JP4738940B2 - Tree crusher - Google Patents
Tree crusher Download PDFInfo
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- JP4738940B2 JP4738940B2 JP2005239161A JP2005239161A JP4738940B2 JP 4738940 B2 JP4738940 B2 JP 4738940B2 JP 2005239161 A JP2005239161 A JP 2005239161A JP 2005239161 A JP2005239161 A JP 2005239161A JP 4738940 B2 JP4738940 B2 JP 4738940B2
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- 239000010720 hydraulic oil Substances 0.000 claims description 49
- 230000007423 decrease Effects 0.000 claims description 12
- 239000012530 fluid Substances 0.000 claims description 7
- 239000003921 oil Substances 0.000 description 37
- 230000007935 neutral effect Effects 0.000 description 10
- 239000000463 material Substances 0.000 description 7
- 230000002093 peripheral effect Effects 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
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Description
本発明は、伐採された樹木や剪定された木の枝などを破砕する樹木破砕機に関するものである。 The present invention relates to a tree crusher that crushes a felled tree or a pruned tree branch.
従来、伐採された樹木や剪定された木の枝などを破砕する樹木破砕機１０１は、図９、図１０に示すように、被破砕物の投入口１０２と、被破砕物を破砕する回転刃１０３を回転軸１０４の外周に取付けた破砕装置１０５と、駆動源１０７の回転軸１０６と破砕装置１０５の回転軸１０４とを連結し回転軸１０４に回転力を伝達する駆動ベルト１０８とを備えている。 Conventionally, as shown in FIGS. 9 and 10, a tree crusher 101 that crushes a felled tree, a pruned tree branch, and the like includes an inlet 102 for a material to be crushed and a rotary blade that crushes the material to be crushed. A crushing device 105 attached to the outer periphery of the rotary shaft 104; a drive belt 108 that connects the rotary shaft 106 of the drive source 107 and the rotary shaft 104 of the crushing device 105 to transmit the rotational force to the rotary shaft 104; Yes.
このような、樹木破砕機１０１は、図９に示すように、破砕装置１０５の回転軸１０４の一端側に駆動ベルト１０８を掛け渡し、他端側に回転刃１０３を取付ける。 As shown in FIG. 9, such a tree crusher 101 has a drive belt 108 stretched over one end side of the rotating shaft 104 of the crushing device 105 and a rotary blade 103 attached to the other end side.
したがって、樹木破砕機１０１を運転すると、破砕装置１０５の回転軸１０４の一方の端部には、駆動ベルト１０８の張力によって力Ｆ１が働く。また、破砕装置１０５の回転軸１０４の他方の端部には、破砕時に受ける力Ｆ２が働く。この破砕時の力は、被破砕物を、投入口から回転刃１０３の回転軌跡内へ押し込んで鉋のように被破砕物を削ることにより発生する。 Therefore, when the tree crusher 101 is operated, a force F <b> 1 is applied to one end portion of the rotating shaft 104 of the crushing device 105 due to the tension of the drive belt 108. Further, a force F <b> 2 received during crushing acts on the other end of the rotating shaft 104 of the crushing device 105. The force at the time of crushing is generated by pushing the object to be crushed into the rotation trajectory of the rotary blade 103 from the inlet and cutting the object to be crushed like a ridge.
この状態の力の関係を、図９の平面図に示す、回転軸１０４の両端に掛かる力Ｆ１、Ｆ２の方向が、回転軸１０４をこじる方向となるため、回転軸１０４の軸受に無理な力が作用する可能性がある。 The relationship between the forces in this state is shown in the plan view of FIG. 9, and the directions of the forces F1 and F2 applied to both ends of the rotating shaft 104 are directions that squeeze the rotating shaft 104. May work.
本発明に係る樹木破砕装機は、被破砕物を破砕する刃を回転軸の外周に取付けた破砕装置と、破砕装置の回転軸の一端側に掛け渡され回転軸に駆動源からの回転力を伝達する駆動ベルトと、回転軸の駆動ベルトを掛け渡した側に配置され、破砕装置の刃の回転軌跡内に連通した被破砕物の投入口と、前記投入口と破砕装置との間に配設され、被破砕物を破砕装置に送る送込装置と、この送込装置を駆動する油圧モータと、駆動源に連結されて作動油を油圧モータへ供給する油圧ポンプと、作動油の供給量が所定値以下になったとき油圧モータへの作動油の供給を停止させる方向切換弁とを備え、前記方向切換弁は、油圧ポンプから油圧モータへの作動油の供給量が減少し所定値以下に低下したとき油圧モータに対する作動油の供給を停止する方向に切換えて油圧ポンプに連動する破砕装置の負荷を軽減し、これによって油圧ポンプの回転数が所定回転数まで回復したときに油圧モータに作動油を供給する方向に切換えるようにした樹木破砕機。 The tree crushing machine according to the present invention includes a crushing device in which a blade for crushing an object to be crushed is attached to the outer periphery of a rotary shaft, and a rotational force from a drive source spanned on one end side of the rotary shaft of the crushing device. Is disposed on the side where the drive belt of the rotating shaft is stretched, and is connected to the crushing device blade rotation trajectory, and is connected between the crushing device blade and the crushing device. A feeding device that is disposed and sends the object to be crushed to the crushing device; a hydraulic motor that drives the feeding device; a hydraulic pump that is connected to a driving source and supplies hydraulic oil to the hydraulic motor; A directional switching valve that stops the supply of hydraulic oil to the hydraulic motor when the amount becomes a predetermined value or less, and the directional switching valve decreases the supply amount of hydraulic oil from the hydraulic pump to the hydraulic motor to a predetermined value. Stop supplying hydraulic oil to hydraulic motor when it drops below Tree crusher that reduces the load of the crushing device linked to the hydraulic pump by switching to the direction and supplies the hydraulic oil to the hydraulic motor when the rotation speed of the hydraulic pump recovers to the predetermined rotation speed. .
