリンダ１か
ら出力する強挾持あるいは破砕状態を示す。FIG. 6 shows a strong holding or crushing state in which the hydraulic pressure is output from the hydraulic cylinder 1 at 100%.
【００３７】図７はグリップ装置４２の爪あるいはアー
ムの開き動作の状態図で、供給圧力は油路４ａから油路
３０、検知弁２８を経由して油路２９に入り、第１の開
閉弁２６を閉鎖している。したがって、油圧源１０から
の供給流量は１００％油圧シリンダ１に供給され、グリ
ップ装置４２の爪あるいはアームを高速で開く。そして
切替弁６が中立位置に戻されて油圧シリンダ１は停止
し、次の差動動作を待つ。FIG. 7 is a state diagram of the opening operation of the claws or arms of the grip device 42. The supply pressure enters the oil passage 29 from the oil passage 4a through the oil passage 30 and the detection valve 28, and the first opening / closing valve. 26 is closed. Therefore, the supply flow rate from the hydraulic pressure source 10 is supplied to the hydraulic cylinder 1 at 100%, and the claws or arms of the grip device 42 are opened at high speed. Then, the switching valve 6 is returned to the neutral position, the hydraulic cylinder 1 stops, and waits for the next differential operation.
【００３８】図８は本実施例の油圧シリンダにおける実
際の圧力変化の一例を示している。被挾持物は変形しに
くいものとし、数値例は上記と同じ場合である。Ａ点で
グリップ装置４２の爪あるいはアームが被挾持物を挟み
込み、油圧シリンダ１のヘッド側油室圧力ＰH とロッド
側油室圧力ＰR は同じ値で上昇していく。Ｂ点に至って
検知弁２８が切り替わり、油路２９に圧油が流入し、絞
り２２から徐々に圧抜きが始まり、このためロッド側油
室２の一部が絞り２２へ向かうことから圧力の上昇が一
瞬停滞し、ついでロッド側油室２の圧力ＰR は速やかに
タンク圧に至り、ヘッド側油室圧力ＰH は供給圧力に至
っている。すなわち、油圧シリンダ１の出力は（ヘッド
側油室断面積×ヘッド側油室圧力ＰH ）−（ロッド側油
室断面積×ロッド側油室圧力ＰR ）であるので、応答波
形からはサージ圧力の発生や途中停止などの無い速やか
な、かつ、スムーズな出力の変化が得られたことを示し
ている。FIG. 8 shows an example of the actual pressure change in the hydraulic cylinder of this embodiment. It is assumed that the object to be held is not easily deformed, and the numerical example is the same as above. At point A, the claw or arm of the grip device 42 sandwiches the object to be held, and the head side oil chamber pressure PH and the rod side oil chamber pressure PR of the hydraulic cylinder 1 rise at the same value. At the point B, the detection valve 28 is switched, the pressure oil flows into the oil passage 29, and the pressure is gradually released from the throttle 22. Therefore, a part of the rod-side oil chamber 2 moves toward the throttle 22 so that the pressure rises. For a moment, then the pressure PR in the rod-side oil chamber 2 quickly reaches the tank pressure, and the head-side oil chamber pressure PH reaches the supply pressure. That is, the output of the hydraulic cylinder 1 is (head-side oil chamber cross-sectional area x head-side oil chamber pressure PH)-(rod-side oil chamber cross-sectional area x rod-side oil chamber pressure PR). This indicates that a prompt and smooth output change without any occurrence or intermediate stop was obtained.
