JPS60175805A - Hydraulic circuit for steering and operational machinery - Google Patents
Hydraulic circuit for steering and operational machineryInfo
- Publication number
- JPS60175805A JPS60175805A JP59030013A JP3001384A JPS60175805A JP S60175805 A JPS60175805 A JP S60175805A JP 59030013 A JP59030013 A JP 59030013A JP 3001384 A JP3001384 A JP 3001384A JP S60175805 A JPS60175805 A JP S60175805A
- Authority
- JP
- Japan
- Prior art keywords
- circuit
- steering
- pump
- supplied
- flow rate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、タイヤショベルローダ、ダンプトラック、モ
ータスクレーパ等に用いられステアリングポンプと補助
ポンプと作業機ポンプの３つのポンプによってステアリ
ング用アクチュエータと作業機用アクチュエータとに圧
油を供給１ｕ１］御するステアリング・作業機用油圧回
路に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention is used in tire shovel loaders, dump trucks, motor scrapers, etc., and provides a steering actuator and a working equipment pump using three pumps: a steering pump, an auxiliary pump, and a working equipment pump. The present invention relates to a hydraulic circuit for a steering/working machine that supplies pressure oil to an actuator (1u1).
従来技術
この種の油圧回路としては第１図に示すようにステアリ
ングポンプ／’、′！１ｌ−ｉｔ回路αで油圧パワース
テアリング用バルブ（以下単にステアリングバルブとす
る）ＡＫ！続し、作業機ポンプＰ２を第２回路Ｃで作業
機バルブｄに接続し、補助ポンプＰｓｋデマンドバルブ
ｅでｍ＋、第２回路ａ、ｃに接続すると共に、デマンド
バルブｅを第１回路σの絞り１前後の差圧で切換え、第
１回路ａの流量が少女い時（ポンプ回転速度が低速の時
）には補助ポンプＰ８の吐出流量１１回路αに供給して
ステアリングバルブ６に多量の油を供給して迅速にステ
アリング操作できる・ようにすると共に、第１回路ａの
流量が多い時（ポンプ回転速度が高速の時）には補助ポ
ンプへの吐出流量全第２回路Ｃに供給して作業機バルブ
ｄに多量の油を供給し、第１回路αの流量が中位の時、
（ポンプ回転速度が中速時）には補助ポンプＰ３の吐出
流量はステアリングの不足油量分のみ、第１回路ａに供
給し、残りの吐出流量は第２回路Ｃに供給するようにし
た油圧回路が知られている。Prior art This type of hydraulic circuit is a steering pump /','!, as shown in Fig. 1. Hydraulic power steering valve (hereinafter simply referred to as steering valve) AK in 1l-it circuit α! Next, the work equipment pump P2 is connected to the work equipment valve d in the second circuit C, the auxiliary pump Psk demand valve e is connected to m+, the second circuits a and c, and the demand valve e is connected to the first circuit σ. It is switched by the differential pressure before and after the throttle 1, and when the flow rate of the first circuit a is small (when the pump rotation speed is low), the discharge flow rate of the auxiliary pump P8 is supplied to the discharge flow rate 11 circuit α, and a large amount of oil is supplied to the steering valve 6. In addition, when the flow rate in the first circuit a is large (when the pump rotation speed is high), the entire discharge flow rate to the auxiliary pump is supplied to the second circuit C. When a large amount of oil is supplied to the work machine valve d and the flow rate of the first circuit α is medium,
(When the pump rotation speed is medium speed), the discharge flow rate of the auxiliary pump P3 is supplied to the first circuit a for the insufficient amount of oil in the steering, and the remaining discharge flow rate is supplied to the second circuit C. circuit is known.
この油圧回路であると、ポンプの吸収トルク金車さくし
てポンプ金駆動するエンジンの馬力全走行に有効できる
と共に、ステアリング操作しても１作業機の速度は変化
しない等の利点を有しているが、その反面に、ポンプ回
転速度が著しく低速の時にはステアリングポンプＰｌと
補助ポンプＰ３との合計流量しかステアリングバルブｂ
に供給されないので、ステアリングへの流量が不足して
思う様にステアリング操作できないとの不具合を有する
。This hydraulic circuit has the advantage that the absorption torque of the pump can be reduced and the full horsepower of the engine driving the pump can be achieved, and the speed of one working machine does not change even when the steering wheel is operated. However, on the other hand, when the pump rotation speed is extremely low, only the total flow rate of the steering pump Pl and the auxiliary pump P3 flows through the steering valve b.
