JPH065876U - Hydraulic breaker - Google Patents
Hydraulic breakerInfo
- Publication number
- JPH065876U JPH065876U JP4622592U JP4622592U JPH065876U JP H065876 U JPH065876 U JP H065876U JP 4622592 U JP4622592 U JP 4622592U JP 4622592 U JP4622592 U JP 4622592U JP H065876 U JPH065876 U JP H065876U
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- pressure
- chamber
- piston
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- adjusting
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Abstract
(57)【要約】
【目的】リリーフ弁、ストップ弁および絞り弁を不要に
し、しかも取扱が簡単な油圧ブレーカを提供する。
【構成】第１圧力室４と連通するコントロールバルブ８
の第２室１６は管路２６により圧力調整バルブ２７の第
３調整室３５に接続されている。高圧回路の圧力がより
小さいとき、第３調整室３５は圧力調整ピストン２９に
よって閉ざされ、打撃ピストン３は上方への移動が阻止
されているので、高圧回路の圧力は上昇して適正作動圧
力の範囲になる。
(57) [Summary] [Purpose] To provide a hydraulic breaker that does not require a relief valve, a stop valve and a throttle valve and is easy to handle. [Constitution] Control valve 8 communicating with the first pressure chamber 4
The second chamber 16 is connected to the third adjusting chamber 35 of the pressure adjusting valve 27 by the pipe line 26. When the pressure in the high pressure circuit is smaller, the third adjusting chamber 35 is closed by the pressure adjusting piston 29, and the striking piston 3 is prevented from moving upward. Therefore, the pressure in the high pressure circuit rises to a proper operating pressure. It becomes the range.
Description
【０００１】[0001]
本考案は、油圧ショベルのアタッチメントとしてアーム先端に取り付け、ビル の解体や砕石作業等に使用される油圧ブレーカに関する。 The present invention relates to a hydraulic breaker which is attached to the end of an arm as an attachment of a hydraulic excavator and is used for demolition of buildings or crushing stones.
【０００２】[0002]
従来の油圧ブレーカは、図２に示すように、シリンダ５１内の打撃ピストン５ ２の位置に対応してコントロールバルブ５３のコントロールピストン５４が切り 替わり、打撃ピストン５２が上昇、下降動を繰返し、下降時にチゼル５５の頭部 を打撃ピストン５２が直接打撃することにより、打撃力を伝達してチゼル５５の 先端でコンクリート等を破砕することが知られている。 In the conventional hydraulic breaker, as shown in FIG. 2, the control piston 54 of the control valve 53 is switched in correspondence with the position of the striking piston 52 in the cylinder 51, and the striking piston 52 repeatedly moves up and down to descend. It is known that the striking piston 52 directly strikes the head of the chisel 55 to transmit the striking force to crush concrete or the like at the tip of the chisel 55.
【０００３】 この種の油圧ブレーカにおいて、油圧ポンプからの供給油量がブレーカの必要 油量より少ない場合、その作動圧力が低下するため、適正作動圧力の範囲へ上昇 させるべく、ブレーカ内の戻り回路に設けた絞り弁５６の開度を調整している。 また、油圧ブレーカの作動圧力は油圧ショベル操作用の圧力より低いため、殆ど の配管にはリリーフ弁が設けられている。さらに、油圧ブレーカと破砕機が併用 できるように、油圧ショベルに破砕機併用配管が施されている場合、破砕機は通 常油圧ブレーカより高い作動圧力で使用されるため、破砕機併用配管は図３に示 すように、リリーフ弁６１の回りにストップ弁６２，６３，６４を設けている。 破砕機併用配管に接続された油圧ブレーカを使用する場合には、すべてのストッ プ弁６２，６３，６４を開き、油圧ポンプ６０から作動圧力が油圧ブレーカの適 正作動圧力より高ければ、配管途上のリリーフ弁６１へ逃がすことで適正作動圧 力の範囲にして油圧ブレーカに供給している。他方、破砕機を使用する場合には すべてのストップ弁６２，６３，６４を閉じ、油圧ポンプ６０から圧油を供給し ている。In this type of hydraulic breaker, when the amount of oil supplied from the hydraulic pump is less than the required amount of oil for the breaker, the operating pressure decreases, so that the return circuit in the breaker should be increased in order to raise it to the range of the appropriate operating pressure. The opening degree of the throttle valve 56 provided at is adjusted. Also, since the working pressure of the hydraulic breaker is lower than the pressure for operating the hydraulic excavator, most pipes are equipped with a relief valve. In addition, if the hydraulic excavator is equipped with a pipe for use with a crusher so that the hydraulic breaker and the crusher can be used together, the crusher is normally used at a higher operating pressure than the hydraulic breaker, so the pipe for use with the crusher is As shown in FIG. 3, stop valves 62, 63, 64 are provided around the relief valve 61. When using a hydraulic breaker connected to a pipe combined with a crusher, open all stop valves 62, 63, 64, and if the working pressure from the hydraulic pump 60 is higher than the proper working pressure of the hydraulic breaker, then the pipe is in the process of being stopped. It is supplied to the hydraulic breaker within the range of the appropriate operating pressure by being released to the relief valve 61. On the other hand, when a crusher is used, all stop valves 62, 63, 64 are closed and pressure oil is supplied from the hydraulic pump 60.