本発明によれば、被破砕物を破砕する刃を回転軸の外周に取付けた破砕装置と、破砕装置の回転軸の一端側に掛け渡され回転軸に駆動源からの回転力を伝達する駆動ベルトと、回転軸の駆動ベルトを掛け渡した側に配置され、破砕装置の刃の回転軌跡内に連通した被破砕物の投入口とを備えたもので、駆動ベルトにより破砕装置の回転軸に張力として加わる力と、被粉砕物の粉砕時に破砕装置の回転軸に加わる力を回転軸の同一端側で受けるので、回転軸をこじるような力が発生しない。 According to the present invention, a crushing device in which a blade for crushing an object to be crushed is attached to the outer periphery of a rotating shaft, and a drive that is passed over one end of the rotating shaft of the crushing device and transmits a rotational force from a driving source to the rotating shaft. It is arranged on the side where the drive belt of the rotating shaft is spanned, and has an inlet for the object to be crushed communicated within the rotation trajectory of the blade of the crushing device. Since the force applied as the tension and the force applied to the rotating shaft of the crushing apparatus when the material to be crushed is crushed on the same end side of the rotating shaft, no force that squeezes the rotating shaft is generated.
また、前記投入口と破砕装置との間に配設され被破砕物を破砕装置に送る送込装置と、この送込装置を駆動する油圧モータと、駆動源に連結されて作動油を油圧モータへ供給する油圧ポンプと、作動油の供給量が所定値以下になったとき油圧モータを停止させる方向切換弁とを備えることにより、油圧ポンプによる作動油の供給量で油圧モータの切換を行えるので、高価な電気センサー、電気制御回路や電磁弁を必要とせず、安価な樹木破砕機を得ることができる。また、例えば、方向切換弁を、油圧ポンプから油圧モータへの作動油の供給量が減少し所定値以下に低下したとき油圧モータに対する作動油の供給を停止する方向に切換えて油圧ポンプに連動する破砕装置の負荷を軽減し、これによって油圧ポンプの回転数が所定回転数まで回復したときに油圧モータに作動油を供給する方向に切換えることにより、油圧モータの停止、すなわち送込装置の停止により破砕物の追加送り込みがない状態で破砕装置に滞留した被破砕物を速やかに破砕することができ、しかも破砕が進行して油圧ポンプの回転数が回復すると自動的に送込装置が作動して破砕作業を継続することができる。 A feeding device that is disposed between the charging port and the crushing device and sends a material to be crushed to the crushing device; a hydraulic motor that drives the feeding device; The hydraulic pump can be switched by the amount of hydraulic oil supplied by the hydraulic pump by providing a hydraulic pump that supplies the hydraulic oil and a direction switching valve that stops the hydraulic motor when the hydraulic oil supply amount falls below a predetermined value. It is possible to obtain an inexpensive tree crusher without requiring an expensive electric sensor, an electric control circuit or a solenoid valve. In addition, for example, when the supply amount of hydraulic oil from the hydraulic pump to the hydraulic motor decreases and falls below a predetermined value, the direction switching valve is switched to a direction in which the supply of hydraulic oil to the hydraulic motor is stopped and linked to the hydraulic pump. reduce the load of the crushing device, whereby by the hydraulic pump speed switch in the direction for supplying hydraulic fluid to the hydraulic motor when it recovers to a predetermined rotational speed, stopping the hydraulic motor, that is, by stopping the infeed device The material to be crushed in the crushing device can be quickly crushed without additional feeding of crushed material, and when the crushing progresses and the rotational speed of the hydraulic pump recovers, the feeding device automatically operates. The crushing operation can be continued.
以下、本発明の一実施形態に係る樹木破砕機を図面に基づいて説明する。 Hereinafter, a tree crusher according to an embodiment of the present invention will be described with reference to the drawings.
樹木破砕機１は、図１に示すように、フレーム２の上に、破砕装置４と、駆動源５とを備えている。 As shown in FIG. 1, the tree crusher 1 includes a crushing device 4 and a drive source 5 on a frame 2.
フレーム２は、この実施形態では、図１に示すように、前進方向に延びており、下部に無端状の走行輪６を前進方向に対して左右に備えているとともに、前進方向の最後部に樹木破砕機１を操縦するためのハンドル７を備えている。 In this embodiment, as shown in FIG. 1, the frame 2 extends in the forward direction. The frame 2 includes endless traveling wheels 6 on the left and right of the forward direction, and at the rearmost part in the forward direction. A handle 7 for operating the tree crusher 1 is provided.
