JPS589301B2 - Hydrostatic drive - Google Patents

Hydrostatic drive

Info

Publication number
JPS589301B2
JPS589301B2 JP48020288A JP2028873A JPS589301B2 JP S589301 B2 JPS589301 B2 JP S589301B2 JP 48020288 A JP48020288 A JP 48020288A JP 2028873 A JP2028873 A JP 2028873A JP S589301 B2 JPS589301 B2 JP S589301B2
Authority
JP
Japan
Prior art keywords
pump
pressure
conduit
low
pressure side
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
JP48020288A
Other languages
Japanese (ja)
Other versions
JPS48103961A (en
Inventor
カール・シユレヒト
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BUTSUTSUMAISUTAA INTAAHORUDEINGU GmbH
Original Assignee
BUTSUTSUMAISUTAA INTAAHORUDEINGU GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by BUTSUTSUMAISUTAA INTAAHORUDEINGU GmbH filed Critical BUTSUTSUMAISUTAA INTAAHORUDEINGU GmbH
Publication of JPS48103961A publication Critical patent/JPS48103961A/ja
Priority to US05/442,627 priority Critical patent/US3942858A/en
Priority to DE19742407516 priority patent/DE2407516B2/en
Publication of JPS589301B2 publication Critical patent/JPS589301B2/en
Expired legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/433—Pump capacity control by fluid pressure control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4183—Preventing or reducing vibrations or noise, e.g. avoiding cavitations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/46—Automatic regulation in accordance with output requirements
    • F16H61/465—Automatic regulation in accordance with output requirements for achieving a target input speed

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Fluid Gearings (AREA)
  • Control Of Transmission Device (AREA)

Description

【発明の詳細な説明】 本発明は、特に斜板を有する可変容量アキシャルポンプ
が液圧モーター又は選択的にコンクリート用ポンプの油
圧シリンダー等を駆動する液圧駆動装置に関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION The present invention particularly relates to a hydraulic drive device in which a variable displacement axial pump with a swash plate drives a hydraulic motor or optionally a hydraulic cylinder of a concrete pump or the like.

此の種の駆動装置ではしばしば、一定の回転数で回転す
る場合に於いてさえもモーターの負荷が急激に変化する
。In this type of drive device, the load on the motor often changes rapidly even when rotating at a constant rotational speed.

ロータ一式又はピストン式コンクリート用ポンプに於で
、ストロークの切換毎に又は吐出回転体の作動毎に供給
管内で静止するコンクリートの柱体を再び加速しなけれ
ばならない此の場合定量吐出ポンプにより駆動されてい
るので油圧モーターの回転速度ないしは供給シリンダー
のピストンロンドの速度は常に一様である。In a complete rotor or piston type concrete pump, the concrete column which is stationary in the supply pipe must be accelerated again at every change of stroke or every actuation of the delivery rotor, in which case it is driven by the metering delivery pump. Therefore, the rotational speed of the hydraulic motor or the speed of the piston rod of the supply cylinder is always uniform.

コンクリートの柱体を再加速するために大きな力を必要
とするこ吉は一方に於で、駆動装置の高圧側に短時間に
高い圧力の上昇を生ぜしめ、此の際ピーク時における圧
力の値は時々リリーフ弁が応答し熱の発生が著しくなる
ほど高くなる。On the one hand, Kokichi, which requires a large force to re-accelerate the concrete column, causes a high pressure rise in a short time on the high-pressure side of the drive device, and in this case the pressure value at the peak is sometimes The higher the relief valve responds, the more heat is generated.

他方に於で急激に加速されたコンクリートの柱体は例え
ばコンクリート導管に衝撃を生じるような具合の悪い反
作用を生じる。On the other hand, a rapidly accelerated concrete column produces an undesirable reaction, such as impacting a concrete conduit.

此の不利を回避するためにストロークの切換毎に油圧ポ
ンプを送り出し量零の状態にし、ゆつくりとコンクリー
トの柱体を移動させるように調節されることが考えられ
るがいろいろの理由、特に供給ピストンの切換の時間と
同ピストンがコンクリートの柱体に作用して加速を開始
する瞬間との間の時間間隔がコンクリートの組成とポン
プの回転速度に依り非常に異なるということで不可能で
ある。In order to avoid this disadvantage, it is conceivable that the hydraulic pump is adjusted to a zero delivery state at each stroke change and the concrete column is moved slowly, but there are various reasons, especially the supply piston. This is not possible because the time interval between the time of switching and the moment when the same piston acts on the concrete column and starts to accelerate is very different depending on the composition of the concrete and the rotational speed of the pump.