【０００４】[0004]
【考案が解決しようとする課題】 上記した従来の油圧ブレーカにおいては、油圧ブレーカ内の戻り回路に設けた 絞り弁５６の開度の調整が難しく、調整ミスによるトラブルが発生することが多 々あった。また、配管途上にリリーフ弁６１を設けると、配管が複雑になるだけ でなく、初めて油圧ブレーカをショベルに取り付ける場合や異なるメーカーの油 圧ブレーカに取り付けを変更する場合、リリーフ弁６１の調整や新設をしなけれ ばならなかった。また、上記ストップ弁６２，６３，６４は油圧ブレーカ使用時 には開き、破砕機を使用時には閉じる必要があるが、この取扱を誤るとトラブル が生ずることがあった。In the above-mentioned conventional hydraulic breaker, it is difficult to adjust the opening degree of the throttle valve 56 provided in the return circuit in the hydraulic breaker, and a trouble due to an adjustment error often occurs. It was If the relief valve 61 is installed on the way of piping, not only the piping becomes complicated, but also when the hydraulic breaker is installed on the shovel for the first time or when the installation is changed to the hydraulic breaker of a different manufacturer, the relief valve 61 is adjusted or a new installation is required. I had to do it. Further, the stop valves 62, 63, 64 need to be opened when the hydraulic breaker is used and closed when the crusher is used, but this mishandling may cause trouble.
【０００５】 このように、従来の油圧ブレーカでは必要とされる調整や取扱方法があり、こ の調整や取扱方法は十分な知識と技能を持つ熟練者によらなければ、種々のトラ ブルを招き易いという不具合があった。As described above, the conventional hydraulic breakers have the necessary adjustments and handling methods, and these adjustments and handling methods can cause various troubles unless an expert with sufficient knowledge and skill is involved. There was a problem that it was easy.
【０００６】 本考案は、上述した従来の油圧ブレーカにおける不具合を除去し、リリーフ弁 やストップ弁、さらに絞り弁が不要であり、しかも面倒な取扱がなく誰でも簡単 に使用できる油圧ブレーカを提供することを目的としている。The present invention eliminates the above-mentioned problems in the conventional hydraulic breaker, provides a hydraulic breaker that does not require a relief valve, a stop valve, and a throttle valve, and is easy for anyone to use without troublesome handling. Is intended.
【０００７】[0007]
上記目的を達成するため本考案は、面積の異なる２つの受圧面を有しチゼルを 打撃する打撃ピストンと、該打撃ピストンの面積の大なる第１受圧面に圧油を作 用する第１圧力室と、前記打撃ピストンの面積の小なる第２受圧面に圧油を作用 する第２圧力室とを有し、前記第１圧力室にはコントロールバルブを介して高圧 回路と低圧回路を交番的に切り換え接続し、第２圧力室には常時高圧回路を接続 する油圧ブレーカにおいて、油圧ブレーカ本体に高圧回路の圧力の大きさに応じ て移動可能な圧力調整ピストンを有する圧力調整弁を設け、該圧力調整弁は高圧 回路の作動圧力が適正作動圧力の範囲より小さいとき、圧力調整ピストンが前記 コントロールバルブを介した前記第１圧力室を閉ざす位置に位置され、高圧回路 の作動圧力が適正作動圧力の範囲に達したとき、圧力調整ピストンが前記第１圧 力室を低圧回路に接続する位置に移動されることを特徴としている。 To achieve the above object, the present invention provides a striking piston for striking a chisel having two pressure receiving surfaces having different areas, and a first pressure for applying pressure oil to a first pressure receiving surface having a large area of the striking piston. Chamber and a second pressure chamber for applying pressure oil to the second pressure receiving surface having a smaller area of the striking piston, and the high pressure circuit and the low pressure circuit are alternately arranged in the first pressure chamber via a control valve. In a hydraulic breaker in which a high pressure circuit is always connected to the second pressure chamber, the main body of the hydraulic breaker is provided with a pressure adjustment valve having a pressure adjustment piston movable according to the pressure of the high pressure circuit. When the working pressure of the high pressure circuit is smaller than the range of the proper working pressure, the pressure regulating piston is positioned so that the pressure regulating piston closes the first pressure chamber via the control valve, and the working pressure of the high pressure circuit is appropriate. Upon reaching a range of operating pressures, is characterized in that the pressure regulating piston is moved to a position connecting said first pressure chamber to the low pressure circuit.
【０００８】 さらに、本考案は前記圧力調整弁は高圧回路の作動圧力が適正作動圧力の範囲 よりも大きいとき、圧力調整ピストンが高圧回路の余分な圧油を低圧回路に逃が す位置に移動されることを特徴としている。Further, according to the present invention, when the working pressure of the high pressure circuit is larger than the proper working pressure range, the pressure adjusting piston moves the pressure adjusting piston to a position where excess pressure oil of the high pressure circuit is released to the low pressure circuit. It is characterized by being done.
