JPH0639796Y2 - Structure of crusher body - Google Patents

Description

【考案の詳細な説明】 〔産業上の利用分野〕 本考案は破砕機本体の構造に関し、特に電力利用に不便
な場所に於いて、繰り返しの衝撃力により物体の破砕に
用いられる破砕機本体の構造の改良に関する。[Detailed Description of the Invention] [Industrial field of application] The present invention relates to the structure of a crusher main body, and particularly to a crusher main body used for crushing an object by repeated impact force in a place where power use is inconvenient. Regarding the improvement of the structure.

〔従来の技術〕[Conventional technology]

破砕機は土木工事などに幅広く使用されている。通常破
砕機はブルドーザ本体のリフトアーム末端部に設けら
れ、硬いコンクリートや岩石等の破砕に使用されてい
た。従来この破砕機本体は、ほとんどが電動操作される
タイプなので、現場に電気が容易に利用出来る所か、或
いは、発電機を設けるなどによって大電力を得られる所
に限られ、この電力によるモータの動力と、ばねの弾性
反発力との繰り返しにより、質量大なピストンロッドの
持ち上げ及び槌打ち動作を反復させ、破砕機のハンマー
としてその先端の鏨ロッドに繰り返しの衝撃を与えて、
破砕の作用を得るものである。然し乍ら、この様な破砕
機は、本体のばねによる反発力が小さい欠点を有し、該
反発力による衝撃力の大きさに限界があり、若しばね力
を増大すると、それに必要な電力もそれに伴って大きく
なり、電力が充分でないと使いこなせず、装備上も大型
化になりがちになると共に、負荷が不安定（周期的波
動）になるなどと色々な問題点をもたらしていた。Crushers are widely used for civil engineering work. Usually, a crusher was installed at the end of the lift arm of the bulldozer body and was used to crush hard concrete and rocks. Conventionally, most of the crusher main body is electrically operated, so it is limited to places where electricity can be easily used or where large power can be obtained by installing a generator. By repeating the motive power and the elastic repulsion of the spring, the lifting and hammering operations of a large mass piston rod are repeated, giving a repeated impact to the chisel rod at the tip as a hammer of the crusher,
The effect of crushing is obtained. However, such a crusher has a drawback that the repulsive force due to the spring of the main body is small, and the magnitude of the impact force due to the repulsive force is limited, and if the spring force is increased, the power required for it also increases. As a result, it became larger, and it could not be used unless the power was sufficient, and the equipment tended to become large, and the load became unstable (periodic waves), causing various problems.

よって、一般には充分な衝撃力が得られる油圧タイプの
使用が考えられるが、油圧とて快速衝撃を行なう槌打ち
動作時と、戻り動作時とのピストンロッド往復行程に起
きる周期的管路圧力差が大きく、このため、戻りの低圧
側油圧回路に、大きな衝撃的圧力波動をきたすので、こ
お圧力波動を解消するためには、低圧管路に波動の衝撃
減衰のための蓄圧器を設けて、低圧管路の圧力衝撃の波
動変化を或る範囲内に保つようにしてこの問題点を解消
していた。Therefore, it is generally possible to use a hydraulic type that can obtain a sufficient impact force, but the periodic pipe line pressure difference that occurs in the reciprocating stroke of the piston rod between the hammering operation that gives a quick impact using hydraulic pressure and the returning operation. Therefore, a large shock-like pressure wave is generated in the return low-pressure side hydraulic circuit.In order to eliminate this pressure wave, a pressure accumulator for shock-damping the wave is provided in the low-pressure line. This problem has been solved by keeping the wave change of the pressure shock of the low pressure pipe within a certain range.

〔考案が解決しようとする課題〕[Problems to be solved by the device]

前記の如く従来の油圧タイプの破砕機は、戻り低圧側の
油圧回路に大きなショックによる圧力波動を緩衝するた
め、低圧管路に蓄圧器を設けることを要し、現場で使用
する角度から見て、経済性や機動性の点でなお改良の余
地が残されている。As described above, the conventional hydraulic type crusher requires a pressure accumulator to be installed in the low pressure pipe line in order to buffer the pressure wave caused by a large shock in the hydraulic circuit on the return low pressure side. However, there is still room for improvement in terms of economy and mobility.

本考案は、前記改良の余地に着目してなされたもので、
所要電力が少なくても済む油圧タイプの破砕機におい
て、本体の戻りの低圧側油圧回路に起こる大きな衝撃的
圧力波動を軽減することにより、衝撃緩和減衰のための
蓄圧器が解消され、大幅に経済性や機動性を向上させた
油圧タイプの破砕機本体を提供しようとするものであ
る。The present invention was made by paying attention to the room for improvement,
In a hydraulic type crusher that requires less power, by reducing the large shocking pressure waves that occur in the low-pressure side hydraulic circuit of the main unit's return, the pressure accumulator for shock relaxation is eliminated, greatly reducing the economy. The present invention aims to provide a hydraulic type crusher body having improved flexibility and mobility.