Since the flow is not supplied to the steering wheel, there is a problem that the flow rate to the steering wheel is insufficient and the steering wheel cannot be operated as desired.
第２図の斜線部分が不足範囲である。The shaded area in FIG. 2 is the insufficient area.
第２図において、ＱｌはステアリングポンプＰ。In FIG. 2, Ql is the steering pump P.
の吐出流量、Ｑ２は作業機ポンプＰ２と補助ポンプＰ８
の合計吐出流量、Ｑ！は全ポンプｐ、 、 ｐ、 、
ｐ、の合計吐出流量であり、実線Ａがステアリングバル
ブｂへの必要供給流量である。The discharge flow rate of Q2 is the work equipment pump P2 and the auxiliary pump P8.
Total discharge flow rate, Q! is the total pump p, , p, ,
The solid line A is the total discharge flow rate of p, and the solid line A is the required supply flow rate to the steering valve b.
前述の不具合全解消するには、補助ポンプＰ３の容量を
大きくすれば良いが、この様にすると最小限のポンプ容
量で油圧回路全構成してエンジン馬力を走行に有効利用
することが達成できなくなる。In order to eliminate all of the above-mentioned problems, it is possible to increase the capacity of the auxiliary pump P3, but if you do this, it will not be possible to configure the entire hydraulic circuit with the minimum pump capacity and effectively utilize the engine horsepower for driving. .
そこで、本出願人は先に纂３図に示すような油圧回路全
出願した。Therefore, the present applicant previously filed an application for a complete hydraulic circuit as shown in Figure 3.
この油圧回路では、ステアリングポンプＰＩ’Ｃステア
リング回路１に接続し、作業機ポンプＰ２と補助ポンプ
Ｐ３とをデマンドバルブ６を介してステアリング回路１
と作業機回路７とに接続詞９１１１すると共に、前記デ
マンドバルブ６を、ステアリング回路１に設けた絞９１
２前後の差圧が所定の最小値よシも小さい時には作業機
ポンプＰ２と補助ポンプＰ３の吐出流量全ステアリング
回路１に全量供給し、前記差圧が所定の最小値よυも順
次大きくなると作業機ポンプＰ２と補助ポンプ７Ｊ、の
吐出流量全ステアリング回路１と作業機回路７とに供給
し、前記差圧がＰＪ＋−５ｊＬの最大値よりも大きくな
ると作業機ポンプＰ２と補助ポンプＰ８の吐出流量を全
量作業様回路７に供給するように構成されている。In this hydraulic circuit, a steering pump PI'C is connected to the steering circuit 1, and a work equipment pump P2 and an auxiliary pump P3 are connected to the steering circuit 1 through a demand valve 6.
and the working machine circuit 7, and the demand valve 6 is connected to the throttle 91 provided in the steering circuit 1.
When the differential pressure before and after 2 is smaller than a predetermined minimum value, the entire discharge flow rate of the work equipment pump P2 and the auxiliary pump P3 is supplied to the entire steering circuit 1, and when the differential pressure becomes larger than the predetermined minimum value by υ, the work starts. The discharge flow rate of the machine pump P2 and the auxiliary pump 7J is supplied to the entire steering circuit 1 and the work machine circuit 7, and when the differential pressure becomes larger than the maximum value of PJ+-5jL, the discharge flow rate of the work machine pump P2 and the auxiliary pump P8 is is configured to supply the entire amount to the work-like circuit 7.
この油圧回路６・よ、ポンプ回転速度が著しく低速の時
にはステアリングバルブｌ〕０、作業機ポンプＰ５、補
助ポンプＰ、の吐出流量全全量ステアリング回路１に供
給でき、ステアリングへの流量を十分として思う様にス
テアリング操作できる。When the pump rotation speed is extremely low in this hydraulic circuit 6, the entire discharge flow rate of the steering valve L〕0, work equipment pump P5, and auxiliary pump P can be supplied to the steering circuit 1, so that the flow rate to the steering is sufficient. You can operate the steering wheel.