破砕装置４は、この実施形態では、図２に示すように、破砕ケース８内に軸受１０で水平方向に軸支された回転軸９を取付けている。回転軸９の外周には刃１１が取付けられている。この実施形態では、図１に示すように、回転軸９に、回転板１２を取付け、この回転板１２の一側面に被破砕物（例えば、樹木）を破砕する刃１１を取付けている。破砕ケース８の一側面側で、回転軸９からやや離れた位置に被破砕物の投入口３を連通させて取付けており、被破砕物を回転板１２にほぼ直角に押しつけて刃１１でチップ状に破砕するようにしている。この破砕されたチップは、回転板１２の回転時に発生する風圧でダクト１３から排出している。この破砕装置４は、回転軸９の向きを、図２に示すように、樹木破砕機１の前進方向と直角にして、回転板１２を前進方向に沿った面内で回転するようにフレーム２上に取付けている。この実施形態では、図３に示すように、前進方向に向かってフレーム２の右側に破砕装置４を前後方向に配置している。このことにより、図３に示すように、投入口３は、前進方向に向かって、フレーム２の左側の後部に位置している。 In this embodiment, as shown in FIG. 2, the crushing device 4 has a rotating shaft 9 pivotally supported in a horizontal direction by a bearing 10 in a crushing case 8. A blade 11 is attached to the outer periphery of the rotating shaft 9. In this embodiment, as shown in FIG. 1, a rotating plate 12 is attached to a rotating shaft 9, and a blade 11 for crushing an object to be crushed (for example, a tree) is attached to one side surface of the rotating plate 12. On one side of the crushing case 8, the crushing object inlet 3 is connected to a position slightly away from the rotary shaft 9, and the crushing object is pressed against the rotating plate 12 at a substantially right angle and inserted with the blade 11. To be crushed into a shape. The crushed chips are discharged from the duct 13 by the wind pressure generated when the rotating plate 12 rotates. As shown in FIG. 2, the crushing device 4 has a frame 2 so that the rotating plate 12 is rotated in a plane along the forward direction with the direction of the rotary shaft 9 being perpendicular to the forward direction of the tree crusher 1. Installed on top. In this embodiment, as shown in FIG. 3, the crushing device 4 is arranged in the front-rear direction on the right side of the frame 2 in the forward direction. As a result, as shown in FIG. 3, the insertion port 3 is located at the rear part on the left side of the frame 2 in the forward direction.
駆動源５は、この実施形態では、エンジンで形成され、走行輪６や破砕装置４等をエンジンで回転駆動する。駆動源５は前進方向向かって回転軸１６を左右方向に配置している（図２参照）。この駆動源５の回転軸１６と、破砕装置４の回転軸９との間に、駆動ベルト１７が掛け渡されている。駆動ベルト１７は、この実施形態では、図１に示すように、回転軸９，１６にプーリ１８，１９をそれぞれ取付け、プーリ１８，１９間に掛け渡して取付けられ、駆動源５の回転力を破砕装置４の回転軸９に伝達する。 In this embodiment, the drive source 5 is formed of an engine, and rotationally drives the traveling wheels 6, the crushing device 4, and the like with the engine. The drive source 5 has a rotating shaft 16 arranged in the left-right direction in the forward direction (see FIG. 2). A drive belt 17 is stretched between the rotation shaft 16 of the drive source 5 and the rotation shaft 9 of the crushing device 4. In this embodiment, as shown in FIG. 1, the drive belt 17 has pulleys 18 and 19 attached to the rotary shafts 9 and 16, respectively, and is installed across the pulleys 18 and 19. This is transmitted to the rotating shaft 9 of the crushing device 4.
また、投入口３と破砕装置４との間には、投入された被破砕物を破砕装置４に送る送込装置２１を設けている。この実施形態では、送込装置２１は、被粉砕物を破砕装置４の回転板１２に押しつける送りローラ２２と、送りローラ２２を回転させる油圧モータ２３とから構成している。油圧モータ２３は、駆動源５に連結された油圧ポンプ２４から送出される作動油を流して回転を制御している。油圧ポンプ２４は、吸込側をタンク２５に接続し、吐出側を油圧モータ２３の作動油供給管路２６に接続している。 Further, a feeding device 21 for sending the crushed material to the crushing device 4 is provided between the charging port 3 and the crushing device 4. In this embodiment, the feeding device 21 includes a feed roller 22 that presses the object to be crushed against the rotating plate 12 of the crushing device 4 and a hydraulic motor 23 that rotates the feed roller 22. The hydraulic motor 23 controls the rotation by flowing hydraulic oil delivered from a hydraulic pump 24 connected to the drive source 5. The hydraulic pump 24 has a suction side connected to the tank 25 and a discharge side connected to a hydraulic oil supply pipe 26 of the hydraulic motor 23.
油圧モータ２３の作動油供給管路２６には、図４に示すように、手動切換弁２７と、方向切換弁２８とを設けている。手動切換弁２７は、３位置切換弁であり、そのレバーを操作することにより、油圧ポンプ２４からの作動油を油圧モータ２３の正転側、または逆転側に供給するか、あるいは、戻り管路２９側へアンロードする。すなわち、手動切換弁２７により、油圧モータ２３の正転、逆転、停止を制御できるようになっている。 As shown in FIG. 4, a manual switching valve 27 and a direction switching valve 28 are provided in the hydraulic oil supply pipe 26 of the hydraulic motor 23. The manual switching valve 27 is a three-position switching valve, and by operating its lever, the hydraulic oil from the hydraulic pump 24 is supplied to the forward rotation side or the reverse rotation side of the hydraulic motor 23, or the return line Unload to 29 side. That is, the manual switching valve 27 can control forward rotation, reverse rotation, and stop of the hydraulic motor 23.