【００３９】本実施例に示す増速弁ユニット２０は、一
つの圧力検知弁２８にて２個の開閉弁２３、２６を開閉
させているが、差動切り替え機能にロジック形開閉弁２
６を用い、圧抜きの開閉弁２３の開きタイミングを開閉
弁２６とほぼ同時あるいはやや前に確実に行うようにす
るため、開閉弁２３の設定圧力を開閉弁２６が閉鎖する
圧力よりある程度低く設定したことにより達成した。ま
た、油路２９の圧力上昇はその容積が小さいため、立上
がりは速いが、開閉弁２３は圧力感知形なので設定圧力
に敏感に切り替わるので、開閉弁２６とのタイミングを
確実かつ容易に変更できる。例えば開閉弁２３の設定圧
力を極端に高くして検知弁２８の設定圧力に近くする
と、圧抜きと開閉弁２６の閉鎖がほぼ同時となってしま
い、場合によっては油圧シリンダ１は一瞬停止し、ロッ
ド側油室２の圧力は油圧シリンダ１の面積差による、増
圧作用で上昇し、ついで圧抜きが行われるため、油圧シ
リンダ１の動きは不連続的となり、また差動切り替えが
ショックを伴って行われる可能性がある。しかし、この
場合でもこの現象は極めて一瞬であり、実際上問題には
ならない。In the speed increasing valve unit 20 shown in this embodiment, the two on-off valves 23 and 26 are opened and closed by one pressure detection valve 28, but the logic type on-off valve 2 has a differential switching function.
In order to ensure that the opening timing of the on-off valve 23 for depressurization is performed almost simultaneously with or slightly before the on-off valve 26, the set pressure of the on-off valve 23 is set to be somewhat lower than the pressure at which the on-off valve 26 is closed. It was achieved by doing. Further, the rise in pressure of the oil passage 29 is small due to its small volume, but rises quickly, but since the on-off valve 23 is a pressure-sensitive type, it switches sensitively to the set pressure, so the timing with the on-off valve 26 can be changed reliably and easily. For example, if the set pressure of the open / close valve 23 is made extremely high and becomes close to the set pressure of the detection valve 28, depressurization and closing of the open / close valve 26 occur almost at the same time, and in some cases, the hydraulic cylinder 1 stops momentarily. The pressure in the rod-side oil chamber 2 rises due to the pressure-increasing action due to the area difference of the hydraulic cylinder 1, and then the pressure is released. Therefore, the movement of the hydraulic cylinder 1 becomes discontinuous, and the differential switching causes a shock. Could be done by However, even in this case, this phenomenon is extremely brief and does not pose a practical problem.
【００４０】開閉弁２３の設定圧力が極端に低い場合、
例えば１０ｋｇｆ／ｃｍ2 などのようなときには検知弁
２８そして開閉弁２３が切り替わった瞬間、絞り２２か
ら圧油の排出が行われ、まだ開いている開閉弁２６から
油圧シリンダ１をバイパスする流れが起きて、この流量
は油圧シリンダ１をバイパスすることになるので、油圧
シリンダ１の動きに貢献せず無駄になる。この無駄な流
れは開閉弁２６が閉鎖してしまえばなくなり、一瞬のも
のであるが、大形のグリップ装置用ではこの流量も大き
いので、ばかにならない。したがって、開閉弁２３の設
定圧力は適度の値に設定される。実験によれば、この設
定圧力は上記のとおり、検知弁２８の設定圧力の３／４
程度以下のかなり広い設定域で使用できるが、１／２〜
１／５程度なら種々の条件で良好に使用できることが確
認されている。When the set pressure of the on-off valve 23 is extremely low,
For example, in the case of 10 kgf / cm 2 or the like, at the moment when the detection valve 28 and the opening / closing valve 23 are switched, pressure oil is discharged from the throttle 22 and a flow that bypasses the hydraulic cylinder 1 occurs from the opening / closing valve 26 that is still open. Since this flow rate bypasses the hydraulic cylinder 1, it does not contribute to the movement of the hydraulic cylinder 1 and is wasted. This useless flow disappears once the on-off valve 26 is closed, and is a momentary flow. However, this flow is large for a large-sized grip device, so it is not ridiculous. Therefore, the set pressure of the on-off valve 23 is set to an appropriate value. According to the experiment, this set pressure is 3/4 of the set pressure of the detection valve 28 as described above.
It can be used in a fairly wide setting range of about less than, but from 1/2 to
It has been confirmed that if it is about 1/5, it can be used favorably under various conditions.