〔課題を解決するための手段〕[Means for Solving the Problems]

前記の目的を達成するための本考案が取った手段として
は、 その内部に、下端に開口部を有する細長い空間部を設け
た本体と、 その中間一部分がカラー状に突き出して両突き出し端面
をそれぞれ上受圧面と下受圧面とにした太径のピストン
部とされ、前記空間部に往復動可能に挿入させたピスト
ンロッドと、 その先端部が前記開口部より本体外部へ延出するように
一部を前記空間部に滑り嵌合させた鏨ロッドと、 前記本体内部の空間部は、前記ピストンロッド上端面側
をその端面部に圧力が作用するようガスを充填した気体
室と、前記ピストン部の付近を油圧室と、前記鏨ロッド
と対向する下端部側から鏨ロッドの後端部側に亘る衝撃
室とをそれぞれ径を拡大して形成し、それと同時に、該
油圧室は、ピストン部が上下往復動する行程の上下死点
部分を各拡大して低圧部と高圧部とし、それらの中間位
置を該往復動時交互に高、低圧部の一方に連続する輪溝
状の制御部に形成してなり、 本体には、内部に細長い空洞を設けて弁室とし、この弁
室内に上下動可能に弁体を嵌挿すると共に、本体の外部
にそれぞれ開口する油の入り口と出口とを設け、前記弁
体が行程上、下死点にあるときの弁室の下記各１か所を
介し、ピストンロッドが下死点にきた時該高圧部と油圧
入り口を、及びピストンロッドが上死点にきた時該低圧
部及び高圧部を同時に油出口とにそれぞれ連通させる入
力及び戻り油路を形成し、 前記弁体は、大小径の異なる２段部に分かれ、この連接
箇所からその両側面が各大小異なる面積をした低圧面部
と高圧面部とにされる突縁部を突設し、弁室のこの突縁
部の上下動範囲内の周りが該突縁部により容積可変の低
圧面部側の低圧弁室部と高圧面部側の高圧弁室部に拡大
され、そして、小径段部の先端部分と中段部分とがさら
に、各凹陥みぞを設けることにより上、下切換部に形成
され、弁室の対応する部分がそれぞれ第１、第２及び第
３の弁室部に拡張され、弁体の上下動時該上、下切換部
の何れかにより第２の弁室部が第１、第３の弁室部の一
方と連続するようにさせてなり、 前記戻り油路は、前記油圧室の低圧部と連通すると共
に、戻り岐路により前記弁室の第１の弁室部に連通する
ようにさせ、 前記油圧室の制御部と前記弁室の１か所である低圧弁室
部との連通として低圧管路を設け、 前記油圧室の高圧部と前記弁室の他の１か所である第２
の弁室部との連通として入力管路を設け、 前記入力油路は、前記弁室の第３の弁室部に分岐入力路
にて連接すると共に、分岐油路により弁室の高圧弁室部
に連通させ、 前記油圧入り口を油圧ポンプの高圧吐出口と、かつ、前
記油出口を油圧ポンプのドレンタンクとそれぞれ連接さ
せるように破砕機本体を構成してなる。Means for achieving the above-mentioned object are as follows: a main body having an elongated space portion having an opening at its lower end, and a middle portion thereof protruding in a collar shape to form both protruding end surfaces, respectively. A piston rod having a large diameter with an upper pressure receiving surface and a lower pressure receiving surface, and a piston rod reciprocally inserted into the space, and a tip of the piston rod extending outside the main body through the opening. Part of the main body is slidably fitted into the space part, and the space part inside the main body has a gas chamber filled with gas so that pressure acts on the upper end surface side of the piston rod, and the piston part. And a shock chamber extending from the lower end side facing the chisel rod to the rear end side of the chisel rod are formed with an enlarged diameter, and at the same time, the hydraulic chamber has a piston portion. On the process of reciprocating up and down The bottom dead center part is enlarged to form a low pressure part and a high pressure part, and an intermediate position between them is formed in a wheel groove-shaped control part continuous to one of the high and low pressure parts alternately during the reciprocating motion. Is a valve chamber having an elongated hollow inside, and a valve body is vertically movably fitted into the valve chamber, and an oil inlet and an oil outlet respectively open to the outside of the main body are provided. When the piston rod comes to the bottom dead center, the high pressure part and the hydraulic inlet, and when the piston rod comes to the top dead center, the low pressure part. And an input and return oil passage for communicating the high pressure portion with the oil outlet at the same time, respectively, and the valve body is divided into two step portions having different sizes, and both side surfaces of the connecting portion have different areas of different sizes. A projecting edge part that is made up of the low pressure surface part and the high pressure surface part is provided so that The circumference of the range is expanded to the low-pressure valve chamber portion on the low-pressure surface side and the high-pressure valve chamber portion on the high-pressure surface side of the volume variable by the projecting edge portion, and the tip portion and the middle portion of the small diameter step portion are further By providing a recessed groove, the upper and lower switching portions are formed, and the corresponding portions of the valve chamber are expanded to the first, second and third valve chamber portions, respectively, and when the valve body moves up and down, the switching is performed. The second valve chamber part is connected to one of the first and third valve chamber parts by any one of the parts, and the return oil passage communicates with the low pressure part of the hydraulic chamber and returns. A low pressure pipe is provided as a communication between the control part of the hydraulic chamber and the low pressure valve chamber part which is one part of the valve chamber, and is made to communicate with the first valve chamber part of the valve chamber by a branch. The high pressure part of the hydraulic chamber and the other one of the valve chambers, the second
An input conduit is provided for communication with the valve chamber part of the valve chamber, and the input oil passage is connected to the third valve chamber part of the valve chamber by a branch input passage, and the high pressure valve chamber of the valve chamber is connected by the branch oil passage. The crusher main body is configured so that the hydraulic inlet is connected to the high pressure discharge port of the hydraulic pump, and the oil outlet is connected to the drain tank of the hydraulic pump.