方向切換弁２８は、油圧ポンプ２４による作動油の流量が少ないときに中立状態、作動油の流量が多いときに作動状態とする２位置切換弁である。この方向切換弁２８は、図５に示すように、作動油の流入側となる入力ポート２８Ｐと、作動油の流出側となる第１出力ポート２８Ａ、および第２出力ポート２８Ｔと、第１分岐通路孔３０と、第２分岐通路３１と、圧縮ばね３２とを備えている。 The direction switching valve 28 is a two-position switching valve that is in a neutral state when the hydraulic oil flow rate by the hydraulic pump 24 is low and is in an active state when the hydraulic oil flow rate is high. As shown in FIG. 5, the direction switching valve 28 includes an input port 28P on the hydraulic oil inflow side, a first output port 28A and a second output port 28T on the hydraulic oil outflow side, and a first branch. A passage hole 30, a second branch passage 31, and a compression spring 32 are provided.
方向切換弁２８は、この実施形態では、図６、図７に示すように、入力ポート２８Ｐ、第１出力ポート２８Ａ、第２出力ポート２８Ｔがバルブ３３に形成され、バルブ３３内の一端側に油溜室３４、他端側にばね３２を配設して、スプール３５をバルブ３３内に往復動可能に配設している。具体的には、この実施形態では、スプール３５を往復動可能に内嵌するバルブ３３の内周壁に、図６、図７の左から右へ入力ポート２８Ｐと連通する第１油室３６、第１出力ポート２８Ａと連通する第２油室３７、第２出力ポート２８Ｔと連通する第３油室３８を設けている。バルブ３３の両端はプラグ３９，４０をねじ込んで取付けている。前記油溜室３４は、入力ポート２８Ｐから供給される作動油が溜まる室で、前記プラグ３９とスプール３５の端部間並びにスプール３５の端部側に形成された室３４ａ、３４ｂ、３４ｃ及びバルブ３３の空間３４ｄで形成されている。スプール３５は、ばね３２により油溜室３４側に附勢されている。 In this embodiment, as shown in FIGS. 6 and 7, the direction switching valve 28 includes an input port 28 </ b> P, a first output port 28 </ b> A, and a second output port 28 </ b> T formed in the valve 33. A spring 32 is disposed on the oil reservoir chamber 34 and the other end side, and a spool 35 is disposed in the valve 33 so as to reciprocate. Specifically, in this embodiment, the first oil chamber 36, the first oil chamber 36, which communicates with the input port 28P from the left to the right in FIGS. A second oil chamber 37 communicating with the first output port 28A and a third oil chamber 38 communicating with the second output port 28T are provided. Plugs 39 and 40 are screwed to both ends of the valve 33. The oil reservoir chamber 34 is a chamber in which hydraulic oil supplied from the input port 28P is stored, and chambers 34a, 34b, 34c and valves formed between the plug 39 and the end portion of the spool 35 and on the end portion side of the spool 35. 33 spaces 34d. The spool 35 is urged toward the oil reservoir chamber 34 by the spring 32.
スプール３５内には、連通路４１が形成されており、一端４１ａが少なくとも二股に分岐してそのうちの第１分岐通路３０がスプール３５の端面において前記油溜室３４に臨んで常時開口している。また、連通路４１の第２分岐通路３１がスプール３５の周面に開口してスプール３５が前記油溜室３４側に往動した状態で油溜室３４に臨んで開口すると共にスプール３５がばね３２に抗して復動した状態でバルブ３３の内周壁によって閉塞されるようになっている。また、連通路４１の他端４１ｂにスプール３５の周面の所定位置に開口４２，４３を形成している。開口４２は第２油室３７と連通し、開口４３は第３油室３８と連通する。開口４３は、前記ばね３２の挿入用の開口にもなっていて、ばね３２の一端が連通路４１内に挿入されている。 A communication passage 41 is formed in the spool 35, and one end 41 a is branched into at least two branches, and the first branch passage 30 of the one end 41 a is always open facing the oil reservoir chamber 34 at the end face of the spool 35. . Further, the second branch passage 31 of the communication passage 41 opens to the circumferential surface of the spool 35 and the spool 35 opens toward the oil reservoir chamber 34 in a state of moving forward to the oil reservoir chamber 34 side, and the spool 35 is spring-loaded. The valve 33 is closed by the inner peripheral wall of the valve 33 in a state of moving backward against the valve 32. Further, openings 42 and 43 are formed at predetermined positions on the peripheral surface of the spool 35 at the other end 41 b of the communication path 41. The opening 42 communicates with the second oil chamber 37, and the opening 43 communicates with the third oil chamber 38. The opening 43 is also an opening for inserting the spring 32, and one end of the spring 32 is inserted into the communication path 41.