【０００９】[0009]
上記の構成によれば、圧力調整弁は高圧回路のブレーカ作動圧力が適正作動圧 力の範囲より小さければ、圧力調整ピストンをコントロールバルブを介した第２ 圧力室を閉ざす位置に位置して作動圧力を上昇でき、高圧回路の圧力が適正作動 圧力の範囲に達すれば、圧力調整ピストンが第２圧力室を低圧回路に接続する位 置に移動するので、絞り弁の調整が不要になるだけでなく、絞り弁自体が不要に なる。 According to the above configuration, if the breaker operating pressure of the high pressure circuit is smaller than the range of the proper operating pressure, the pressure adjusting piston is positioned so that the pressure adjusting piston closes the second pressure chamber via the control valve. If the pressure in the high pressure circuit reaches the range of the proper operating pressure, the pressure adjusting piston moves to the position where the second pressure chamber is connected to the low pressure circuit, so that not only the adjustment of the throttle valve becomes unnecessary. , The throttle valve itself becomes unnecessary.
【００１０】 さらに、上記の構成によれば、圧力調整弁は高圧回路の作動圧力が適正作動圧 力の範囲よりも大きいとき、圧力調整ピストンが高圧回路の余分な圧油を低圧回 路に逃がす位置に移動するので、油圧ブレーカと破砕機を併用しても配管途上の リリーフ弁やストップ弁が不要になる。Furthermore, according to the above configuration, when the working pressure of the high pressure circuit is larger than the range of the proper working pressure, the pressure regulating piston allows the pressure regulating piston to release excess pressure oil of the high pressure circuit to the low pressure circuit. Since it moves to the position, even if a hydraulic breaker and a crusher are used together, there is no need for a relief valve or stop valve in the middle of piping.
【００１１】[0011]
以下、本考案の実施例を添付図面に従って説明する。 図１において、油圧ブレーカはその本体１にチゼル２が上下往復動可能に支持 され、さらに油圧ブレーカ本体１内にはチゼル２を打撃する打撃ピストン３が図 の上下方向に往復動可能に収容されている。打撃ピストン３には、受圧面積の大 なる第１受圧面Ａ１および受圧面積小なる第２受圧面Ａ２との２つの面積の異な る受圧面を有している。 Embodiments of the present invention will be described below with reference to the accompanying drawings. In FIG. 1, the hydraulic breaker has a body 1 in which a chisel 2 is supported so as to be capable of reciprocating vertically, and a striking piston 3 for striking the chisel 2 is accommodated in the body 1 of the hydraulic breaker so as to be capable of reciprocating in the vertical direction in the figure. ing. The striking piston 3 has two pressure receiving surfaces having different areas: a first pressure receiving surface A1 having a large pressure receiving area and a second pressure receiving surface A2 having a small pressure receiving area.
【００１２】 油圧ブレーカ本体１には、第１受圧面Ａ１に圧力を作用する圧油を収容する第 １圧力室４と、第２受圧面Ａ２に圧力を作用する圧油を収容する第２圧力室５と が形成されている。第２圧力室５には、高圧回路管路６が接続され、第１圧力室 ４には管路７によりコントロールバルブ８が接続されている。The hydraulic breaker body 1 has a first pressure chamber 4 for accommodating pressure oil that exerts pressure on the first pressure receiving surface A1 and a second pressure chamber 4 for accommodating pressure oil that exerts pressure on the second pressure receiving surface A2. A chamber 5 is formed. A high pressure circuit line 6 is connected to the second pressure chamber 5, and a control valve 8 is connected to the first pressure chamber 4 via a line 7.
【００１３】 コントロールバルブ８は、高圧回路と低圧回路とを第１圧力室４に交番的に切 換接続可能に形成されている。図１の例では、コントロールバルブ８がバルブ本 体９と該バルブ本体９に摺動案内されるコントロールピストン１０とを有してい る。コントロールピストン１０内には、軸線方向に延びる貫通穴１１が設けられ 、外周面には受圧面積の異なる３つの受圧面として第１段部１２、第２段部１３ 、第３段部１４とが形成されている。バルブ本体９には、第１段部１２に圧力を 作用し、高圧回路と接続されている第１室１５と、第２段部１３に圧力を作用す る第２室１６と、第３段部１４に圧力を作用する第３室１７と、コントロールピ ストン１０の一側端に面して形成され前記管路６により第１圧力室４に接続され る第４室１８と、コントロールピストン１０の反対端に面して形成される第５室 １９と、該第５室２１にコントロールピストン１０の動きに応じて連通可能な第 ６室２０とが形成されている。なお、コントロールピストン１０の各受圧面積は 第１室１５を受圧面Ａ３、第２室１６を受圧面Ａ４と、第３室１７を受圧面Ａ５ と、第４室１８を受圧面Ａ６と、第５室１９を受圧面Ａ７とすると、受圧面Ａ３ ，Ａ５，Ａ６，Ａ７はＡ５＞Ａ３，Ａ６＝Ａ７である。The control valve 8 is formed so that the high pressure circuit and the low pressure circuit can be alternately connected to the first pressure chamber 4 by switching. In the example of FIG. 1, the control valve 8 has a valve body 9 and a control piston 10 slidably guided by the valve body 9. A through hole 11 extending in the axial direction is provided in the control piston 10, and a first step portion 12, a second step portion 13, and a third step portion 14 are provided on the outer peripheral surface as three pressure receiving surfaces having different pressure receiving areas. Has been formed. In the valve body 9, a first chamber 15 that exerts pressure on the first stage 12 and is connected to a high-pressure circuit, a second chamber 16 that exerts pressure on the second stage 13, and a third stage A third chamber 17 for exerting pressure on the portion 14, a fourth chamber 18 formed facing one end of the control piston 10 and connected to the first pressure chamber 4 by the pipe 6, and a control piston 10 A fifth chamber 19 formed facing the opposite end of the control chamber 10 and a fifth chamber 21 formed with a sixth chamber 20 communicable with the control piston 10 according to the movement of the control piston 10. The pressure receiving areas of the control piston 10 are the pressure receiving surface A3 for the first chamber 15, the pressure receiving surface A4 for the second chamber 16, the pressure receiving surface A5 for the third chamber 17, the pressure receiving surface A6 for the fourth chamber 18, and Assuming that the five chambers 19 are the pressure receiving surface A7, the pressure receiving surfaces A3, A5, A6, A7 are A5> A3, A6 = A7.