〔作用〕[Action]

前記のように構成された破砕機本体は、通常制御弁は入
力油路、分岐油路から高圧弁室部へ油圧をかけ、高圧面
部に対し作用させ、弁体を上死点に上動させる。これに
より、分岐入力路から第３と第２の弁室部を連通させ、
入力管路より油圧室の高圧部に作動油を送り、気体室の
ガス圧作用で下死点にあるピストンロッドを、ピストン
部の下受圧面より作動させ、ガス圧に抗して上死点へ上
動させる。また、前記上動運動は、単に前記油圧作用、
又は本機を破砕物に鏨ロッドから押付ける動作、或いは
両方によりさせることもできる。In the crusher main body configured as described above, the control valve normally applies hydraulic pressure from the input oil passage and the branch oil passage to the high pressure valve chamber portion to act on the high pressure surface portion to move the valve element upward to the top dead center. . As a result, the third and second valve chamber portions are communicated with each other from the branch input path,
The hydraulic oil is sent from the input line to the high pressure part of the hydraulic chamber, and the piston pressure at the bottom dead center is actuated from the bottom pressure receiving surface of the piston part by the gas pressure action of the gas chamber to resist the gas pressure and reach the top dead center. Move to. Further, the upward movement is simply the hydraulic action,
Alternatively, the machine may be pressed against the crushed material with a chisel rod, or both.

ピストンロッドが上死点に来ると、ピストン部の上動で
制御部と高圧部が連通され、油圧室の作動油は低圧管路
より制御弁の低圧弁室部へ入り、弁体を圧力作用面積の
大きな低圧面部より圧し、下死点へ下動させる。この結
果、第２と第３の弁室部間が遮断され、入力管路から油
圧室高圧部への作動油は停止し、同時に上切換部の下動
により第２と第１の弁室部間が連通し、高圧部より戻り
油路への経路が形成され、高圧部の圧力は解消される。When the piston rod reaches the top dead center, the control part and the high pressure part communicate with each other by the upward movement of the piston part, and the hydraulic oil in the hydraulic chamber enters the low pressure valve chamber part of the control valve from the low pressure pipe line and pressure acts on the valve element. Press down from the low pressure surface with a large area to move it to the bottom dead center. As a result, the second and third valve chamber parts are shut off, the hydraulic oil from the input pipe to the hydraulic chamber high pressure part is stopped, and at the same time, the downward movement of the upper switching part causes the second and first valve chamber parts to move. The passages are communicated with each other, a path is formed from the high pressure portion to the return oil passage, and the pressure in the high pressure portion is released.

ピストンロッドが上死点に上動の際、気体室は容積の減
少により気圧が上昇蓄積されているが、前記高圧部の圧
力解消によって釈放されるため、ピストンロッドの後端
面部に気圧が作用してこれを押し、急速下動させること
になり、先端部により鏨ロッドを打ち付ける破砕動作を
行なう。この時、油圧室の高圧部における作動油は、ピ
ストン部の下動により、急速に排斥されるため入力管路
と戻り油路の油量流並びに油圧が急増するが、分岐油路
がピストン部の下降により容積増大する低圧部へ連通し
ているので、その一部を分担導入し、油出口側への流量
と油圧の急激な変化を緩和するように作用する。When the piston rod moves up to the top dead center, the air pressure rises and accumulates in the gas chamber due to the decrease in volume, but since the pressure is released by the pressure release in the high pressure part, the air pressure acts on the rear end face of the piston rod. Then, this is pushed to move it down rapidly, and the tip portion hits the chisel rod to perform a crushing operation. At this time, the hydraulic oil in the high pressure part of the hydraulic chamber is rapidly repelled by the downward movement of the piston part, so that the oil amount flow and the oil pressure of the input pipe line and the return oil line sharply increase. Since it is communicated with the low-pressure portion whose volume increases due to the lowering, a part of it is shared and introduced to act to mitigate a sudden change in the flow rate and oil pressure to the oil outlet side.

前記破砕機の破砕動作が完了すれば、プストン部は下死
点位置にあるので、低圧管路により低圧弁室部が油圧室
の制御部と連通され、低圧面部に作用する圧力が低下
し、対向側の高圧弁室部の圧力上昇が優勢になると、弁
体を上死点位置へ押すことが出来るようになり、前記動
作を最初から反復させる。When the crushing operation of the crusher is completed, the low pressure valve chamber portion is communicated with the control portion of the hydraulic chamber by the low pressure pipe because the pston portion is at the bottom dead center position, and the pressure acting on the low pressure surface portion decreases, When the pressure increase in the high pressure valve chamber portion on the opposite side becomes dominant, the valve body can be pushed to the top dead center position, and the above operation is repeated from the beginning.

この考案の上記またはその他の目的、特徴および利点
は、図面を参照しての以下の実施例に詳細な説明から一
層あきらかとなろう。The above and other objects, features and advantages of the present invention will be more apparent from the detailed description in the following embodiments with reference to the drawings.

〔実施例〕〔Example〕

破砕機の本体１は内部に、下端に開口部11を有する細長
い空間部10を設け、該空間部10は、所定行程の上下動が
可能にピストンロッド５を嵌挿し、続いて鏨ロッド６
を、その先端部が該開口部11より延出するように遊挿
し、ピン61により本体１から抜けないように保持させて
いる。The body 1 of the crusher is provided with an elongated space portion 10 having an opening 11 at the lower end therein, and the space portion 10 has a piston rod 5 fitted therein so that the piston rod 5 can be moved up and down by a predetermined stroke, followed by a chisel rod 6.
Is loosely inserted so that its tip extends from the opening 11, and is held by a pin 61 so as not to come off from the main body 1.