しかし、この油圧回路の場合には作業機回路流量は第４
）ネＩの実線Ｈの様になり、実用範囲においてポンプ回
転速度低速時に作業機回路流量が少ないために作業機の
作動速度が遅くなると共に、ステアリング操作せずに作
業機全単独で操作した時に作業様ポンプＰ２、補助ポン
プＰ３からステアリング回路１に斜線部分の流量が流れ
るので、それだけの流量（Ｌ：無駄とし、エネルギーロ
スとなってしまう。However, in the case of this hydraulic circuit, the work equipment circuit flow rate is
) In the practical range, when the pump rotation speed is low, the work equipment circuit flow rate is low, so the operating speed of the work equipment becomes slow, and when the work equipment is operated independently without steering operation. Since the flow rate shown in the shaded area flows from the working pump P2 and the auxiliary pump P3 to the steering circuit 1, that much flow rate (L: is wasted and results in energy loss).
発明の目的
ポンプ容量全最小限としてエンジン馬力全走行等に有効
利用できると共に、ポンプ回転が著しく低速回転の時に
ステアリング操作するとステアリング回路に必要流量を
供給でき、作業機を単独操作すると作業機回路に必要流
量を供給できるようにした油圧回路全提供すること。Purpose of the Invention The pump capacity is kept to a minimum so that it can be effectively used for running at full engine horsepower, and when the pump is rotating at a very low speed, steering operation can supply the necessary flow to the steering circuit, and when the work machine is operated independently, the required flow rate can be supplied to the work machine circuit. Provide a complete hydraulic circuit capable of supplying the required flow rate.
発明の構成
作業機ポンプと補助ポンプの吐出流体を作業機回路とス
テアリング回路とに供給するデマンドバルブを、ステア
リング回路に設けた絞り前後の差圧及びデマンドバルブ
を通ってステアリング回路に供給される流量によって切
換作動する構造とし、ポンプ回転が著しく低速回転の時
にステアリング操作すると作業機ポンプ、補助ポンプの
吐出流体がステアリング回路に供給され、ステアリング
操作しないと作業機回路に供給されるようにしたもの。Components of the Invention A demand valve that supplies the discharge fluid of the work equipment pump and the auxiliary pump to the work equipment circuit and the steering circuit is provided in the steering circuit, and the differential pressure before and after the throttle and the flow rate supplied to the steering circuit through the demand valve are When the pump is rotating at an extremely low speed, if the steering is operated, the fluid discharged from the work equipment pump and auxiliary pump is supplied to the steering circuit, and when the steering is not operated, the fluid is supplied to the work equipment circuit.
実施例
第５図において、ステアリングポンプＰＩは第１回路（
ステアリング回路）１に接続し、作業機ポンプＰ、と補
助ポンプＰ、は第２、第３回路２゜３にそれぞれ接続さ
れ、第２、第３回路２．３は逆止弁４を有する短絡路５
で連通され、がっデマンドバルブ６′ｆｔ：介して作業
機回路７と補助［す回路８とに接続制御されると共に、
作業機回路７は作業機バルブ９に接続され、補助回路８
は第１回路１に接続しである。In FIG. 5 of the embodiment, the steering pump PI is connected to the first circuit (
The steering circuit) 1 is connected to the working machine pump P, and the auxiliary pump P is connected to the second and third circuits 2.3, respectively, and the second and third circuits 2.3 are short-circuited with a check valve 4. Road 5
It is connected and controlled to the working machine circuit 7 and the auxiliary circuit 8 through the demand valve 6'ft.
The work machine circuit 7 is connected to the work machine valve 9 and the auxiliary circuit 8
is connected to the first circuit 1.
前記第１回路１はステアリングバルブｉｏを介してステ
アリングシリンダ１１に接続制御されると共に、絞勺１
２が設けてあり、その絞ｐ前後の圧力が第１、第２パイ
ロット路１３．１４でデマンドバルブ６の第１、第２受
圧部６α。The first circuit 1 is connected to and controlled by a steering cylinder 11 via a steering valve io, and is also connected to a throttle valve 1.
2 is provided, and the pressure before and after the throttle p is transmitted to the first and second pressure receiving portions 6α of the demand valve 6 in the first and second pilot paths 13.14.