【００４１】この開閉弁２３と絞り２２とで構成した圧
抜き弁２４は開閉のタイミングを開閉弁２３で、圧抜き
速度を絞り２２で、というように分担させたので、圧抜
き動作は非常に安定なものとなった。The pressure relief valve 24 constituted by the on-off valve 23 and the throttle 22 shares the timing of opening and closing with the on-off valve 23 and the pressure relief speed with the throttle 22. It became stable.
【００４２】開閉弁２３の設定は圧力設定なので、スプ
ールの開き速度を絞りで行う方式のように開き方に油温
などの影響をほとんど受けず、非常に安定した動作とな
る。また圧抜きは絞り２２によるので、圧抜きが徐々に
行われ、圧力弁方式によるような一気に抜けることはな
い。絞り２２は可変型が望ましいが、シリンダサイズご
とに穴径を決めたプラグでも良く、この場合調整を省く
ことになるので、コンパクト化を更に進めるとともに調
整コストを下げることができる。Since the opening / closing valve 23 is set to the pressure setting, the opening speed is hardly affected by the oil temperature and the like as in the system in which the opening speed of the spool is controlled by the throttle, and the operation is very stable. Further, since the pressure release is performed by the throttle 22, the pressure release is gradually performed, and the pressure release does not occur all at once. The diaphragm 22 is preferably a variable type, but a plug having a hole diameter determined for each cylinder size may be used. In this case, adjustment can be omitted, so further compactification and reduction in adjustment cost can be achieved.
【００４３】すなわち、本方式では検知弁２８の設定圧
力ぎりぎりまで確実に差動動作が行われ、圧抜きは圧抜
き動作に基本的に安定である絞り方式で行うので、開閉
弁２３の設定圧力はその動作への影響が一瞬であるこ
と、かつ、検知弁２８に対してかなり低くて良いことか
ら、ラフで良く、したがって圧力調整は基本的には検知
弁２８のみでほとんど決まるなど、従来のものに比べて
非常に容易なものとなった。That is, in this system, the differential operation is reliably performed up to the set pressure of the detection valve 28, and the pressure release is performed by the throttle system which is basically stable in the pressure release operation. Has a brief effect on its operation, and can be considerably low with respect to the detection valve 28, so it can be rough, and therefore the pressure adjustment is basically determined only by the detection valve 28. It became much easier than the ones.
【００４４】図９は本増速弁ユニット２０のブロック組
立体の一例を示すものであり、構成弁はすべてねじ込み
式の挿入弁である。（ａ）は平面図、（ｂ）は正面図、
（ｃ）は側面図である。検知弁２８、第１の開閉弁２
６、第２の開閉弁２３、逆止弁２１などをブロック３５
にねじ込んで装着する挿入式ユニット形に構成したもの
である。なお、図示しない絞り２２は絞り穴付きのプラ
グを油路途中にねじ込んでいる。したがって、ブロック
３５と弁ユニットとは別体に製作されているので、交換
や取扱いが極めて容易である。ブロック３５の材質に軽
量かつ高強度のアルミ合金、エンジニアリングプラスチ
ック、あるいはチタンを用いることができる。FIG. 9 shows an example of a block assembly of the speed increasing valve unit 20. The constituent valves are all screw-in type insertion valves. (A) is a plan view, (b) is a front view,
(C) is a side view. Detection valve 28, first opening / closing valve 2
6, the second on-off valve 23, the check valve 21, etc. are blocked 35
It is configured as an insertion type unit that is screwed into and attached to. The throttle 22 (not shown) has a plug with a throttle hole screwed into the oil passage. Therefore, since the block 35 and the valve unit are manufactured separately, replacement and handling are extremely easy. The block 35 may be made of lightweight and high-strength aluminum alloy, engineering plastic, or titanium.