又、ピストンロッド５は、中段部に径がカラー状に太く
突き出し両端面を上、下受圧面13,14としたピストン部5
1にされ、下死点に下動したとき、鏨ロッド６の後面を
叩くようになっている。Further, the piston rod 5 has a large diameter protruding in the shape of a collar in the middle part and has both end faces as upper and lower pressure receiving faces 13 and 14 as the piston part 5.
When it is set to 1 and moves downward to the bottom dead center, it hits the rear surface of the chisel rod 6.

前記空間部10は、ピストンロッド５の後端面に臨み窒素
ガス等を充満する空気の気体室101、ピストン部51が上
下動行程範囲に摺動する空間の油圧室100、及び先端部
と鏨ロッド６の後端部にわたる空間の衝撃室103にそれ
ぞれ径を拡大形成し、前記油圧室100は、さらにピスト
ン部51により上下両側の容積可変の２室に仕切られると
共に、ピストン部51が上下死点位置にあるとき、それぞ
れ前記上、下受圧面13,14に臨むように低、高圧部104,1
02をリング溝状に拡大され、両者の中間に位置して交互
に前記容積可変の２室によって低、高圧部104,102と連
通されるような制御部105が拡大形成されている。前記
各部104,105,102には、それぞれ戻り油口７、制御油口
８及び入力油口９が開口されている。The space portion 10 includes a gas chamber 101 for air that faces the rear end surface of the piston rod 5 and is filled with nitrogen gas, a hydraulic chamber 100 for a space in which the piston portion 51 slides in a vertical movement range, and a tip portion and a chisel rod. 6, the diameter of each of the impact chambers 103 in the space extending over the rear end of the hydraulic chamber 100 is enlarged, and the hydraulic chamber 100 is further partitioned by the piston portion 51 into two chambers of variable volume on the upper and lower sides. When in the position, the low and high pressure portions 104 and 1 face the upper and lower pressure receiving surfaces 13 and 14, respectively.
02 is enlarged in the shape of a ring groove, and a control section 105 is formed so as to be located in the middle of the two and alternately communicate with the low and high pressure sections 104 and 102 by the two chambers of variable volume. A return oil port 7, a control oil port 8 and an input oil port 9 are opened in each of the parts 104, 105 and 102.

次いで、図に於いて、制御弁４は、径の大小異なった棒
状弁体40を、上下動自在に嵌挿させた細長な空洞の弁室
400からなり、弁体40の大小径の連接箇所よりその両側
面の面積が互いに小大異なる高、低圧面部412,411にな
るフランジ部42が突設され、小径部分側の先端部と中段
部にそれぞれリング溝による上、下切換部43,41が設け
られ、弁室400は、前記フランジ部42の上、下死点位置
の付近に各高、低圧面412,411に臨むか所の径を拡大し
て高、低圧弁室部405,404に形成され、また、前記上切
換部43の上死点位置に臨んで第１の弁室部401を、下切
換部41の両側面がそれぞれ上、下死点位置に臨む付近に
第２、第３の弁室部402,403を径を拡大して形成し、弁
体40が上死点位置にあるときは、下切換部41により第２
と第３の弁室部402と403とを連通させ、弁体40が下死点
位置にあるとき、上切換部43により第１と第２の弁室部
401と402とを連通させるようにしてなる。Next, in the figure, the control valve 4 is a valve chamber having an elongated cavity in which rod-shaped valve bodies 40 having different diameters are vertically movably fitted and inserted.
The high pressure and low pressure surface portions 412, 411 are formed by projecting flange portions 42, which are composed of 400, and the areas of both side surfaces of the valve element 40 are different in size from the connecting portion of large and small diameters. Upper and lower switching parts 43, 41 by the ring groove are provided, and the valve chamber 400 has an upper part on the flange part 42, each high in the vicinity of the bottom dead center position, and the diameter of the place facing the low pressure surface 412, 411 is enlarged. Formed in the high and low pressure valve chamber parts 405, 404, and facing the top dead center position of the upper switching part 43, the first valve chamber part 401, the both side surfaces of the lower switching part 41 are respectively at the top and bottom dead center positions. The second and third valve chamber portions 402 and 403 are formed to have an enlarged diameter in the vicinity of the valve body 40, and when the valve body 40 is at the top dead center position, the second switching portion 41 causes the second
And the third valve chamber portions 402 and 403 are communicated with each other, and when the valve body 40 is at the bottom dead center position, the upper switching portion 43 causes the first and second valve chamber portions to move.
401 and 402 are made to communicate.