方向切換弁２８の中立状態とは、スプール３５がばね３２の力により油溜室３４側へ移動している状態で、プラグ３９とスプール３５の端部が当接している。この時、開口４２がバルブ３３の内周壁で閉じられており、開口４３と第三油室３８が連通する。また、方向切換弁２８の作動状態とは、図７に示すように、作動油の供給量が増大して、第１分岐通路３０、第２分岐通路３１を通過する流量による圧力差が増大し、スプール３５がばね３２の力に抗して反油溜室３４側へ移動している状態で、プラグ４０とスプール３５の開口４３の端部が当接して第三油室３８との連通を閉じ、開口４２と第２油室３７が連通する。したがって、スプール３５が中立状態に位置する時には、油溜室３４に、第１分岐通路３０と第２分岐通路３１とで連通し、スプール３５が作動状態に位置する時には、第２分岐通３１をバルブ３３の内周壁で閉じて、第１分岐通路３０だけを連通する。 The neutral state of the direction switching valve 28 is a state in which the spool 35 is moved to the oil reservoir chamber 34 side by the force of the spring 32, and the plug 39 and the end of the spool 35 are in contact with each other. At this time, the opening 42 is closed by the inner peripheral wall of the valve 33, and the opening 43 and the third oil chamber 38 communicate with each other. Further, as shown in FIG. 7, the operating state of the direction switching valve 28 means that the amount of hydraulic oil supplied increases, and the pressure difference due to the flow rate passing through the first branch passage 30 and the second branch passage 31 increases. In the state where the spool 35 moves toward the anti-oil reservoir chamber 34 against the force of the spring 32, the plug 40 and the end of the opening 43 of the spool 35 come into contact with each other to establish communication between the third oil chamber 38. The opening 42 and the second oil chamber 37 communicate with each other. Therefore, when the spool 35 is positioned in the neutral state, the oil reservoir chamber 34 communicates with the first branch passage 30 and the second branch passage 31, and when the spool 35 is positioned in the operating state, the second branch passage 31 is connected. It is closed by the inner peripheral wall of the valve 33 and communicates only the first branch passage 30.
このような樹木伐採装置１は、図４に示すように、駆動源５と破砕装置４、油圧ポンプ２４は連動しており、駆動源５の回転軸１６の回転が速ければ、破砕装置４の回転軸９の回転速度、油圧ポンプ２４の回転速度も速くなる。また、破砕装置４の回転軸９の回転速度が被破砕物を破砕する抵抗等で遅くなれば、駆動源５の回転軸１６の回転も遅くなり、油圧ポンプ２４の回転も遅くなる。すなわち、駆動源５、破砕装置４、油圧ポンプ２４は、連動して回転数が早くなったり、遅くなったりする。 In such a tree cutting device 1, as shown in FIG. 4, the drive source 5, the crushing device 4, and the hydraulic pump 24 are interlocked, and if the rotation of the rotary shaft 16 of the drive source 5 is fast, the crushing device 4 The rotational speed of the rotary shaft 9 and the rotational speed of the hydraulic pump 24 are also increased. Moreover, if the rotational speed of the rotating shaft 9 of the crushing device 4 is slowed down due to resistance to crush the object to be crushed, the rotation of the rotating shaft 16 of the drive source 5 is slowed down, and the rotation of the hydraulic pump 24 is also slowed down. That is, the drive source 5, the crushing device 4, and the hydraulic pump 24 increase or decrease in speed in conjunction with each other.
被破砕物を投入していない状態では、駆動源５の回転軸１６を一定回転数で運転すると、動力伝達手段１７により破砕装置４の回転軸９は回転数Ｒ１以上で回転して刃１１を回転する。また、同時に油圧ポンプ２４も回転させられ、油圧ポンプ２４から作動油を流量Ｑ１以上で吐出する。この回転数Ｒ１により作動油の流量がＱ１以上となると、方向切換弁２８の油溜室３３にＱ１の流量が流れて、第１分岐通路３０、第２分岐通路３１を通過する流量による圧力差が増大し、ばね３２の力に抗してスプール３５を復動させて方向切換弁２８を作動状態する。この結果、油圧モータ２３の作動油の流量Ｑ１を油圧モータ２３に供給して油圧モータ２３を回転させ、送込装置２１を作動させる。 When the object to be crushed is not charged, when the rotary shaft 16 of the drive source 5 is operated at a constant rotational speed, the rotational shaft 9 of the crushing device 4 is rotated at the rotational speed R1 or more by the power transmission means 17 and the blade 11 is moved. Rotate. At the same time, the hydraulic pump 24 is also rotated, and hydraulic oil is discharged from the hydraulic pump 24 at a flow rate Q1 or more. When the flow rate of hydraulic oil becomes equal to or greater than Q1 due to this rotational speed R1, the flow rate of Q1 flows into the oil reservoir chamber 33 of the direction switching valve 28, and the pressure difference due to the flow rate passing through the first branch passage 30 and the second branch passage 31 Increases, and the spool 35 is moved back against the force of the spring 32 to activate the direction switching valve 28. As a result, the hydraulic oil flow rate Q1 of the hydraulic motor 23 is supplied to the hydraulic motor 23 to rotate the hydraulic motor 23 and operate the feeding device 21.
そして、この状態で伐採された樹木や剪定された枝などの被破砕物を投入口３に投入すると、被破砕物が送込装置２１によって破砕装置４の回転板１２に押しつけられ刃１１によりチップ状に破砕され、ダクト１３から排出される。 Then, when objects to be crushed such as trees or pruned branches that have been cut in this state are put into the inlet 3, the objects to be crushed are pressed against the rotating plate 12 of the crushing device 4 by the feeding device 21 and chipped by the blade 11. And is discharged from the duct 13.