【００１４】 油圧ブレーカ本体１には、コントロールバルブ８と接続されて打撃ピストン３ の移動ストロークを制御するための第１溝２１と、該第１溝２１に対して所定の 間隔で、かつ低圧回路が接続された第２溝２２とが形成され、打撃ピストン３の 動きに応じて打撃ピストン３に形成された小径中間部２３により第１溝２１と第 ２溝２２とが連通可能になっている。なお、符号２４は第２圧力室５に接続され た高圧アキュムレータであり、圧油が畜圧される。The hydraulic breaker body 1 has a first groove 21 connected to the control valve 8 for controlling the movement stroke of the striking piston 3, and a low pressure circuit at a predetermined interval with respect to the first groove 21. And a second groove 22 to which the striking piston 3 is connected. The small diameter intermediate portion 23 formed on the striking piston 3 according to the movement of the striking piston 3 allows the first groove 21 and the second groove 22 to communicate with each other. . Reference numeral 24 is a high pressure accumulator connected to the second pressure chamber 5, and the pressure oil is stored.
【００１５】 コントロールバルブ８の貫通穴１１と第２室１６とは、横穴２５によって連通 され、この第２室１６には管路２６により圧力調整バルブ２７が接続されている 。圧力調整バルブ２７は、調整バルブ本体２８と該調整バルブ本体２８に図にお いて左右方向に摺動案内される圧力調整ピストン２９を有している。圧力調整ピ ストン２９内には、軸線方向に延びる貫通穴３０が設けられ、外周面には第１調 整段部３１および第２調整段部３２とが形成されている。そして、調整バルブ本 体２８には第１調整段部３１に圧力を作用する第１調整室３３と、第２調整段部 ３２に圧力を作用する第２調整室３４と、圧力調整ピストン２９の一端部に面し て形成され、管路２６により第２室１６に接続される第３調整室３５とが設けら れ、第１調整室３３と第２調整室３４は低圧回路と常時通じており、第３調整室 ３５は圧力調整ピストン２９の動きに応じて第１調整室３３と連通可能になって いる。さらに、圧力調整バルブ２７は、圧力調整ピストン２９の一側端に面して 形成された第４調整室３６と、圧力調整ピストン２９の反対端に面して形成され る第５調整室３７とが形成され、第４調整室３６および第５調整室３７は高圧回 路と常時通じている。さらにまた、圧力調整バルブ２７には圧力調整ピストン２ ９の反対端に圧接して図における左方へ力Ｆで押圧するバネ３９が設けられ、バ ネ３９はロックナット４０に螺合された調整ネジ３８の進退によってバネ力Ｆが 可変される。なお、圧力調整ピストン２９の各受圧面積は、第４調整室３６を受 圧面Ａ８と、第５調整室３７を受圧面Ａ９とすると、受圧面Ａ８，Ａ９はＡ８＞ Ａ９である。The through hole 11 of the control valve 8 and the second chamber 16 are communicated with each other by a lateral hole 25, and a pressure adjusting valve 27 is connected to the second chamber 16 by a pipe line 26. The pressure adjusting valve 27 has an adjusting valve body 28 and a pressure adjusting piston 29 which is slidably guided in the adjusting valve body 28 in the left-right direction in the figure. A through hole 30 extending in the axial direction is provided in the pressure adjusting piston 29, and a first adjusting step portion 31 and a second adjusting step portion 32 are formed on the outer peripheral surface. The adjusting valve body 28 includes a first adjusting chamber 33 that applies pressure to the first adjusting step portion 31, a second adjusting chamber 34 that applies pressure to the second adjusting step portion 32, and a pressure adjusting piston 29. A third adjusting chamber 35, which is formed to face one end and is connected to the second chamber 16 by the pipe line 26, is provided, and the first adjusting chamber 33 and the second adjusting chamber 34 are in constant communication with the low-voltage circuit. The third adjusting chamber 35 can communicate with the first adjusting chamber 33 according to the movement of the pressure adjusting piston 29. Further, the pressure adjusting valve 27 includes a fourth adjusting chamber 36 formed facing one end of the pressure adjusting piston 29 and a fifth adjusting chamber 37 formed opposite the end of the pressure adjusting piston 29. Is formed, and the fourth adjusting chamber 36 and the fifth adjusting chamber 37 are in constant communication with the high-voltage circuit. Furthermore, the pressure adjusting valve 27 is provided with a spring 39 that is pressed against the opposite end of the pressure adjusting piston 29 and pressed by the force F to the left in the figure, and the panel 39 is screwed into the lock nut 40. The spring force F is changed by moving the screw 38 back and forth. The pressure receiving areas of the pressure adjusting pistons 29 are A8> A9 when the fourth adjusting chamber 36 is the pressure receiving surface A8 and the fifth adjusting chamber 37 is the pressure receiving surface A9.