本体１の前記油圧室100と制御弁４の弁室400には、破砕
機を油圧操作するための油圧回路がもうけられている。
図中、油の入り口Ｐは、図示しない油圧ポンプの高圧作
動油吐き出口に接続され、入力油路２により分岐入力路
21から第３の弁室部403へ、また分岐油路22から高圧弁
室部405へと連通させ、油の出口Ｔは、図示しない油圧
ポンプのドレンタンクへ接続され、本体１内で戻り油路
３により油圧室100の低圧部104と戻り油口において、か
つ戻り岐路231により弁体400の第１の弁室部401とそれ
ぞれ連通される。そして、油圧室100の高圧部102と弁室
400の第２の弁室部402が、入力油口９を経て入力管路25
により連通されると共に、油圧室100の制御部105は制御
油口８において、低圧管路24により弁室400の低圧弁室
部404と連通される。A hydraulic circuit for hydraulically operating the crusher is provided in the hydraulic chamber 100 of the main body 1 and the valve chamber 400 of the control valve 4.
In the figure, the oil inlet P is connected to a high pressure hydraulic oil outlet of a hydraulic pump (not shown), and is branched by the input oil passage 2.
21 to the third valve chamber 403 and from the branched oil passage 22 to the high pressure valve chamber 405, the oil outlet T is connected to a drain tank of a hydraulic pump (not shown), and the return oil is returned in the main body 1. The passage 3 communicates with the low pressure portion 104 of the hydraulic chamber 100 and the return oil port, and the return branch passage 231 communicates with the first valve chamber portion 401 of the valve body 400. The high pressure section 102 of the hydraulic chamber 100 and the valve chamber
The second valve chamber portion 402 of 400 passes through the input oil port 9 and enters the input line 25.
And the control unit 105 of the hydraulic chamber 100 is communicated with the low pressure valve chamber 404 of the valve chamber 400 by the low pressure pipe 24 at the control oil port 8.

前記実施例の構成による破砕機は、以下に説明するごと
く作動する。The crusher having the configuration of the above-mentioned embodiment operates as described below.

すなわち、第１図が示す状態に、通常制御弁４は入力油
路２、分岐油路22から高圧弁室部405へ油圧をかけ、高
圧面部412に対し作用させ、この際対向側の低圧弁室部4
04は戻り油路３へ通じ低圧状態にあるので、弁体40を下
死点位置より上死点方向へ上動させる。弁体40の上動に
より、下切換部41によって分岐入力路21から第３と第２
の弁室部403と402とを連通させ、入力管路25より油圧室
100の高圧部102に作動油を送り、気体室101のガス圧作
用で下死点にあるピストンロッド５を、ピストン部51の
下受圧面14より作動させ、ガス圧に抗して第２図が示す
状態のごとく上死点へ上動させる。また、前記上動運動
は、単に前記油圧作用、又は本破砕機を被破砕物に鏨ロ
ッド６から押付ける動作、或いは両方によりさせること
もできる。この際、ピストン部51から上側の油圧室100
内部作動油は、戻り油路３へ排出され、気体室101は容
積の減少により圧縮される。That is, in the state shown in FIG. 1, the normal control valve 4 applies hydraulic pressure from the input oil passage 2 and the branch oil passage 22 to the high pressure valve chamber portion 405 to act on the high pressure surface portion 412, and at this time, the low pressure valve on the opposite side. Chamber 4
Since 04 communicates with the return oil passage 3 and is in a low pressure state, the valve body 40 is moved upward from the bottom dead center position toward the top dead center. By the upward movement of the valve body 40, the lower switching unit 41 causes the third and second branch input paths 21 to
The valve chamber parts 403 and 402 of the
The hydraulic oil is sent to the high pressure portion 102 of 100, and the piston rod 5 at the bottom dead center is actuated from the lower pressure receiving surface 14 of the piston portion 51 by the gas pressure action of the gas chamber 101 to resist the gas pressure, and FIG. Move it to top dead center as shown by. Further, the upward movement can be performed by simply the hydraulic action, the operation of pressing the crusher against the object to be crushed from the chisel rod 6, or both. At this time, the hydraulic chamber 100 above the piston portion 51
The internal hydraulic oil is discharged to the return oil passage 3, and the gas chamber 101 is compressed due to the decrease in volume.

ピストンロッド５が上死点に来ると、第２図示のよう
に、ピストン部51の上動で油圧室100の制御部105と高圧
部102が連通され、油圧室100の作動油は低圧管路24より
制御弁４の低圧弁室部404へ入り、弁体40を圧力作用面
積の大きな低圧面部411により圧し、高圧弁室部405の油
圧に抗して下死点へ下動させる。この結果、第３図示の
状態のごとく、第２と第３の弁室部402と403間が遮断さ
れ、入力管路25から油圧室100の高圧部102への作動油は
停止し、同時に上切換部43の下動により第２と第１の弁
室部402と401間が連通し、高圧部102より戻り岐路231、
戻り油路３への経路が形成され、高圧部102の油圧は解
消される。When the piston rod 5 reaches the top dead center, the control unit 105 of the hydraulic chamber 100 and the high pressure unit 102 communicate with each other due to the upward movement of the piston unit 51 as shown in FIG. From 24, it enters the low pressure valve chamber 404 of the control valve 4, presses the valve body 40 by the low pressure surface 411 having a large pressure acting area, and moves downward to the bottom dead center against the hydraulic pressure of the high pressure valve chamber 405. As a result, as in the third illustrated state, the second and third valve chamber portions 402 and 403 are shut off, the hydraulic oil from the input pipeline 25 to the high pressure portion 102 of the hydraulic chamber 100 is stopped, and at the same time Due to the downward movement of the switching portion 43, the second and first valve chamber portions 402 and 401 communicate with each other, and the high pressure portion 102 returns to the branch line 231,
A path to the return oil passage 3 is formed, and the hydraulic pressure in the high pressure section 102 is canceled.