６ｈに接続しである〇
前記デマンドバルブ６は第２回路２と作業機回路７とを
遮断し、第３回路３を補助回路８に接続する第１位置■
にパネカで保持され、前記絞り１２前後の差圧が所定の
最少値となると第２回路２と作業機回路７とを絞りを介
して連通し、第３回路３と補助回路８とを直接連通ずる
第１連通位置Ｈに切換り、以下順次前記差圧が太き、く
なると第２回路２と第３回路３とを作業機回路７と補助
回路８とに同時に連通ずる第２連通位置■、第２回路２
と作業機回路７とを直接連通しかつｍ３回路３全絞りを
介して補助回路８に連通ずる第３連通位置ＩＶＫ順次切
換えられ、前記差圧が所定の最大値となると第２、第３
回路２’、３ｔｌ一作業機回路７に接続する第５装置Ｖ
に切換えられる。そして各位置の時にはパイロン）ＰＶ
Ｊ＋５にパイロット流体を供給するパイロットボート１
５が形成され、このパイロット路１５は絞り１７全介し
て前記第１受圧部６αに接続しである。6h.〇The demand valve 6 is in the first position where it cuts off the second circuit 2 and the working machine circuit 7 and connects the third circuit 3 to the auxiliary circuit 8■
When the differential pressure before and after the throttle 12 reaches a predetermined minimum value, the second circuit 2 and the working machine circuit 7 are connected through the throttle, and the third circuit 3 and the auxiliary circuit 8 are connected directly. When the differential pressure gradually increases, the second communication position H switches the second circuit 2 and the third circuit 3 to the working machine circuit 7 and the auxiliary circuit 8 at the same time. , second circuit 2
and a third communication position IVK which directly communicates with the working machine circuit 7 and communicates with the auxiliary circuit 8 through the full throttle of the m3 circuit 3. When the differential pressure reaches a predetermined maximum value, the second and third communication positions
Circuit 2', 3tl-fifth device V connected to work machine circuit 7
can be switched to and at each position pylon) PV
Pilot boat 1 that supplies pilot fluid to J+5
5 is formed, and this pilot path 15 is connected to the first pressure receiving portion 6α through the entire throttle 17.
したがって、デマンドバルブ６は絞９１２前後の差圧、
及びパイロットボート１４を流れる流量によって各位置
に切換え制御される。Therefore, the demand valve 6 has a differential pressure before and after the throttle 912,
It is switched and controlled to each position depending on the flow rate flowing through the pilot boat 14.
しかして、ボンボ回転（っマク、エンジンＭの回転）が
著しく低速回転速度の時には、第１回路１の流量が少な
く絞シ１２前後の差圧が所定の最少値よりも低いので、
デマンドバルブ６は第１位ＩＲＩに保持され、作業機ポ
ンプＰ２と補助ポンプＰ、の吐出流量が第１回路１に供
給される。However, when the rotation speed of the engine M is extremely low, the flow rate in the first circuit 1 is small and the differential pressure across the throttle 12 is lower than the predetermined minimum value.
The demand valve 6 is held at the first IRI, and the discharge flow rates of the work equipment pump P2 and the auxiliary pump P are supplied to the first circuit 1.
この状態で、ステアリングバルブ１０を操作すればステ
アリングシリンダ１１に流体が供給され、その供給流量
は十分なものとなり、迅速なステアリングが操作できる
。In this state, if the steering valve 10 is operated, fluid is supplied to the steering cylinder 11, and the supply flow rate is sufficient, allowing quick steering operation.
この時、絞り１２前後の差圧は大きくなり、デマンドバ
ルブ６は順次第１、第２、Ｍ３３連位置ｎ、ｍ、 ■に
切換えられ、ステアリングの操作速度に見合った流ｔが
供給されることになる。At this time, the differential pressure before and after the throttle 12 becomes large, and the demand valve 6 is sequentially switched to the 1st, 2nd, and M3 triple positions n, m, and (2), and a flow t commensurate with the steering operation speed is supplied. become.
また、前述の状態においてステアリング操作しないと絞
り１２前後の圧力差は著しく小さく、補助管路８には多
量の流体が供給されるので、パイロットボートＩ６にも
多量の流体が流れ、パイロット路１５内の圧力は高くな
るので、デマンドバルブ６は第２、第３連通位置１［１
，ＩＶに向けて押動されて最終的には第５装置Ｖとなる
から、作業機ポンプＰ２と補助ポンプＰｓとの吐出流体
は作業機回路７に供給され、作業機には必要なる流体が
流れることになり、作業機を速く作動できる。In addition, if the steering is not operated in the above-mentioned state, the pressure difference before and after the throttle 12 will be extremely small, and a large amount of fluid will be supplied to the auxiliary pipe 8, so a large amount of fluid will also flow into the pilot boat I6, and the pilot boat I6 will have a large amount of fluid. , the demand valve 6 moves to the second and third communication positions 1[1].