【００４５】図１０はブロック３５内の構成弁の一つで
ある第１の開閉弁２６の断面図である。ねじ込み式弁は
挿入式弁の一種で、他に挿入式弁としてはブロック３５
に挿入後、別部品のカバーで抜けてこないように抑える
方式としても良い。また挿入式の弁には図３〜図７に具
体的形状で概要を示したようにロジック弁といわれるシ
ート状のものもあればスプール状のものもあり、いずれ
でも良い。要は、挿入式の弁は弁機能はそのもの自体で
動作でき（弁ユニット）、ブロックは弁ユニットを収納
し、互いに油路にて接続することであり、従来のように
ブロック内に摺動孔を形成しその摺動孔内で、スプー
ル、ポペットなどの弁部品を摺動させるものではない。FIG. 10 is a sectional view of the first on-off valve 26 which is one of the constituent valves in the block 35. The screw-in type valve is a type of insertion type valve.
After inserting it in, the cover may be a separate component to prevent it from coming off. Further, as the insertable valve, there are a sheet-like valve called a logic valve and a spool-like valve as shown in the outline of the concrete shape in FIGS. 3 to 7, and any of them may be used. The point is that the valve of the insertable type can operate by itself (valve unit), the block accommodates the valve unit, and they are connected to each other by the oil passage. The valve component such as the spool and the poppet is not slid in the sliding hole.
【００４６】図９に示すように、ブロック形式で構成し
た増速弁ユニットは、ブロック３５に切替弁に接続する
２個のポートＶ1 、Ｖ2 を有し、また油圧シリンダとの
接続ポートＣ1 、Ｃ2 は取付面に開口している。このブ
ロック３５は４個の取付穴３６を使ってグリップ装置に
取り付けられる。グリップ装置への取付位置は図２に示
すように安全・保護の面からグリップ装置内部に収納す
るのが良い。また油圧シリンダに直接取り付けても良
い。As shown in FIG. 9, a block type speed increasing valve unit has two ports V1 and V2 connected to a switching valve in a block 35, and connection ports C1 and C2 to a hydraulic cylinder. Has an opening on the mounting surface. This block 35 is attached to the grip device using four attachment holes 36. The mounting position of the grip device is preferably housed inside the grip device for safety and protection as shown in FIG. It may be directly attached to the hydraulic cylinder.
【００４７】（実施例２）図１１は本発明の実施例２に
係る増速弁ユニットの油圧回路図で、図１２は各構成弁
の概要を示す図で図３に相当する状態図である。本実施
例は、小型のグリップ装置に適するように更に考慮・実
験を加えて得られたものである。実施例１の圧抜き弁２
４において第２の開閉弁２３を除いたものである。第２
の開閉弁２３を有しないため、絞り２２は常時作用状態
にある。(Embodiment 2) FIG. 11 is a hydraulic circuit diagram of a speed increasing valve unit according to Embodiment 2 of the present invention, and FIG. 12 is a view showing an outline of each constituent valve and is a state diagram corresponding to FIG. . This embodiment was obtained by further considering and experimenting so as to be suitable for a small grip device. Pressure relief valve 2 of Example 1
In FIG. 4, the second on-off valve 23 is removed. Second
Since it does not have the open / close valve 23, the throttle 22 is always in the operating state.
【００４８】実施例１との差は差動動作および差動動作
解除の途中までに現れ、他の動作では変わらない。ま
た、開閉弁２６の構造は閉鎖後のオーバラップが少な
く、解放ストロークが小さい割に開口面積の大きいもの
なら良いので、シートタイプに変えて使用している。The difference from the first embodiment appears in the middle of the differential operation and cancellation of the differential operation, and does not change in other operations. Further, since the structure of the on-off valve 26 has a small overlap after closure and a large opening area despite a small opening stroke, it is used in place of the seat type.