ピストンロッド５が上死点に上動の際、気体室101は容
積の減少により気圧が上昇蓄積されているが、前記高圧
部102の油圧解消によって釈放されるため、ピストンロ
ッド５の後端面部に気圧が作用してこれを押し、急速下
動させることになり、第４図示の状態のごとく、衝撃室
103における先端部により鏨ロッド６を打ち付ける破砕
動作を行なう。この時、油圧室100の高圧部102における
作動油は、ピストン部51の下動により、急速に排斥され
るため入力管路25と戻り岐路231油流量並びに油圧が急
増するが、戻り油路３がピストン部51の下降により容積
増大する低圧部104へ戻り油口７において連通し、負圧
吸入現象気味になっているので、その一部を分担導入
し、油出口Ｔ側への油流量と油圧の急激な変化を緩和す
るように作用する。When the piston rod 5 moves up to the top dead center, the pressure in the gas chamber 101 rises and accumulates due to the decrease in volume. However, since the hydraulic pressure in the high pressure portion 102 is released, the rear end surface portion of the piston rod 5 is released. Atmospheric pressure acts on and pushes it down, causing it to move downward rapidly.
A crushing operation of hitting the chisel rod 6 with the tip of 103 is performed. At this time, the hydraulic oil in the high-pressure portion 102 of the hydraulic chamber 100 is rapidly repulsed by the downward movement of the piston portion 51, so that the input pipe line 25 and the return branch line 231 oil flow rate and the hydraulic pressure rapidly increase. Is communicated to the low pressure portion 104 whose volume increases due to the lowering of the piston portion 51, and communicates with the oil port 7 at the oil port 7, and a negative pressure suction phenomenon is likely to occur. Therefore, part of this is shared and introduced, and the oil flow rate to the oil outlet T side is It acts to mitigate sudden changes in hydraulic pressure.

前記破砕機の破砕動作が完了すれば、ピストン部51は下
死点位置にあるので、低圧管路24により低圧弁室部404
が油圧室100の制御部105と連通され、低圧面部411に作
用する圧力が低下し、対向側の高圧弁室部405の圧力上
昇が優勢になると、高圧面部412に油圧が作動して弁体
を上死点位置へ押すことが出来るようになり、前記動作
を最初からふたたび反復させる。When the crushing operation of the crusher is completed, since the piston portion 51 is at the bottom dead center position, the low pressure pipe 24 causes the low pressure valve chamber portion 404.
Is communicated with the control unit 105 of the hydraulic chamber 100, the pressure acting on the low pressure surface portion 411 decreases, and when the pressure rise in the high pressure valve chamber portion 405 on the opposite side becomes dominant, the hydraulic pressure operates on the high pressure surface portion 412 and the valve element Can be pushed to the top dead center position, and the above operation is repeated again from the beginning.

〔考案の効果〕[Effect of device]

本考案の破砕機によれば、ピストンロッド５の上端面部
に臨む気体室101が設けられ、窒素などガスが充満さ
れ、ピストンロッド５が上死点に上動の際、気体室101
は容積の減少により気圧が上昇蓄積されるが、前記高圧
部102の油圧解消によって釈放されるとき、ピストンロ
ッド５の後端面部に前記蓄積された気圧が作用してこれ
を押し、急速下動させることになり、第４図示の状態の
ごとく、衝撃室103における先端部により鏨ロッド６を
打ち付ける破砕動作を行なう。またこの時、油圧室100
の高圧部102における作動油が、ピストン部51の下動に
より、急速に排出されるために、急増する入力管路25と
戻り岐路231油流量並びに油圧が、戻り油路３がピスト
ン部51の下降により容積増大する低圧部104へ戻り油口
７において連通し、負圧吸入現象気味になっているの
で、その一部を分担導入し、油出口Ｔ側への油流量と油
圧の急激な変化を緩和するように作用する。According to the crusher of the present invention, the gas chamber 101 facing the upper end surface portion of the piston rod 5 is provided, filled with gas such as nitrogen, and when the piston rod 5 moves up to the top dead center, the gas chamber 101
The air pressure rises and accumulates due to the decrease in the volume, but when the air pressure is released due to the elimination of the oil pressure in the high pressure portion 102, the accumulated air pressure acts on the rear end surface portion of the piston rod 5 to push it, causing a rapid downward movement. As a result, as in the state shown in FIG. 4, a crushing operation is performed in which the tip of the impact chamber 103 strikes the chisel rod 6. At this time, the hydraulic chamber 100
The hydraulic oil in the high-pressure part 102 of the above is rapidly discharged by the downward movement of the piston part 51, so that the input pipe line 25 and the return branch line 231 oil flow rate and the hydraulic pressure that rapidly increase, and the return oil line 3 of the piston part 51 It communicates with the return oil port 7 to the low-pressure portion 104 whose volume increases due to the downward movement, and the negative pressure suction phenomenon tends to occur. Therefore, part of this is shared and introduced, and the rapid change of the oil flow rate and the oil pressure to the oil outlet T side. Acts to relieve.