, IV and finally becomes the fifth device V, the discharge fluid of the work equipment pump P2 and the auxiliary pump Ps is supplied to the work equipment circuit 7, and the work equipment is supplied with the necessary fluid. This allows the work equipment to operate faster.
この様に、デマンドバルブ６は絞９１２前後の差圧とデ
マンドバルブ６より補助管路８へ流れる流量によって各
位置に切換作動されてステアリング操作速度に見合った
流量ラステアリング回路１に供給し、残りの流量を作業
機回路７に供給するので、ポンプ回転が著〜しく低速の
時にステアリング操作すればステアリング回路１に必要
流量全供給でき、ステアリング操作しなければ作業機回
路７に必要流量を供給できる。In this way, the demand valve 6 is switched to each position depending on the differential pressure before and after the throttle 912 and the flow rate flowing from the demand valve 6 to the auxiliary pipe 8, and supplies the flow rate to the last steering circuit 1 in accordance with the steering operation speed. Since this flow rate is supplied to the work equipment circuit 7, if the steering operation is performed when the pump rotation speed is extremely low, the entire required flow rate can be supplied to the steering circuit 1, and if the steering operation is not performed, the required flow rate can be supplied to the work equipment circuit 7. .
つまり、作業機回路７の流量は第６図において、Ｂ、
−１３，の範囲全圧力条件（補助管路８の流量）に基づ
いて変化する。In other words, the flow rate of the work machine circuit 7 is B,
-13, varies based on the total pressure condition (flow rate of auxiliary pipe 8).
また、ポンプ回転が中速回転速度の時には第１回路１の
流量が多くなって絞りＩ２前後の差圧が所定の最少値よ
りも高くなりデマンドバルブ６は第１連通位置■となり
、作業機ポンプへの吐出流量は第１回路１と作業機回路
７とに供給され補助ポンプｌＪｓの吐出流量は第１回路
１に供給されてステアリングポンプＰ１の流量不辰ヲ補
うと共に、作業４３ｑバルブ９に供給される。Furthermore, when the pump rotation is at a medium rotation speed, the flow rate of the first circuit 1 increases, and the differential pressure before and after the throttle I2 becomes higher than the predetermined minimum value, and the demand valve 6 becomes the first communication position ■, and the work equipment pump The discharge flow rate of the auxiliary pump lJs is supplied to the first circuit 1 and the work equipment circuit 7, and the discharge flow rate of the auxiliary pump lJs is supplied to the first circuit 1 to compensate for the insufficient flow rate of the steering pump P1, and is also supplied to the work 43q valve 9. be done.
以下順次ポンプ回転が速くなると絞り１２前後の差圧が
順次大きくなってデマンドバルブ６は爪２、第３連通位
置Ｉｌｌ 、、 ＩＶに順次切換えられ、作業機ポンプ
Ｐ２と補助ポンプＰ３との吐出流量：は第１回路１への
供給流量が１１［１次減少し、作業機バルブ９への供給
流量が順次増大する。Thereafter, as the pump rotation speeds up, the differential pressure before and after the throttle 12 increases, and the demand valve 6 is sequentially switched to the claw 2, third communication position Ill, IV, and the discharge flow rate of the work equipment pump P2 and the auxiliary pump P3 increases. : The flow rate supplied to the first circuit 1 decreases by 11 [1], and the flow rate supplied to the working machine valve 9 increases sequentially.
また、ポンプ回転が高速回転速度となると第１回路１の
流量がステアリングシリンダ１１への必要供給流」７１
゛以上となって絞り１２前後の差圧が所定の酸大値以−
ヒとなり、゛デマンドバルブ６は第２７通装置Ｖとなる
から、作業機ポンプｐ２と補助ポンプＰ３の吐出流量（
は作業機回Ｖ６７に合流供給される。Furthermore, when the pump rotation reaches a high rotational speed, the flow rate of the first circuit 1 increases to the required supply flow to the steering cylinder 11.
゛The differential pressure before and after the orifice 12 exceeds the predetermined maximum acid value.
Since the demand valve 6 becomes the 27th communication device V, the discharge flow rate of the work equipment pump p2 and the auxiliary pump P3 (
is combined and supplied to the working machine V67.