この時、破砕作業時に破砕装置４の負荷が増大すると破砕装置４と同期して駆動源５の回転が落ち、回転軸１６の回転がＲ２に下がり、油圧ポンプ２４から吐出される作動油の流量がＱ２以下にまで下がる。作業油の流量がＱ２以下となると、第１分岐通路３０を通過する流量による圧力差が減少し、方向切換弁２８のスプール３５を押圧する力が弱くなり、ばね３１の力でスプール３５が往動し中立状態となる。方向切換弁２８が中立状態になると、作動油は方向切換弁２８の第２出力ポート２８Ｔから手動切換弁２７に流れて、タンク２５へと流れる。この結果、油圧モータ２３への作動油の供給が停止して、送込装置２１が一時的に停止する。 At this time, if the load on the crushing device 4 increases during crushing work, the rotation of the drive source 5 falls in synchronization with the crushing device 4, the rotation of the rotary shaft 16 falls to R2, and the flow rate of hydraulic oil discharged from the hydraulic pump 24 Decreases to below Q2. When the flow rate of the working oil is equal to or less than Q2, the pressure difference due to the flow rate passing through the first branch passage 30 decreases, the force that presses the spool 35 of the direction switching valve 28 becomes weak, and the spool 35 moves forward by the force of the spring 31. It moves and becomes neutral. When the direction switching valve 28 is in a neutral state, the hydraulic fluid flows from the second output port 28T of the direction switching valve 28 to the manual switching valve 27 and then flows to the tank 25. As a result, the supply of hydraulic oil to the hydraulic motor 23 is stopped, and the feeding device 21 is temporarily stopped.
送込装置２１が停止することにより、破砕装置４の回転軸９の負荷が低下するので、これにより、駆動源５の回転軸１６の回転が上昇に転じて回転数Ｒ１以上に回復すると、油圧ポンプ２４から流量Ｑ１以上の作動油を方向切換弁２８の入力ポート２８Ｐに吐出する。方向切換弁２８の入力ポート２８Ｐと連通している油溜室３４に作動油の流量Ｑ１以上が流入すると、当初は油溜室３４から第１分岐通路３０，第２分岐通路３１，連通路４１，開口４３、第３油室３８、第２出力ポート２８Ｔへ作動油が流れるが、油溜室３４側の第１分岐通路３０、第２分岐通路３１を通過する流量による圧力差による力がばね３１の力よりも大きくなると、スプール３５をばね３１の力に抗して復動させ方向切換弁２８を再び作動状態にする。 Since the load on the rotating shaft 9 of the crushing device 4 decreases due to the stop of the feeding device 21, when the rotation of the rotating shaft 16 of the drive source 5 starts to rise and recovers to the rotational speed R1 or higher, the hydraulic pressure The hydraulic fluid with a flow rate of Q1 or more is discharged from the pump 24 to the input port 28P of the direction switching valve 28. When the hydraulic oil flow rate Q1 or more flows into the oil reservoir chamber 34 communicating with the input port 28P of the direction switching valve 28, the first branch passage 30, the second branch passage 31, and the communication passage 41 are initially fed from the oil reservoir chamber 34. , The opening 43, the third oil chamber 38, and the second output port 28T, the hydraulic oil flows, but the force due to the pressure difference due to the flow rate passing through the first branch passage 30 and the second branch passage 31 on the oil reservoir chamber 34 side is spring. When the force is greater than 31, the spool 35 is moved back against the force of the spring 31 and the direction switching valve 28 is again activated.
油圧ポンプ２４から吐出される作動油の流量Ｑは、駆動源５の回転軸１６の回転数の増減により、増減する。このため、方向切換弁２８の作動は、図８に示すようになる。 The flow rate Q of the hydraulic oil discharged from the hydraulic pump 24 increases and decreases as the rotational speed of the rotating shaft 16 of the drive source 5 increases and decreases. Therefore, the operation of the direction switching valve 28 is as shown in FIG.
ａ;作動油の流量が増加する場合（回転軸１６の回転数が上がる場合） a: When the flow rate of hydraulic oil increases (when the rotational speed of the rotating shaft 16 increases)
ａ−１；作動油の流量がＱ１未満の場合
作動油は、入力ポート２８Ｐ→第１油室３６→油溜室３４→第１分岐通路３０，第２分岐通路３１→連通路４１→開口４３→第３油室３８→第２出力ポート２８Ｔへと流れて、タンク２５へ作動油を戻している。この時、第１分岐通路３０，第２分岐通路３１の圧力損失をＰ１、スプール３５の断面積をＡとすると、Ｐ１×Ａ＜ばね力Ｆｂ１（Ｆｂ１は、方向切換弁２８を中立状態に保持するばね３２の力）の関係にある。
a-1: When the flow rate of hydraulic oil is less than Q1, the hydraulic oil is input port 28P → first oil chamber 36 → oil reservoir 34 → first branch passage 30, second branch passage 31 → communication passage 41 → opening 43 → The third oil chamber 38 → flows to the second output port 28T and returns the hydraulic oil to the tank 25. At this time, if the pressure loss of the first branch passage 30 and the second branch passage 31 is P1, and the sectional area of the spool 35 is A, then P1 × A <spring force Fb1 (Fb1 holds the direction switching valve 28 in a neutral state. The force of the spring 32).