このように、ガス圧力を圧縮蓄積した気体室101の釈放
時の反発力の利用により、ピストンロッド５の下向きの
衝撃的な下動速度が非常に速いため、本体１以外の油圧
装置にある管路、又はブルドーザ本体の機械部品が、こ
のピストン部51の下受圧面14から生じた強い油圧のショ
ックを、ピストン部51の下動時、その上受圧面13の上側
油圧室100が容積増大することにより、作動油の量と圧
力の大部分が吸収されることになり、大幅に戻り油路３
より油出口Ｔへ排出される油量の減少及び油圧の緩衝を
するので、従来のような戻り油路の低圧側に、この大き
なショックによる圧力の緩衝のための蓄圧器を設けるこ
となく、低圧油圧回路をほぼ一定の圧力に保つことがで
きる。As described above, since the repulsive force at the time of releasing the gas chamber 101 in which the gas pressure is compressed and accumulated is used, the downward shocking downward movement speed of the piston rod 5 is very fast, so that a pipe in a hydraulic device other than the main body 1 can be used. The passage or the mechanical component of the bulldozer main body receives a strong hydraulic shock generated from the lower pressure receiving surface 14 of the piston portion 51, and when the piston portion 51 moves downward, the volume of the upper hydraulic chamber 100 of the upper pressure receiving surface 13 increases. As a result, most of the amount and pressure of hydraulic oil are absorbed and the return oil passage 3
Since the amount of oil discharged to the oil outlet T is reduced and the hydraulic pressure is buffered, the low pressure side of the return oil passage is not provided with a pressure accumulator for buffering the pressure due to the large shock as in the prior art. The hydraulic circuit can be kept at a substantially constant pressure.

これにより、従来の油圧装置における波動状負荷衝撃が
緩和ないし解消され、低電力に適した油圧タイプの破砕
機といえども、平穏且つ安全に使用することができる。As a result, the wave-like load impact in the conventional hydraulic device is alleviated or eliminated, and even a hydraulic type crusher suitable for low electric power can be used calmly and safely.

【図面の簡単な説明】[Brief description of drawings]

第１図は本考案破砕機の本体構造の一実施例にかかる構
成説明のための縦断側視概要図、第２図ないし第４図は
それぞれ同前の異なる位置のピストンロッド作動状態説
明の概要図である。 １……本体、２……入力油路、 ３……戻り油路、５……ピストンロッド、 ６……鏨ロッド、10……空間部、 11……開口部、13……上受圧面、 14……下受圧面、21……分岐入力路、 22……分岐油路、23……戻り油路、 24……低圧管路、25……入力管路、 40……棒状弁体、41……下切換部、 42……突縁部、43……上切換部、 51……ピストン部、100……油圧室、 101……気体室、102……高圧部、 103……衝撃室、104……低圧部、 105……制御部、400……弁室、 401……第１の弁室部、402……第２の弁室部、 403……第３の弁室部、404……低圧弁室部、 405……高圧弁室部、411……低圧面部、 412……高圧面部。FIG. 1 is a schematic view of a longitudinal section for explaining the configuration according to an embodiment of the main body of the crusher of the present invention, and FIGS. It is a figure. 1 ... Main body, 2 ... Input oil passage, 3 ... Return oil passage, 5 ... Piston rod, 6 ... Heart rod, 10 ... Space portion, 11 ... Opening portion, 13 ... Upper pressure receiving surface, 14 …… Lower pressure receiving surface, 21 …… Branch input passage, 22 …… Branch oil passage, 23 …… Return oil passage, 24 …… Low pressure pipe, 25 …… Input pipe, 40 …… Bar valve, 41 ...... Lower switching part, 42 ...... Projection part, 43 ...... Up switching part, 51 ...... Piston part, 100 ...... Hydraulic chamber, 101 ...... Gas chamber, 102 ...... High pressure part, 103 ...... Impact chamber, 104 ... Low pressure part, 105 ... Control part, 400 ... Valve chamber, 401 ... First valve chamber part, 402 ... Second valve chamber part, 403 ... Third valve chamber part, 404 ... Low pressure valve chamber, 405 High pressure valve chamber, 411 Low pressure face, 412 High pressure face.

Claims (1)