第７図はデマンドバルブの具体例を示し、ステアリング
バルブ１０とデマンドバルブ６とは弁本体２０内に組込
外れている。FIG. 7 shows a specific example of the demand valve, in which the steering valve 10 and the demand valve 6 are disassembled from the valve body 20.
つまり、弁本体２０の詔１、第２弁孔２１．２２には第
１、第２スプール２３．２４が嵌挿され、第１スプール
２３を左右に摺動することで絞り１２を経て流入した流
体がステアリングシリンダ１１に供給されると共に、第
２スプール２４は左右受圧部６α、６Ａの圧力差によっ
てバネ２５に抗してボート２６と補助管路８となる油孔
とを遮断する方向に押動され、第２スグール２４にはボ
ート２６に絞９１７で開口したパイロットボート１６（
パイロット路１５）が形成してあり、このパイロットボ
ート１６は右受圧部６ａに連通し、かつ絞Ｊ２７ｉ介し
て補助管路８となる油孔に連通している。That is, the first and second spools 23 and 24 are fitted into the first and second valve holes 21 and 22 of the valve body 20, and by sliding the first spool 23 from side to side, the flow of water through the throttle 12 is caused. While the fluid is supplied to the steering cylinder 11, the second spool 24 is pushed against the spring 25 by the pressure difference between the left and right pressure receiving parts 6α and 6A in a direction that blocks the boat 26 and the oil hole that becomes the auxiliary pipe 8. The pilot boat 16 (which has an opening in the boat 26 with an aperture 917
A pilot passage 15) is formed, and this pilot boat 16 communicates with the right pressure receiving part 6a, and also with an oil hole which becomes the auxiliary conduit 8 via a restriction J27i.
発明の効果
ポンプ容量ケ最小限としてエンジン馬力を走行等に有効
利用できる。Effects of the Invention By minimizing the pump capacity, engine horsepower can be effectively utilized for driving, etc.
ポンプ回転が著しく低速回転の時にステアリング操作す
ると作業機ポンプＰ２、補助ポンプＰ３の吐出流体がス
テアリング回路１に供給されるから、ステアリング回路
に必要流量を供給でき、ステアリング操作しないと作業
機ポンプＰ７、補助ポンプＰ３の吐出流体が作業機回路
７に供給されるから作業機単独操作した時に作業機回路
７に必要流１１？−を供給できる。If the steering operation is performed when the pump rotation speed is extremely low, the discharge fluid of the work equipment pump P2 and the auxiliary pump P3 will be supplied to the steering circuit 1, so the required flow rate can be supplied to the steering circuit.If the steering operation is not performed, the work equipment pump P7, Since the discharge fluid of the auxiliary pump P3 is supplied to the work equipment circuit 7, when the work equipment is operated alone, the required flow 11? − can be supplied.
第１図は従来の油圧回路図、第２図はその流暗特性金示
す表面、第３図は不出ＩｉＱ人が先に出願した油圧回１
烙図、第４図はその流量特性金示す表面、第５図は本発
明の実施例を示す油圧回路図、第６図はその流山１特性
金示す嵌置、第７図はデマンドバルブの具体例を示す断
面図である。
Ｐ、はステアリングポンプ、Ｐ２（ａ作業機ポンプ、Ｐ
３は補助ポンプ、１はステアリング回路、６はデマンド
バルブ、７は作業機回路、８は補助管路、１２は絞り。
山鳥【［４人 株式会社 小松製作所
代理人弁即士米原正章
弁理士浜本 忠
［
第６図
ネ・ンブ伊東ん丈ｊしFigure 1 is a conventional hydraulic circuit diagram, Figure 2 is the surface showing its flow-dark characteristics, and Figure 3 is the hydraulic circuit 1 that was previously filed by IiQ.
Fig. 4 shows the surface showing the flow rate characteristics, Fig. 5 shows the hydraulic circuit diagram of an embodiment of the present invention, Fig. 6 shows the fitting showing the flow rate characteristics, and Fig. 7 shows the details of the demand valve. It is a sectional view showing an example. P is steering pump, P2 (a work equipment pump, P
3 is an auxiliary pump, 1 is a steering circuit, 6 is a demand valve, 7 is a work machine circuit, 8 is an auxiliary pipe, and 12 is a throttle. Yamatori [[4 people Komatsu Ltd. Representative attorney Masaaki Yonehara Patent attorney Tadashi Hamamoto [Fig.