ａ−２；作動油の流量がＱ１以上の場合
作動油は、入力ポート２８Ｐ→第１油室３６→油溜室３４→第１分岐通路３０→連通路４１→開口４２→第２油室３７→第１出力ポート２８Ａと流れて、手動切換弁２７を介して油圧モータ２３→タンク２５へと流れる。この時、第１分岐通路３０の圧力損失をＰ２、スプール３５の断面積をＡとすると、Ｐ２×Ａ＞ばね力Ｆｂ２（Ｆｂ２は、方向切換弁２８を作動状態から中立状態に戻すばね３２の力）の関係にある。
ｂ;作動油の流量が減少する場合（回転軸１６の回転数が下がる場合）
a-2: When the flow rate of hydraulic oil is Q1 or more The hydraulic oil is input port 28P → first oil chamber 36 → oil reservoir 34 → first branch passage 30 → communication passage 41 → opening 42 → second oil chamber 37 → Flows through the first output port 28 </ b> A and flows through the manual switching valve 27 to the hydraulic motor 23 → the tank 25. At this time, if the pressure loss of the first branch passage 30 is P2 and the cross-sectional area of the spool 35 is A, P2 × A> spring force Fb2 (Fb2 is the value of the spring 32 that returns the direction switching valve 28 from the operating state to the neutral state. Power).
b: When the flow rate of hydraulic oil decreases (when the rotational speed of the rotating shaft 16 decreases)
ｂ−１；作動油の流量がＱ２以上の場合
作動油は、入力ポート２８Ｐ→第１油室３６→油溜室３４→第１分岐通路３０→連通路４１→開口４２→第２油室３７→第１出力ポート２８Ａと流れて、手動切換弁２７を介して油圧モータ２３→タンク２５へと流れる。この時、第１分岐通路３０の圧力損失をＰ３、スプール３５の断面積をＡとすると、Ｐ３×Ａ＞ばね力Ｆｂ２（Ｆｂ２は、方向切換弁２８を作動状態から中立状態に戻すばね３２の力）の関係にある。
b-1: When the flow rate of the hydraulic oil is Q2 or more, the hydraulic oil is supplied from the input port 28P → the first oil chamber 36 → the oil reservoir 34 → the first branch passage 30 → the communication passage 41 → the opening 42 → the second oil chamber 37. → Flows through the first output port 28 </ b> A and flows through the manual switching valve 27 to the hydraulic motor 23 → the tank 25. At this time, assuming that the pressure loss of the first branch passage 30 is P3 and the cross-sectional area of the spool 35 is A, P3 × A> spring force Fb2 (Fb2 is the value of the spring 32 that returns the direction switching valve 28 from the operating state to the neutral state. Power).
ｂ−１；作動油の流量がＱ２未満の場合
作動油は、入力ポート２８Ｐ→第１油室３６→油溜室３４→第１分岐通路３０，第２分岐通路３１→連通路４１→開口４３→第３油室３８→第２出力ポート２８Ｔへと流れて、タンク２５へ作動油を戻している。この時、第１分岐通路３０，第２分岐通路３１の圧力損失をＰ４、スプール３５の断面積をＡとすると、Ｐ４×Ａ＜ばね力Ｆｂ１（Ｆｂ１は、方向切換弁２８を中立状態に保持するばね３２の力）の関係にある。
b-1: When the flow rate of hydraulic fluid is less than Q2, the hydraulic fluid is input port 28P → first oil chamber 36 → oil reservoir 34 → first branch passage 30, second branch passage 31 → communication passage 41 → opening 43 → The third oil chamber 38 → flows to the second output port 28T and returns the hydraulic oil to the tank 25. At this time, assuming that the pressure loss of the first branch passage 30 and the second branch passage 31 is P4 and the sectional area of the spool 35 is A, P4 × A <spring force Fb1 (Fb1 holds the direction switching valve 28 in a neutral state. The force of the spring 32).
また、方向切換弁２８から自動的に作動油を供給している状態の時には、手動切換弁２７を操作することにより、油圧モータ２３の正転、逆転、停止の操作をすることができる。 Further, when the hydraulic oil is automatically supplied from the direction switching valve 28, the manual switching valve 27 can be operated to perform forward rotation, reverse rotation, and stop operation of the hydraulic motor 23.
以上説明したように、樹木破砕機１は、破砕装置４の回転軸９に駆動ベルト１７を掛け渡した側に、投入口３を配置しているので、破砕装置４の回転軸９に作用する力は、回転軸９の一端側において駆動ベルト１７からの張力として発生する力Ｆ１（図１，図２で示すＦ１の方向）と、回転軸９の同じ一端側において破砕装置４の刃１１が被破砕物との衝突により破砕時に受ける力の反力Ｆ２（図１，図２で示すＦ２の方向）となる。このように図１，図２に示すように、回転軸９の同一端部側で力Ｆ１，Ｆ２を受けるので、力Ｆ１，Ｆ２が互いに一部相殺される結果となり、回転軸９をこじるような力が発生せず、軸受に過大な力が掛かることがなく、騒音や振動を小さくすることができる。 As described above, the tree crusher 1 has the input port 3 arranged on the side where the drive belt 17 is spanned over the rotation shaft 9 of the crushing device 4, and thus acts on the rotation shaft 9 of the crushing device 4. The force F1 generated as tension from the drive belt 17 on one end side of the rotating shaft 9 (direction F1 shown in FIGS. 1 and 2) and the blade 11 of the crushing device 4 on the same one end side of the rotating shaft 9 It becomes a reaction force F2 (direction of F2 shown in FIGS. 1 and 2) of the force received during crushing due to the collision with the object to be crushed. As shown in FIGS. 1 and 2, since the forces F1 and F2 are received on the same end side of the rotating shaft 9, the forces F1 and F2 are partially offset from each other. Thus, no excessive force is generated, no excessive force is applied to the bearing, and noise and vibration can be reduced.