【００４９】差動動作時には油圧シリンダ１は無負荷あ
るいは低負荷であるので、油圧シリンダ１は差動中低圧
で高速突き出しを行う。この時、絞り２２から高速動作
を阻害する損失として流量がタンク８へ流出する。ただ
し、本装置は小型用なので絞りの径が小さいことおよび
低圧であることから、その流量は無視できるものであ
る。検知弁２８が切り替わるまでは、圧力上昇とともに
絞り２２からの流出流量は増えていき、その量によって
は多少の流体音が発生することもある。そして検知弁２
８が切り替わり、開閉弁２６が閉じると、実施例１と同
じく１００％の油圧力が油圧シリンダ１から出力され
る。During the differential operation, the hydraulic cylinder 1 is unloaded or has a low load, and therefore the hydraulic cylinder 1 ejects at high speed at a medium to low differential pressure. At this time, the flow rate flows out from the throttle 22 to the tank 8 as a loss that hinders the high speed operation. However, since this device is for a small size, the diameter of the throttle is small and the pressure is low, so the flow rate can be ignored. Until the detection valve 28 is switched, the flow rate of outflow from the throttle 22 increases as the pressure increases, and some fluid noise may be generated depending on the amount. And the detection valve 2
When 8 is switched and the on-off valve 26 is closed, 100% hydraulic pressure is output from the hydraulic cylinder 1 as in the first embodiment.
【００５０】本実施例は、実施例１に対し、差動動作か
らそれの切り替え完了までの動作において、差動動作と
して損失となる流れがあるが、小型用であることから、
絞り径が小さくその損失量もわずかであること、それよ
り小型化、軽量化への貢献の方が最優先であり、特に小
型の油圧ショベルなどの建設車両に装着して、挾持、破
砕などをするグリップ装置に最適な増速弁ユニットとな
っている。In contrast to the first embodiment, this embodiment has a flow of loss as a differential operation in the operation from the differential operation to the completion of switching thereof, but since it is for a small size,
The small diameter and small loss are the top priorities for contributing to downsizing and weight reduction.Especially for small hydraulic excavators and other construction vehicles, they can be held and crushed. It is an optimal speed increasing valve unit for the grip device.
【００５１】[0051]
【発明の効果】以上のように、本発明は、１個の圧力検
知弁でパイロット操作形の開閉弁の差動切り替えを行
い、圧抜きは絞りにて徐々に行わせるようにしたので、
急激な圧抜きを防止することができ、検知弁の設定圧力
ぎりぎりまで差動動作を継続させることができる。その
ためショックレスで安定性の高い、高応答性の増速弁ユ
ニットが得られている。As described above, according to the present invention, the differential operation of the pilot operated on-off valve is switched by one pressure detection valve, and the pressure release is gradually performed by the throttle.
It is possible to prevent sudden depressurization, and it is possible to continue the differential operation until the set pressure of the detection valve is almost reached. Therefore, a shockless, highly stable, highly responsive speed increasing valve unit is obtained.
【００５２】また、検知弁の圧力設定値は圧抜き弁また
は第２の開閉弁のそれに比べて相当高く、圧抜き弁また
は第２の開閉弁の圧力設定はラフで良いため、圧力調整
が容易である。Further, the pressure set value of the detection valve is considerably higher than that of the pressure relief valve or the second opening / closing valve, and the pressure setting of the pressure relief valve or the second opening / closing valve may be rough, so that the pressure adjustment is easy. Is.
【００５３】さらに、油圧回路がシンプルで、小型・軽
量化を図ることができ、グリップ装置の大から小まで適
用範囲を拡大させることが可能になっている。Further, the hydraulic circuit is simple, the size and weight can be reduced, and the range of application of the grip device can be expanded from large to small.
【図１】本発明の実施例１による増速弁ユニットの油圧
回路図である。FIG. 1 is a hydraulic circuit diagram of a speed increasing valve unit according to a first embodiment of the present invention.
【図２】増速弁ユニットの油圧ショベルへの取付位置を
示す概要図である。FIG. 2 is a schematic diagram showing a mounting position of a speed increasing valve unit on a hydraulic excavator.
【図３】油圧シリンダの停止状態の油圧回路図である。FIG. 3 is a hydraulic circuit diagram of a hydraulic cylinder in a stopped state.
【図４】油圧シリンダの差動動作時の油圧回路図であ
る。FIG. 4 is a hydraulic circuit diagram during differential operation of a hydraulic cylinder.
【図５】油圧シリンダの差動から圧砕への移行動作時の
油圧回路図である。FIG. 5 is a hydraulic circuit diagram during a transition operation from differential to crushing of a hydraulic cylinder.