Claims (1)
ンドバルブ６を介してステアリング回路１に接続した補
助管路８と作業機回路７とに接続制御すると共に、前記
デマンドバルブ６を、ステアリング回路１に設けた絞り
１２前後の差圧とデマンドバルブ６全通って補助管路８
に供給される流量とによって、ポンプ回転が著しく低速
回転の時にステアリング操作すると作業機ポンプＰ２、
補助ポンプＰ３の吐出流体全ステアリング回路１に供給
し、かつステアリング操作しないと作業機回路７に供給
する構造としたことを特徴とするステアリング・作業機
用油圧回路。[Claims] The steering circuit 1 includes a steering pump P. and connect and control the auxiliary pump P3 to the work machine pump to the work machine circuit 7 and the auxiliary pipe line 8 connected to the steering circuit 1 via the demand valve 6, and connect the demand valve 6 to the steering circuit 1. The differential pressure before and after the throttle 12 provided in 1 and the demand valve 6 all pass through to the auxiliary pipe 8.
Due to the flow rate supplied to P2, if the steering operation is performed when the pump rotation speed is extremely low, the work equipment pump P2,
A hydraulic circuit for a steering/working machine characterized by having a structure in which the discharge fluid of the auxiliary pump P3 is supplied to the entire steering circuit 1, and is also supplied to the working machine circuit 7 when the steering is not operated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59030013A JPS60175805A (en) | 1984-02-20 | 1984-02-20 | Hydraulic circuit for steering and operational machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59030013A JPS60175805A (en) | 1984-02-20 | 1984-02-20 | Hydraulic circuit for steering and operational machinery |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60175805A true JPS60175805A (en) | 1985-09-10 |
Family
ID=12291976
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59030013A Pending JPS60175805A (en) | 1984-02-20 | 1984-02-20 | Hydraulic circuit for steering and operational machinery |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60175805A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5775276A (en) * | 1995-02-15 | 1998-07-07 | Toyota Jidosha Kabushiki Kaisha | Valve driving apparatus using an electromagnetic coil to move a valve body with reduced noise |
| EP0896132A1 (en) | 1997-08-08 | 1999-02-10 | Toyota Jidosha Kabushiki Kaisha | Solenoid valve device |
| US5875746A (en) * | 1997-04-02 | 1999-03-02 | Torota Jidosha Kabushiki Kaisha | Cylinder head structure for an internal combustion engine |
| US6366831B1 (en) | 1993-02-23 | 2002-04-02 | Faro Technologies Inc. | Coordinate measurement machine with articulated arm and software interface |
| WO2014097423A1 (en) * | 2012-12-19 | 2014-06-26 | 株式会社 島津製作所 | Hydraulic circuit and cargo-handling vehicle |
-
1984
- 1984-02-20 JP JP59030013A patent/JPS60175805A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6366831B1 (en) | 1993-02-23 | 2002-04-02 | Faro Technologies Inc. | Coordinate measurement machine with articulated arm and software interface |
| US6535794B1 (en) | 1993-02-23 | 2003-03-18 | Faro Technologoies Inc. | Method of generating an error map for calibration of a robot or multi-axis machining center |
| US6606539B2 (en) | 1993-02-23 | 2003-08-12 | Faro Technologies, Inc. | Portable coordinate measurement machine with pre-stressed bearings |
| US5775276A (en) * | 1995-02-15 | 1998-07-07 | Toyota Jidosha Kabushiki Kaisha | Valve driving apparatus using an electromagnetic coil to move a valve body with reduced noise |
| US5875746A (en) * | 1997-04-02 | 1999-03-02 | Torota Jidosha Kabushiki Kaisha | Cylinder head structure for an internal combustion engine |
| EP0896132A1 (en) | 1997-08-08 | 1999-02-10 | Toyota Jidosha Kabushiki Kaisha | Solenoid valve device |
| US6032925A (en) * | 1997-08-08 | 2000-03-07 | Toyota Jidosha Kabushiki Kaisha | Gel cushioned solenoid valve device |
| WO2014097423A1 (en) * | 2012-12-19 | 2014-06-26 | 株式会社 島津製作所 | Hydraulic circuit and cargo-handling vehicle |
| TWI486529B (en) * | 2012-12-19 | 2015-06-01 | Shimadzu Corp | Hydraulic circuit and loading and unloading vehicle |
| JP5896041B2 (en) * | 2012-12-19 | 2016-03-30 | 株式会社島津製作所 | Hydraulic circuit and cargo handling vehicle |
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