【００１６】 かく構成の油圧ブレーカの作動態様について説明する。 油圧ポンプからの供給油量が油圧ブレーカの必要油量より少なく作動圧力が油 圧ブレーカの適正作動圧力の範囲より小さいとき、油圧ブレーカでは圧力調整弁 ２７の第４調整室３６の受圧面Ａ８と第５調整室３７の受圧面Ａ９とがＡ８＞Ａ ９であるため、圧力調整ピストン２９が図の右方へ移動しようとする。しかし、 圧力調整ピストン２９にはバネ３９の力Ｆが加わっているので、供給油量が少な いときには、圧力調整ピストン２９は図１の状態で平衡し、第３調整室３５は圧 力調整ピストン２９によって閉ざす位置にある。第３調整室３５が閉ざされてい ると、第２室１６、横穴２５、貫通穴１１、第４室１８および管路７を介して連 通する第１圧力室４が閉ざされているので、打撃ピストン３は上方への移動が阻 止されている。そして、高圧回路の圧力は上昇して高圧アキュムレータ２４も蓄 圧される。The operation mode of the hydraulic breaker thus configured will be described. When the amount of oil supplied from the hydraulic pump is less than the required amount of oil for the hydraulic breaker and the operating pressure is less than the range of the appropriate operating pressure for the hydraulic breaker, the hydraulic breaker will cause the pressure adjusting valve 27 to contact the pressure receiving surface A8 of the fourth adjusting chamber 36. Since the pressure receiving surface A9 of the fifth adjusting chamber 37 is A8> A9, the pressure adjusting piston 29 tries to move to the right in the drawing. However, since the force F of the spring 39 is applied to the pressure adjusting piston 29, when the amount of supplied oil is small, the pressure adjusting piston 29 is in equilibrium in the state of FIG. It is in a closed position by 29. When the third adjusting chamber 35 is closed, the second chamber 16, the lateral hole 25, the through hole 11, the fourth chamber 18, and the first pressure chamber 4 communicating with each other through the pipe line 7 are closed. The striking piston 3 is prevented from moving upward. Then, the pressure of the high-voltage circuit rises and the high-pressure accumulator 24 is also accumulated.
【００１７】 高圧回路の圧力が上昇すると、圧力調整弁２７はＡ８＞Ａ９の受圧面積差によ る駆動力差の絶対値がバネ３９の力Ｆに勝り、圧力調整ピストン２９がバネ力Ｆ に抗して右方へ移動する。そして、高圧回路の圧力が油圧ブレーカの適正作動圧 力の範囲に達すると、第３調整室３５が第１調整室３３に通じる。これにより、 第３調整室３５と連通されている第１圧力室４が低圧回路に通じるため、打撃ピ ストン３は上方へ移動し始める。When the pressure in the high pressure circuit rises, the pressure adjusting valve 27 causes the absolute value of the driving force difference due to the pressure receiving area difference of A8> A9 to exceed the force F of the spring 39, and the pressure adjusting piston 29 becomes a spring force F 2. Move to the right against. Then, when the pressure of the high pressure circuit reaches the range of the proper operating pressure of the hydraulic breaker, the third adjusting chamber 35 communicates with the first adjusting chamber 33. As a result, the first pressure chamber 4 communicating with the third adjustment chamber 35 communicates with the low pressure circuit, so that the impact piston 3 begins to move upward.
【００１８】 打撃ピストン３が移動中コントロールピストン１０は、図１の状態を保つが、 打撃ピストン３がストロークＳ１移動すると、第２圧力室５が第１溝２１に通じ るため、コントロールバルブ８の第３室１７は高圧になり、Ａ５＞Ａ３の受圧面 積差により、コントロールピストン１０は上方へ切り換わる。コントロールピス トン１０の切り換わりにより、第１圧力室４と第６室２０とが連通し、第１圧力 室４が高圧になり、打撃ピストン３は受圧面積差により下方へ移動し始める。打 撃ピストン３は、チゼル２を打撃する直前で小径中間部２３を介して第１溝２１ と第２溝２２とが連通し、コントロールバルブ８の第３室１７は第２溝２２、第 １溝２１を介して低圧になり、コントロールピストン１０は元の位置に切り換わ る。このため、第１圧力室４は再び低圧になるので、チゼル２を打撃した打撃ピ ストン３は上方へ移動し始める。以後、同様の動作を繰り返される。While the striking piston 3 is moving, the control piston 10 maintains the state shown in FIG. 1. However, when the striking piston 3 moves by the stroke S1, the second pressure chamber 5 communicates with the first groove 21. The third chamber 17 has a high pressure, and the control piston 10 switches upward due to the pressure receiving surface area difference of A5> A3. By switching the control piston 10, the first pressure chamber 4 and the sixth chamber 20 communicate with each other, the first pressure chamber 4 has a high pressure, and the striking piston 3 starts to move downward due to the difference in pressure receiving area. Immediately before hitting the chisel 2, the striking piston 3 communicates with the first groove 21 and the second groove 22 via the small-diameter intermediate portion 23, and the third chamber 17 of the control valve 8 has the second groove 22 and the first groove 22. A low pressure is applied via the groove 21 and the control piston 10 switches back to its original position. For this reason, the first pressure chamber 4 becomes low in pressure again, and the striking piston 3 striking the chisel 2 starts moving upward. After that, the same operation is repeated.