たびたび此の加速力のピーク値が供給圧力の２００％を
越えるのを回避するためには既知の圧力補償手段も用い
ることができない。In order to avoid that the peak value of this acceleration force often exceeds 200% of the supply pressure, known pressure compensation means cannot be used either.

なぜならコンクリートの供給の場合の圧力のレベルは、
コンクリ−トの濃度と供給導管の長さが変化するために
常に変化するからである。Because the level of pressure in case of concrete supply is
This is because the concentration of the concrete and the length of the supply conduit are constantly changing.

多くの静液圧ポンプに於で、特に斜板式アキシャルピス
トンポンプに於ては、圧力上昇の際圧力油の漏洩が高ま
る。In many hydrostatic pumps, especially swash plate axial piston pumps, leakage of pressure oil increases as pressure increases.

此れは此の種のポンプの制御板が間隙量により圧力を受
けたり圧力を受けなかったりして相対回転するその間隙
の値が変化することに基本的に理由があるとされている
。The basic reason for this is said to be that the control plate of this type of pump receives pressure or does not receive pressure depending on the amount of the gap, and the value of the gap in which the control plate rotates relative to each other changes.

此の結果回路が閉鎖している場合には、圧力の上昇が急
激な場合には供給ポンプの供給量がしばしば充分でなく
なる。As a result of this, when the circuit is closed, the supply pump's supply rate is often insufficient if the pressure rises rapidly.

此の結果供給油量が減少し低圧側の油の予圧力が低下し
、やっかいで有害なキャビテーションを発生する原因と
なる。As a result, the amount of oil supplied decreases and the preload force of the oil on the low pressure side decreases, causing troublesome and harmful cavitation.

高圧側の圧力が所定のレベルになると直ちに油の漏洩が
再び通常の値になる。As soon as the pressure on the high side reaches a predetermined level, the oil leakage returns to its normal value.

本発明は静液圧ポンプにおける圧力の急上昇により低圧
側の液体の予圧が低下するのを回避した静液圧駆動装置
を提供することを目的としている。SUMMARY OF THE INVENTION An object of the present invention is to provide a hydrostatic drive device that avoids a drop in the pre-pressure of a low-pressure liquid due to a sudden increase in pressure in a hydrostatic pump.

この目的を本発明は従来不利であると思われていた現象
を利用することにより達成した。This object has been achieved by the present invention by taking advantage of a phenomenon hitherto considered to be disadvantageous.

最近の駆動装置における多くの油圧ポンプでは供給量は
もはや機械的には制御されず油圧調節シリンダーを介し
て、例えば駆動モーターの回転数を基として制御される
ので、液圧調節シリンダーが装着された液圧ポンプ、特
に予圧力が掛けられた液圧回路の中で供給ポンプ及びそ
れに所属の通常の充填圧力限定手段、フラツシ弁及び切
換弁が装備された、斜板式アキシャルポンプに於で、本
発明に依り、調節シリンダーの圧力室をポンプの低圧側
の導管と逆止弁を介して接続し、液体の漏洩が高まる結
果低圧側で圧力が降下した場合に圧力液が制御シリンダ
ーから前記逆止弁を経てポンプの低圧側に流れ且つ上記
の逆止弁に依り液体が逆の方向に流れるのが阻止される
ようにした構成が提案される。In many hydraulic pumps in modern drive systems, the supply volume is no longer controlled mechanically, but via a hydraulic regulating cylinder, e.g. on the basis of the rotational speed of the drive motor, so a hydraulic regulating cylinder is installed. The invention relates to hydraulic pumps, in particular swash plate axial pumps, which are equipped with a feed pump and its associated customary filling pressure limiting means, flush valves and switching valves in a prestressed hydraulic circuit. The pressure chamber of the regulating cylinder is connected to the conduit on the low-pressure side of the pump via a check valve, so that if the pressure drops on the low-pressure side as a result of increased liquid leakage, the pressure fluid will flow from the control cylinder to the said check valve. A configuration is proposed in which the liquid flows to the low-pressure side of the pump through the liquid, and the check valve prevents the liquid from flowing in the opposite direction.

此の結果特にポンプの斜板が一時的に動かされて圧力導
管の中の圧力の上昇速度が減少される。As a result of this, in particular the swash plate of the pump is temporarily moved and the rate of pressure rise in the pressure conduit is reduced.

供給料が供給圧力とは関係なく斜板を内部サーボ調節手
段に依って調節することにより調節される本発明に依る
装置に於で、サーボ調節装置が外部調節シリンダーに枢
着されている外部調節レバーを備え、内部調節シリンダ
ーが同様に低圧導管との接続部を備え、同低圧導管との
接続が逆止弁を介して行なわれると有利である。In a device according to the invention, in which the feed rate is regulated by adjusting the swash plate by means of an internal servo-adjustment means independently of the supply pressure, the servo-adjustment means is pivotally connected to the external adjustment cylinder. It is advantageous if the internal regulating cylinder, which is equipped with a lever, is also provided with a connection to a low-pressure line, with the connection being effected via a check valve.