【実用新案登録請求の範囲】[Scope of utility model registration request] 【請求項１】その内部に、下端に開口部（11）を有する
細長い空間部（10）を設けた本体（１）と、 その中間一部分がカラー状に突き出して両突き出し端面
をそれぞれ上受圧面（13）と下受圧面（14）とにした太
径のピストン部（51）にされ、前記空間部（10）に往復
動可能に挿入させたピストンロッド（５）と、 その先端部が前記開口部（11）より本体（１）外部へ延
出するように一部を前記空間部（10）に滑り嵌合させた
鏨ロッド（６）と、 前記本体（１）内部の空間部（10）は、前記ピストンロ
ッド（５）上端面側をその端面部に圧力が作用するよう
ガスを充填した気体室（101）と、前記ピストン部（5
1）の付近を油圧室（100）と、前記鏨ロッド（６）と対
向する下端部側から鏨ロッド（６）の後端部側に亘る衝
撃室（103）とをそれぞれ径を拡大して形成し、それと
同時に、該油圧室（100）は、ピストン部（51）が上下
往復動する行程の上、下死点部分を各拡大して低圧部
（104）と高圧部（102）とし、それらの中間位置を該往
復動時交互に高、低圧部（104,102）の一方に連続する
輪溝状の制御部（105）に形成してなり、 本体（１）には、弁室（400）とする細長い空洞と、こ
の弁室（400）内に上下動可能に棒状弁体（40）を嵌挿
すると共に、本体（１）の外部にそれぞれ開口する油の
入り口（Ｐ）と出口（Ｔ）とを設け、前記弁体（40）が
行程上下死点にあるときの弁室（400）の下記各１か所
を介し、ピストンロッド（５）が下死点にきた時該高圧
部（102）と油圧入り口（Ｐ）を、及びピストンロッド
（５）が上死点にきた時該低圧部（102）及び高圧部（1
04）を同時に油出口（Ｔ）とにそれぞれ連通させる入力
及び戻り油路（2,3）を形成し、 前記弁体（40）は、大小径の異なる２段部に分かれ、こ
の連接箇所からその両側面が各大小異なる面積をした低
圧面部（411）と高圧面部（412）とにされる突縁部（4
2）を突設し、弁室（400）のこの突縁部（42）の上下動
範囲内の周りが該突縁部（42）により容積可変の低圧面
部側の低圧弁室部（404）と高圧面部側の高圧弁室部（4
05）に拡大され、そして、小径段部の先端部分と中段部
分とがさらに、各凹陥みぞを設けることにより上、下切
換部（43,41）に形成され、弁室（400）の対応する部分
がそれぞれ第１、第２及び第３の弁室部（401,402,40
3）に拡張され、弁体（40）の上下動時該上、下切換部
（43,41）の何れかにより第２の弁室部（402）が第１、
第３の弁室部（401,403）の一方と連通するようにさせ
てなり、 前記戻り油路（３）は、前記油圧室（100）の低圧部（1
04）と連通すると共に、戻り岐路（23）により前記弁室
（400）の第１の弁室部（401）に連通するようにさせ、 前記油圧室（100）の制御部（105）と前記弁室（400）
の１か所である低圧弁室部（404）との連通として低圧
管路（24）を設け、 前記油圧室（100）の高圧部（102）と前記弁室（400）
の他の１か所である第２の弁室部（402）との連通とし
て入力管路（25）を設け、 前記入力油路（２）は、前記弁室（400）の第３の弁室
部（403）に分岐入力路（21）にて連接すると共に、分
岐油路（22）により弁室（400）の高圧弁室部（405）に
連通させ、 前記油圧入り口（Ｐ）を油圧ポンプの高圧吐出口と、か
つ、前記油出口（Ｔ）を油圧ポンプのドレンタンクとそ
れぞれ連接させるように構成してなる破砕機本体の構
造。1. A main body (1) having an elongated space (10) having an opening (11) at a lower end therein, and a middle portion thereof protruding in a collar shape so that both protruding end faces are respectively upper pressure receiving surfaces. (13) and the lower pressure receiving surface (14) are formed into a large diameter piston part (51), and the piston rod (5) reciprocally inserted into the space part (10) and its tip part are A chisel rod (6) partly slidingly fitted into the space (10) so as to extend from the opening (11) to the outside of the body (1), and a space (10) inside the body (1). ) Is a gas chamber (101) in which the upper end surface side of the piston rod (5) is filled with gas so that pressure acts on the end surface part, and the piston part (5).
The diameter of the hydraulic chamber (100) in the vicinity of 1) and the impact chamber (103) extending from the lower end side facing the chisel rod (6) to the rear end side of the chisel rod (6) are enlarged. At the same time, in the hydraulic chamber (100), the bottom dead center portion is enlarged to form a low pressure portion (104) and a high pressure portion (102) in the upward and downward stroke of the piston portion (51). The intermediate position between them is formed in a wheel groove-shaped control part (105) which is continuous to one of the high and low pressure parts (104, 102) alternately during the reciprocating motion. The main body (1) has a valve chamber (400). And a rod-shaped valve body (40) which is vertically movable in the valve chamber (400), and has an oil inlet (P) and an outlet (T) that are open to the outside of the main body (1). ) Is provided, the high pressure is applied when the piston rod (5) reaches the bottom dead center through one of the following positions of the valve chamber (400) when the valve body (40) is at the stroke top and bottom dead center. (102) and a hydraulic pressure inlet (P), and Toki該 low pressure section of the piston rod (5) has come to the top dead center (102) and the high pressure section (1
The input and return oil passages (2, 3) for communicating the (04) with the oil outlet (T) at the same time are respectively formed, and the valve body (40) is divided into two step portions having different diameters from each other. A projecting edge (4) which is a low-pressure surface (411) and a high-pressure surface (412) whose both sides have different areas.
2) is projectingly provided, and the circumference of the vertical movement range of the projecting edge portion (42) of the valve chamber (400) is variable by the projecting edge portion (42) on the low pressure surface side low pressure valve chamber side (404). And the high pressure valve chamber (4
05), and the tip portion and the middle portion of the small-diameter stepped portion are further formed in the upper and lower switching portions (43, 41) by providing each recessed groove, and correspond to the valve chamber (400). The parts are respectively the first, second and third valve chamber parts (401, 402, 40
3), and when the valve body (40) moves up and down, the second valve chamber portion (402) is moved to the first by the upper or lower switching portion (43, 41).
The return oil passage (3) is configured to communicate with one of the third valve chamber portions (401, 403), and the return oil passage (3) includes a low pressure portion (1) of the hydraulic chamber (100).
04) and communicate with the first valve chamber part (401) of the valve chamber (400) by the return branch (23), and the control part (105) of the hydraulic chamber (100) and the Valve room (400)
A low pressure pipe (24) is provided as a communication with the low pressure valve chamber (404), which is one of the above, and the high pressure part (102) of the hydraulic chamber (100) and the valve chamber (400).
An input pipe (25) is provided as a communication with the second valve chamber (402) that is another one of the above, and the input oil passage (2) is the third valve of the valve chamber (400). It is connected to the chamber part (403) through the branch input path (21) and is communicated with the high pressure valve chamber part (405) of the valve chamber (400) through the branch oil path (22), and the hydraulic pressure inlet (P) is hydraulically connected. A structure of a crusher main body configured to connect a high-pressure discharge port of a pump and the oil outlet (T) to a drain tank of a hydraulic pump, respectively.