【００１９】 かくして、圧力調整バルブ２７を油圧ブレーカの戻り回路に設けることにより 、油圧ブレーカへの供給油量が少なくともその作動圧力が適正作動圧力の範囲内 に上昇させて作動できる。従って、従来の如き絞り弁の開度を調整する必要がな く、誰でも簡単に取り扱うことが可能になる。Thus, by providing the pressure regulating valve 27 in the return circuit of the hydraulic breaker, the hydraulic breaker can be operated by increasing the amount of oil supplied to the hydraulic breaker at least within the range of the proper operating pressure. Therefore, it is not necessary to adjust the opening of the throttle valve as in the conventional case, and anyone can easily handle it.
【００２０】 一方、油圧ブレーカへの供給油量が必要油量より多い場合、作動圧力が適正作 動圧力の範囲を越えることがある。この場合、圧力調整バルブ２７はＡ８＞Ａ９ による駆動力差の絶対値がバネ３９の力Ｆを上回り、圧力調整ピストン２９がス トロークＳ２移動する。この結果、第４調整室３６が第１調整段部３１に通じ、 高圧回路の余分な圧油が低圧回路に逃がされるため、油圧ブレーカへの供給油量 が必要油量より多くとも、作動圧力が適正作動圧力の範囲以上に上昇されること が防止される。しかも、圧力調整バルブ２７のバネ３９の調整はメーカー出荷時 に予め圧力調整できるので、ショベルに取付時にリリーフ弁の調整が不要になる だけでなく、配管途上にリリーフ弁やストップ弁をなくすことができる。On the other hand, when the amount of oil supplied to the hydraulic breaker is larger than the required amount of oil, the operating pressure may exceed the range of appropriate operating pressure. In this case, in the pressure adjusting valve 27, the absolute value of the driving force difference due to A8> A9 exceeds the force F of the spring 39, and the pressure adjusting piston 29 moves to the stroke S2. As a result, the fourth adjusting chamber 36 communicates with the first adjusting step portion 31, and excess pressure oil in the high pressure circuit is released to the low pressure circuit, so that even if the amount of oil supplied to the hydraulic breaker is greater than the required oil amount, the operating pressure Is prevented from rising above the proper operating pressure range. Moreover, since the spring 39 of the pressure adjusting valve 27 can be adjusted in advance at the time of shipment from the manufacturer, not only the relief valve need not be adjusted when the excavator is attached, but also the relief valve and the stop valve can be eliminated in the middle of the piping. it can.
【００２１】[0021]
上記の構成によれば、本考案は圧力調整弁は高圧回路の圧力が適正作動圧力の 範囲より小さいとき、圧力調整ピストンをコントロールバルブを介した第１圧力 室を閉ざす位置に位置し、高圧回路の圧力が適正作動圧力の範囲であるとき、圧 力調整ピストンが第１圧力室を低圧回路に接続する位置に移動するので、供給油 量が少ない場合でも圧油を上昇させて適正作動圧力の範囲にでき、調整の難しい 絞り弁が不要になる。しかも、圧力調整弁はメーカー出荷時に予め圧力調整でき るので、熟練者によらずとも簡単に使用できる。 According to the above construction, the pressure adjusting valve of the present invention is located at the position where the pressure adjusting piston closes the first pressure chamber via the control valve when the pressure of the high pressure circuit is smaller than the range of the proper operating pressure. When the pressure in the range is within the proper operating pressure range, the pressure adjustment piston moves to the position that connects the first pressure chamber to the low pressure circuit. It is possible to set the range, and it becomes unnecessary to use a throttle valve that is difficult to adjust. Moreover, since the pressure adjusting valve can adjust the pressure in advance at the time of shipment from the manufacturer, it can be easily used even by an unskilled person.
【００２２】 さらに、上記の構成によれば、圧力調整弁は高圧回路の圧力が適正作動圧力の 範囲よりも大きいとき、圧力調整ピストンが高圧回路の余分な圧油を低圧回路に 逃がす位置に移動されるので、ショベルに取付時にリリーフ弁の調整が不要にな るだけでなく、配管途上にリリーフ弁やストップ弁をなくすことができる。Further, according to the above configuration, when the pressure in the high pressure circuit is higher than the range of the proper operating pressure, the pressure adjustment piston moves to the position where the pressure adjustment piston releases excess pressure oil in the high pressure circuit to the low pressure circuit. As a result, not only the relief valve does not need to be adjusted when it is attached to the shovel, but also the relief valve and stop valve can be eliminated during piping.