此の場合外部調節シリンダーがばねを備え、同ばねの復
帰力がポンプの低圧導管の中の圧力よりもごくわずかし
か低くない圧力と一致していると有利である。In this case, it is advantageous if the external adjusting cylinder is equipped with a spring, the restoring force of which corresponds to a pressure that is only slightly lower than the pressure in the low-pressure line of the pump.

外部調節シリンダー並びに此のシリングーと逆止弁を介
して結合されている低圧導管及びサーボ切換弁も此の場
合外部補助ポンプから供給される。The external regulating cylinder as well as the low-pressure line and the servo-switching valve, which are connected to this cylinder via a check valve, are in this case also fed by an external auxiliary pump.

本発明の更に他の構成に於で、サーボ切換弁は逆止弁を
介して補助ポンプと結合されている。In a further development of the invention, the servo switching valve is connected to the auxiliary pump via a check valve.

通常ポンプにフランジ固定されている供給ポンプは此の
様な装置に於では省略されることができる。The feed pump, which is normally flange-fixed to the pump, can be omitted in such devices.

本発明に依る装置の更に他の有利な構成に於で、補助ポ
ンプ及び同ポンプの後に接続された絞りが省略された場
合に調節シリンダーが機械的な調節装置と結合されてお
り、調節シリンダーの底側か調節絞りと逆止弁とを介し
てポンプのサーボ制御圧力側と結合されることができる
。In a further advantageous embodiment of the device according to the invention, if the auxiliary pump and the throttle connected after the pump are omitted, the regulating cylinder is combined with a mechanical regulating device, and the regulating cylinder is connected to a mechanical regulating device. The bottom side can be connected to the servo-controlled pressure side of the pump via a regulating throttle and a check valve.

以下本発明を添付の実施例に関する図面に就き詳細に説
明する。The invention will now be described in detail with reference to the attached drawings and embodiments.

ポンプ１の主回路のそれぞれの低圧側に、充填圧力安全
弁６に依って保護された供給ポンプ５から逆止弁７を介
して液圧が供給される。The respective low-pressure side of the main circuit of the pumps 1 is supplied with hydraulic pressure via a check valve 7 from a supply pump 5 protected by a filling pressure relief valve 6 .

説明を簡単にするために主回路のポンプ１は一方向にの
み液体を供給し、逆には作動しない斜板式ポンプの例に
ついて示されている。To simplify the explanation, the pump 1 of the main circuit is shown as an example of a swash plate pump that supplies liquid only in one direction and does not operate in the opposite direction.

しかし高圧側、低圧側を交互に切換える場合も可能であ
る。However, it is also possible to alternately switch between the high pressure side and the low pressure side.

ポンプ１の供給量は公知の如く斜板の調節により制御さ
れ、その斜板の調節は、斜板の調節部材と連結された剛
性のある機械的結合千段９、例えばロンドにより行なわ
れる。The feed rate of the pump 1 is controlled in a known manner by the adjustment of a swashplate, which is effected by a rigid mechanical coupling stage 9, for example a rond, connected to the adjusting member of the swashplate.

前記結合手段９は内部調節シリンダー８のピストンロン
ドと連結されている。Said coupling means 9 are connected to the piston rod of the internal adjustment cylinder 8.

内部調節シリンダー８のピストンロツドの出入動ば供給
ポンプ５からサーボ方式の切換弁（以下サーボ切換弁と
いう）１０を経て内部調節シリンダー８に供給される液
体の圧力の作用により行なわれる内部調節シリンダー８
のピストンロンドと前記サーボ切換弁１０、例えばサー
ボ切換弁１０のケーシング部とが機械的にフィードバッ
ク手段２０、例えばフィードバックロツド２０により連
結されている。When the piston rod of the internal adjustment cylinder 8 moves in and out, the internal adjustment cylinder 8 is controlled by the pressure of the liquid supplied from the supply pump 5 to the internal adjustment cylinder 8 via a servo type switching valve (hereinafter referred to as servo switching valve) 10.
The piston rod and the servo switching valve 10, for example the casing portion of the servo switching valve 10, are mechanically connected by a feedback means 20, for example a feedback rod 20.