【図６】油圧シリンダの強挾持動作時の油圧回路図であ
る。FIG. 6 is a hydraulic circuit diagram at the time of a strong holding operation of the hydraulic cylinder.
【図７】油圧シリンダの戻り動作時の油圧回路図であ
る。FIG. 7 is a hydraulic circuit diagram at the time of returning operation of the hydraulic cylinder.
【図８】油圧シリンダの両室における圧力変化を示すグ
ラフである。FIG. 8 is a graph showing pressure changes in both chambers of the hydraulic cylinder.
【図９】増速弁ユニットの装着用ブロック組立体の概要
図である。FIG. 9 is a schematic view of a block assembly for mounting the speed increasing valve unit.
【図１０】ブロック内に組み込んだ第１の開閉弁の部分
断面図である。FIG. 10 is a partial cross-sectional view of a first opening / closing valve incorporated in a block.
【図１１】本発明の実施例２による増速弁ユニットの油
圧回路図である。FIG. 11 is a hydraulic circuit diagram of the speed increasing valve unit according to the second embodiment of the present invention.
【図１２】実施例２の各弁の概略構成図である。FIG. 12 is a schematic configuration diagram of each valve of the second embodiment.
【図１３】従来の増速弁ユニットの油圧回路図である。FIG. 13 is a hydraulic circuit diagram of a conventional speed increasing valve unit.
【図１４】従来の増速弁ユニットの油圧回路図である。FIG. 14 is a hydraulic circuit diagram of a conventional speed increasing valve unit.
【図１５】従来の増速弁ユニットの油圧回路図である。FIG. 15 is a hydraulic circuit diagram of a conventional speed increasing valve unit.
１ 油圧シリンダ ２ ロッド側油室 ３ ヘッド側油室 ４ ロッド側油路 ５ ヘッド側油路 ６ 切替弁 ７ 油圧ポンプ ８ タンク １０ 油圧源 １１ ピストンロッド ２０ 増速弁ユニット ２１ 逆止弁 ２２ 絞り ２３ 第２の開閉弁 ２４ 圧抜き弁 ２５ バイパス路 ２６ 第１の開閉弁 ２７ パイロット油路 ２８ 検知弁 ２９ 油路 ３０ 油路 ３１ 油路 ３５ ブロック 1 hydraulic cylinder 2 Rod side oil chamber 3 Head side oil chamber 4 Rod side oil passage 5 head side oil passage 6 switching valve 7 hydraulic pump 8 tanks 10 Hydraulic power source 11 piston rod 20 Speed increasing valve unit 21 Check valve 22 aperture 23 Second on-off valve 24 Pressure relief valve 25 Bypass 26 First on-off valve 27 Pilot oil passage 28 Detection valve 29 oil passage 30 oilways 31 oil passage 35 blocks
フロントページの続き (56)参考文献 特開 平６−81801（ＪＰ，Ａ) 実開 平６−43155（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) E02F 9/22 F15B 11/024 Continuation of the front page (56) Reference JP-A-6-81801 (JP, A) Actual development: 6-43155 (JP, U) (58) Fields investigated (Int.Cl. 7 , DB name) E02F 9 / 22 F15B 11/024
Claims (6)
油圧シリンダと該油圧シリンダの操作用切替弁との間に
接続される増速弁ユニットにおいて、 前記油圧シリンダのロッド側油室に通じるロッド側油路
に設けられた、該油室に向かってのみ流れを許す逆止弁
と、 前記逆止弁と並列に接続された圧抜き弁と、 前記逆止弁より下流側の前記ロッド側油路と前記油圧シ
リンダのヘッド側油室に通じるヘッド側油路とを連通さ
せるバイパス油路に設けられたパイロット操作形の開閉
弁と、 前記ヘッド側油路のパイロット油路に設けられ、前記圧
抜き弁より高い圧力設定値を有する検知弁と、 前記検知弁の開動作時の出力接続口と前記開閉弁のパイ
ロット接続口を接続した油路と、 前記検知弁の閉動作時の出力接続口と前記逆止弁より上
流側の前記ロッド側油路を接続した油路と、を備え、 前記圧抜き弁が絞りである ことを特徴とする作業機械の
グリップ装置用増速弁ユニット。1. A speed-increasing valve unit connected between a hydraulic cylinder that drives a grip device of a work machine to open and close, and an operation switching valve of the hydraulic cylinder, wherein a rod side communicating with a rod-side oil chamber of the hydraulic cylinder. A check valve provided in the oil passage, which allows the flow only toward the oil chamber, a pressure relief valve connected in parallel with the check valve, and the rod-side oil passage downstream of the check valve. And a pilot-operated on-off valve provided in a bypass oil passage that communicates with a head-side oil passage that communicates with the head-side oil chamber of the hydraulic cylinder; and the pressure relief valve provided in the pilot oil passage of the head-side oil passage. A detection valve having a pressure set value higher than that of the valve, an oil passage connecting the output connection port during the opening operation of the detection valve and the pilot connection port of the opening / closing valve, and the output connection port during the closing operation of the detection valve In front of the check valve And a fluid passage connecting the serial rod side oil passage, the working machine of the gripping device for the acceleration valve unit, characterized in that the depressurization valves is squeezed.