【提出日】平成４年８月６日[Submission date] August 6, 1992
【手続補正１】[Procedure Amendment 1]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】０００９[Correction target item name] 0009
【補正方法】変更[Correction method] Change
【０００９】[0009]
上記の構成によれば、圧力調整弁は高圧回路のブレーカ作動圧力が適正作動圧 力の範囲より小さければ、圧力調整ピストンをコントロールバルブを介した第２ 圧力室を閉ざす位置に位置して作動圧力を上昇でき、高圧回路の圧力が適正作動 圧力の範囲に達すれば、圧力調整ピストンが第１圧力室を低圧回路に接続する位 置に移動するので、絞り弁の調整が不要になるだけでなく、絞り弁自体が不要に なる。According to the above configuration, if the breaker operating pressure of the high pressure circuit is smaller than the range of the proper operating pressure, the pressure adjusting piston is positioned so that the pressure adjusting piston closes the second pressure chamber via the control valve. If the pressure in the high pressure circuit reaches the range of the proper operating pressure, the pressure adjusting piston moves to the position connecting the first pressure chamber to the low pressure circuit, and not only the adjustment of the throttle valve becomes unnecessary. , The throttle valve itself becomes unnecessary.
【手続補正２】[Procedure Amendment 2]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１３[Correction target item name] 0013
【補正方法】変更[Correction method] Change
【００１３】 コントロールバルブ８は、高圧回路と低圧回路とを第１圧力室４に交番的に切 換接続可能に形成されている。図１の例では、コントロールバルブ８がバルブ本 体９と該バルブ本体９に摺動案内されるコントロールピストン１０とを有してい る。コントロールピストン１０内には、軸線方向に延びる貫通穴１１が設けられ 、外周面には受圧面積の異なる３つの受圧面として第１段部１２、第２段部１３ 、第３段部１４とが形成されている。バルブ本体９には、第１段部１２に圧力を 作用し、高圧回路と接続されている第１室１５と、第２段部１３に圧力を作用す る第２室１６と、第３段部１４に圧力を作用する第３室１７と、コントロールピ ストン１０の一側端に面して形成され前記管路６により第１圧力室４に接続され る第４室１８と、コントロールピストン１０の反対端に面して形成される第５室 １９と、該第５室１９にコントロールピストン１０の動きに応じて連通可能な第 ６室２０とが形成されている。なお、コントロールピストン１０の各受圧面積は 第１室１５を受圧面Ａ３、第２室１６を受圧面Ａ４と、第３室１７を受圧面Ａ５ と、第４室１８を受圧面Ａ６と、第５室１９を受圧面Ａ７とすると、受圧面Ａ３ ，Ａ５，Ａ６，Ａ７はＡ５＞Ａ３，Ａ６＝Ａ７である。The control valve 8 is formed so that the high pressure circuit and the low pressure circuit can be alternately connected to the first pressure chamber 4 by switching. In the example of FIG. 1, the control valve 8 has a valve body 9 and a control piston 10 slidably guided by the valve body 9. A through hole 11 extending in the axial direction is provided in the control piston 10, and a first step portion 12, a second step portion 13, and a third step portion 14 are provided on the outer peripheral surface as three pressure receiving surfaces having different pressure receiving areas. Has been formed. In the valve body 9, a first chamber 15 that exerts pressure on the first stage 12 and is connected to a high-pressure circuit, a second chamber 16 that exerts pressure on the second stage 13, and a third stage A third chamber 17 for exerting pressure on the portion 14, a fourth chamber 18 formed facing one end of the control piston 10 and connected to the first pressure chamber 4 by the pipe 6, and a control piston 10 A fifth chamber 19 formed facing the opposite end of the second chamber 19 and a sixth chamber 20 communicable with the fifth chamber 19 according to the movement of the control piston 10 are formed. The pressure receiving areas of the control piston 10 are the pressure receiving surface A3 for the first chamber 15, the pressure receiving surface A4 for the second chamber 16, the pressure receiving surface A5 for the third chamber 17, the pressure receiving surface A6 for the fourth chamber 18, and Assuming that the five chambers 19 are the pressure receiving surface A7, the pressure receiving surfaces A3, A5, A6, A7 are A5> A3, A6 = A7.
【提出日】平成４年８月１８日[Submission date] August 18, 1992
【手続補正１】[Procedure Amendment 1]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】０００９[Correction target item name] 0009
【補正方法】変更[Correction method] Change
【０００９】[0009]
上記の構成によれば、圧力調整弁は高圧回路のブレーカ作動圧力が適正作動圧 力の範囲より小さければ、圧力調整ピストンをコントロールバルブを介した第１ 圧力室を閉ざす位置に位置して作動圧力を上昇でき、高圧回路の圧力が適正作動 圧力の範囲に達すれば、圧力調整ピストンが第１圧力室を低圧回路に接続する位 置に移動するので、絞り弁の調整が不要になるだけでなく、絞り弁自体が不要に なる。According to the above configuration, if the breaker operating pressure of the high pressure circuit is smaller than the range of the proper operating pressure, the pressure adjusting piston is positioned so that the pressure adjusting piston closes the first pressure chamber via the control valve. If the pressure in the high pressure circuit reaches the range of the proper operating pressure, the pressure adjusting piston moves to the position connecting the first pressure chamber to the low pressure circuit, and not only the adjustment of the throttle valve becomes unnecessary. , The throttle valve itself becomes unnecessary.