また、破砕装置４の負荷が増大し、油圧ポンプ２４からの作動油の流量がＱ２以下に減少したときは、油圧モータ２３への作動油の供給を停止し、破砕装置４の負荷を軽減する。破砕装置４の負荷が軽減されると、駆動源５の回転軸１６の負荷も軽減されて、回転軸１６の回転数が上昇し、この回転数の上昇が所定値Ｒ１以上となると、方向切換弁２８の油溜室３３の作動油の流量がＱ１以上となってばね３２の力に抗してスプール３５を切換えて、油圧モータ２３へ作動油を流量Ｑ１以上で供給して、油圧モータ２３を回転させる。したがって、破砕装置４の破砕性能低下を防止でき安定した破砕ができる。また、破砕時に回転軸９をこじる力が働かないので、こじりによる回転軸９の回転数変動を少なくして、方向切換弁２８の切換え回数を少なくすることができる。 Further, when the load of the crushing device 4 increases and the flow rate of the hydraulic oil from the hydraulic pump 24 decreases to Q2 or less, the supply of the hydraulic oil to the hydraulic motor 23 is stopped, and the load on the crushing device 4 is reduced. . When the load on the crushing device 4 is reduced, the load on the rotary shaft 16 of the drive source 5 is also reduced, and the rotational speed of the rotary shaft 16 increases. When the increase in the rotational speed exceeds a predetermined value R1, the direction is switched. The flow rate of the hydraulic oil in the oil reservoir chamber 33 of the valve 28 becomes Q1 or higher, the spool 35 is switched against the force of the spring 32, and the hydraulic oil is supplied to the hydraulic motor 23 at a flow rate Q1 or higher. Rotate. Therefore, the crushing performance of the crushing device 4 can be prevented from being lowered and stable crushing can be performed. In addition, since the force that squeezes the rotary shaft 9 does not work during crushing, fluctuations in the rotational speed of the rotary shaft 9 due to squeezing can be reduced, and the number of switching of the direction switching valve 28 can be reduced.
以上、本発明の一実施形態に係る樹木破砕機を説明したが、本発明に係る樹木破砕機は、上記した実施形態に限定されるものではなく、本発明の要旨を逸脱しない範囲内において種々変更を加えることができる。 As mentioned above, although the tree crusher which concerns on one Embodiment of this invention was demonstrated, the tree crusher which concerns on this invention is not limited to above-described embodiment, In the range which does not deviate from the summary of this invention, it is various. You can make changes.
例えば、実施形態では、破砕装置４の回転軸９を駆動源５の回転軸１６で回転させたが、油圧ポンプ２４の作動油で回転する油圧モータの回転軸と破砕装置４の回転軸９を動力伝達手段で連結することもできる。また、送込装置２１を送りローラと油圧モータで構成したが、コンベアと油圧モータで構成してもよい。また、方向切換弁２８においては、第１分岐通路だけとして、ばね力を2段階に変化させても、分岐通路を細長い通路で断面積を変化させてもよい。 For example, in the embodiment, the rotating shaft 9 of the crushing device 4 is rotated by the rotating shaft 16 of the drive source 5, but the rotating shaft of the hydraulic motor that rotates with the hydraulic oil of the hydraulic pump 24 and the rotating shaft 9 of the crushing device 4 are used. It can also be connected by power transmission means. In addition, although the feeding device 21 is configured with a feeding roller and a hydraulic motor, it may be configured with a conveyor and a hydraulic motor. Further, in the direction switching valve 28, the spring force may be changed in two stages only for the first branch passage, or the sectional area of the branch passage may be changed by an elongated passage.
１ 樹木破砕機
２ フレーム
３ 投入口
４ 破砕装置
５ 駆動源
９ 回転軸
１１ 刃
１２ 回転板
１３ ダクト
１６ 回転軸
１７ 駆動ベルト
１８，１９ プーリ
２１ 送込装置
２３ 油圧ポンプ
２４ 油圧ポンプ
２６ 作動油供給管路
２８ 方向切換弁
DESCRIPTION OF SYMBOLS 1 Tree crusher 2 Frame 3 Slot 4 Crushing device 5 Driving source 9 Rotating shaft 11 Blade 12 Rotating plate 13 Duct 16 Rotating shaft 17 Driving belts 18 and 19 Pulley 21 Feeding device 23 Hydraulic pump 24 Hydraulic pump 26 Hydraulic oil supply pipe Path 28 Directional switching valve
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005239161A JP4738940B2 (en) | 2005-08-19 | 2005-08-19 | Tree crusher |
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| JP2005239161A JP4738940B2 (en) | 2005-08-19 | 2005-08-19 | Tree crusher |
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| JP4738940B2 true JP4738940B2 (en) | 2011-08-03 |
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09193108A (en) * | 1996-01-22 | 1997-07-29 | Komatsu Zenoah Co | Crusher for wood and the like |
| JP2000202808A (en) * | 1998-11-11 | 2000-07-25 | Komatsu Zenoah Co | Self-propelled branch/leaf/trunk crushing machine |
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2005
- 2005-08-19 JP JP2005239161A patent/JP4738940B2/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09193108A (en) * | 1996-01-22 | 1997-07-29 | Komatsu Zenoah Co | Crusher for wood and the like |
| JP2000202808A (en) * | 1998-11-11 | 2000-07-25 | Komatsu Zenoah Co | Self-propelled branch/leaf/trunk crushing machine |
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| JP2007050391A (en) | 2007-03-01 |
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