の第２の開閉弁とをシリーズに接続して構成され、該第
２の開閉弁のパイロット接続口を前記開閉弁のパイロッ
ト接続口に接続したことを特徴とする請求項１記載の作
業機械のグリップ装置用増速弁ユニット。2. The pressure relief valve is configured by connecting a throttle and a pilot operated second on-off valve in series, and the pilot connection port of the second on-off valve is connected to the pilot connection port of the on-off valve. The speed increasing valve unit for a grip device of a working machine according to claim 1, wherein the speed increasing valve unit is connected.
２の開閉弁の圧力設定値を３／４以下としたことを特徴
とする請求項２記載の作業機械のグリップ装置用増速弁
ユニット。To pressure setpoint of claim 3 wherein said sensing valve, the second work machine gripping devices for acceleration according to claim 2, characterized in that a pressure setting value 3/4 of the on-off valve Valve unit.
とする請求項１または請求項２記載の作業機械のグリッ
プ装置用増速弁ユニット。4. The method of claim 1 or claim 2 working machine gripping devices for acceleration valve unit according is characterized in that a sheet-shaped the on-off valve.
ロックにねじ込みなどの挿入式ユニット形で構成されて
いることを特徴とする請求項１、請求項２、請求項３、
または請求項４記載の作業機械のグリップ装置用増速弁
ユニット。5. A block according to claim 1, wherein each of said valves is constructed in the form of an insertable unit such as screwing into said block.
Or claim 4 work machine gripping device for a speed increase valve unit according.
アルミ合金もしくはエンジニアリングプラスチックまた
はチタンとしたことを特徴とする請求項５記載の作業機
械のグリップ装置用増速弁ユニット。6. The speed increasing valve unit for a grip device of a working machine according to claim 5, wherein the block is made of a lightweight and high-strength aluminum alloy, engineering plastic, or titanium.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05227794A JP3396728B2 (en) | 1994-03-23 | 1994-03-23 | Speed-up valve unit for work equipment grip device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05227794A JP3396728B2 (en) | 1994-03-23 | 1994-03-23 | Speed-up valve unit for work equipment grip device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07259139A JPH07259139A (en) | 1995-10-09 |
| JP3396728B2 true JP3396728B2 (en) | 2003-04-14 |
Family
ID=12910304
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP05227794A Expired - Fee Related JP3396728B2 (en) | 1994-03-23 | 1994-03-23 | Speed-up valve unit for work equipment grip device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3396728B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE29810860U1 (en) * | 1998-06-17 | 1998-08-13 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Hydraulic control device |
| SE545550C2 (en) * | 2020-08-20 | 2023-10-17 | Komatsu Forest Ab | Hydraulic log grapple with adaptive control and log handling vehicles including such |
-
1994
- 1994-03-23 JP JP05227794A patent/JP3396728B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH07259139A (en) | 1995-10-09 |
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