【図１】図１は本考案に係る油圧ブレーカの断面図であ
る。FIG. 1 is a sectional view of a hydraulic breaker according to the present invention.
【図２】図２は従来の油圧ブレーカの断面図である。FIG. 2 is a sectional view of a conventional hydraulic breaker.
【図３】図３は従来の油圧ブレーカ・破砕機併用配管の
回路図である。FIG. 3 is a circuit diagram of conventional hydraulic breaker / crusher combined piping.
１ 油圧ブレーカ本体 ２ チゼル ３ 打撃ピストン ４ 第１圧力室 ５ 第２圧力室 ８ コントロールバルブ ２７ 圧力調整バルブ ２９ 圧力調整ピストン Ａ１ 第１受圧面 Ａ２ 第２受圧面 1 hydraulic breaker body 2 chisel 3 striking piston 4 first pressure chamber 5 second pressure chamber 8 control valve 27 pressure adjusting valve 29 pressure adjusting piston A1 first pressure receiving surface A2 second pressure receiving surface
Claims (2)
を打撃する打撃ピストンと、該打撃ピストンの面積の大
なる第１受圧面に圧油を作用する第１圧力室と、前記打
撃ピストンの面積の小なる第２受圧面に圧油を作用する
第２圧力室とを有し、前記第１圧力室にはコントロール
バルブを介して高圧回路と低圧回路を交番的に切り換え
接続し、第２圧力室には常時高圧回路を接続する油圧ブ
レーカにおいて、 油圧ブレーカ本体に高圧回路の圧力の大きさに応じて移
動可能な圧力調整ピストンを有する圧力調整弁を設け、
該圧力調整弁は高圧回路の作動圧力が適正作動圧力の範
囲より小さいとき、圧力調整ピストンが前記コントロー
ルバルブを介した前記第１圧力室を閉ざす位置に位置さ
れ、高圧回路の作動圧力が適正作動圧力の範囲に達した
とき、圧力調整ピストンが前記第１圧力室を低圧回路に
接続する位置に移動されることを特徴とする油圧ブレー
カ。1. A striking piston for striking a chisel having two pressure receiving surfaces having different areas, a first pressure chamber for acting pressure oil on a first pressure receiving surface having a large area of the striking piston, and the striking piston. A second pressure chamber for applying pressure oil to a second pressure receiving surface having a small area, and a high pressure circuit and a low pressure circuit are alternately switched and connected to the first pressure chamber via a control valve. In a hydraulic breaker that always connects a high-pressure circuit to the two pressure chambers, a pressure-regulating valve having a pressure-adjusting piston that can move according to the magnitude of the pressure in the high-pressure circuit is provided in the hydraulic breaker body,
When the working pressure of the high pressure circuit is smaller than the range of the proper working pressure, the pressure regulating valve is positioned so that the pressure regulating piston closes the first pressure chamber via the control valve, and the working pressure of the high pressure circuit is properly operated. A hydraulic breaker characterized in that, when a pressure range is reached, the pressure adjusting piston is moved to a position connecting the first pressure chamber to the low pressure circuit.
て、前記圧力調整弁は高圧回路の作動圧力が適正作動圧
力の範囲よりも大きいとき、圧力調整ピストンが高圧回
路の余分な圧油を低圧回路に逃がす位置に移動されるこ
とを特徴とする油圧ブレーカ。2. The hydraulic breaker according to claim 1, wherein when the working pressure of the high pressure circuit of the pressure regulating valve is larger than the range of the proper working pressure, the pressure regulating piston removes excess pressure oil of the high pressure circuit from the low pressure circuit. A hydraulic breaker characterized by being moved to a position where it escapes.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4622592U JP2559018Y2 (en) | 1992-07-02 | 1992-07-02 | Hydraulic breaker |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4622592U JP2559018Y2 (en) | 1992-07-02 | 1992-07-02 | Hydraulic breaker |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH065876U true JPH065876U (en) | 1994-01-25 |
| JP2559018Y2 JP2559018Y2 (en) | 1998-01-14 |
Family
ID=12741175
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4622592U Expired - Lifetime JP2559018Y2 (en) | 1992-07-02 | 1992-07-02 | Hydraulic breaker |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2559018Y2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009090458A (en) * | 2007-10-05 | 2009-04-30 | Sandvik Mining & Construction Oy | Rock crushing apparatus, prevention valve and operation method of the rock crushing apparatus |
| CN107988062A (en) * | 2017-12-28 | 2018-05-04 | 广州聚能纳米生物科技股份有限公司 | A kind of cell breaking plant explosion-protection equipment |
-
1992
- 1992-07-02 JP JP4622592U patent/JP2559018Y2/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009090458A (en) * | 2007-10-05 | 2009-04-30 | Sandvik Mining & Construction Oy | Rock crushing apparatus, prevention valve and operation method of the rock crushing apparatus |
| CN107988062A (en) * | 2017-12-28 | 2018-05-04 | 广州聚能纳米生物科技股份有限公司 | A kind of cell breaking plant explosion-protection equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2559018Y2 (en) | 1998-01-14 |
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