サーボ切換弁１０の調節レバー１２がニュートラル位置
から動かされていると、軸４がポンプ１及び供給ポンプ
５を駆動すると直ちにサーボ切換弁１０を通して内部調
節シリンダー８に液体が供給されることにより内部調節
シリンダー８のピストンロツドが突出し、その動きによ
り結合千段９を介して斜板が調節される。If the regulating lever 12 of the servo switching valve 10 is moved from the neutral position, as soon as the shaft 4 drives the pump 1 and the supply pump 5, liquid is supplied to the internal regulating cylinder 8 through the servo switching valve 10, thereby causing internal regulation. The piston rod of the cylinder 8 protrudes and its movement adjusts the swash plate via the connecting stage 9.

同時にサーボ切換弁１０がフィードバックロンド２０に
より動かされ、主ポンプの供給量が所要の値になる斜板
の位置に達するとサーボ切換弁１０はニュートラル位置
に復帰する。At the same time, the servo switching valve 10 is moved by the feedback iron 20, and when the swash plate position at which the supply amount of the main pump reaches the required value is reached, the servo switching valve 10 returns to the neutral position.

サーボ切換弁の調節レバーの制御は外部調節シリンダー
１３の作用により行なわれ、該外部調節シリンダーのピ
ストンは復帰ばね１７により通常零位置すなわちシリン
ダーの底部に押圧される位置に保持される。The control of the adjusting lever of the servo switching valve takes place by the action of an external adjusting cylinder 13, the piston of which is normally held by a return spring 17 in the zero position, ie in a position pressed against the bottom of the cylinder.

外部調節シリンダーは補助ポンプ１４の吐出側と主回路
の低圧側導管（主ポンプ１の吸入側に連結された導管）
３との間に配設された導管と逆止弁１６を介して接続し
ている。The external adjustment cylinder is connected to the discharge side of the auxiliary pump 14 and the low-pressure side conduit of the main circuit (the conduit connected to the suction side of the main pump 1).
3 through a conduit and a check valve 16.

外部調節シリンダー１３の必要な調節圧力は補助ポンプ
１４により供給され、該補助ポンプは一般にポンプ１と
同じモーターによってすなわちポンプ１の回転速度と比
例した速度で駆動される。The necessary regulating pressure of the external regulating cylinder 13 is supplied by an auxiliary pump 14, which is generally driven by the same motor as the pump 1, ie at a speed proportional to the rotational speed of the pump 1.

補助ポンプ１４より吐出される液体の一部は調節絞り１
５を通してすぐにタンクに排出される。A part of the liquid discharged from the auxiliary pump 14 is controlled by the adjustment throttle 1.
5 and is immediately discharged into the tank.

補助ポンプ１４にはリリ−フ弁が連結されている。A relief valve is connected to the auxiliary pump 14.

絞１５が所定の如くに調節された場合には調節シリンダ
ー１３の中で作用する制御油圧が駆動モータの回転数に
ほゾ比例して上昇する。When the throttle 15 is adjusted in a defined manner, the control oil pressure acting in the adjusting cylinder 13 increases in proportion to the rotational speed of the drive motor.

回転数がある所定の値の場合にはばね１７の予張力が克
服されて調節シリンダー１３のピストンが突出し従って
調節レバー１２が動かされ、サーボ機構を介してポンプ
１の供給量が変えられる。At a certain predetermined value of the rotational speed, the pretension of the spring 17 is overcome and the piston of the adjusting cylinder 13 protrudes, so that the adjusting lever 12 is moved and the supply rate of the pump 1 is varied via the servomechanism.

絞り１５が閉じられているとき場合によってはリリ−フ
弁による制限下で補助ポンプ１４から外部調節シリンダ
ー１３及び主回路の低圧導管３には最大液圧が作用され
る。When the throttle 15 is closed, a maximum hydraulic pressure is exerted from the auxiliary pump 14 on the external regulating cylinder 13 and on the low-pressure line 3 of the main circuit, possibly with the limitation of a relief valve.

この圧力は低圧導管３の正常運転時の圧力と同じか低圧
導管３の圧力より僅かに小さい圧力である（この場合は
逆止弁１６は閉じている。This pressure is the same as the pressure in normal operation of the low-pressure conduit 3 or slightly less than the pressure in the low-pressure conduit 3 (in this case, the check valve 16 is closed).

）この最大圧力は装置の正常な運転時、すなわちポンプ
１の一定の値に調節された供給出力において特に供給ポ
ンプ５によりもはや補われることができないように液洩
れを生じて圧力導管３の圧力が低下するときに維持され
る。) This maximum pressure during normal operation of the device, i.e. at a feed output of pump 1 set to a constant value, in particular causes leakage and the pressure in pressure line 3 is such that it can no longer be compensated by feed pump 5. maintained when it declines.

今回転数が一定の場合に主ポンプ１が作動状態に入り、
同状態に依り高圧導管２の圧力を急速に強く圧力上昇さ
せると、その結果著しい液体が閉じた作動回路（主回路
）からポンプの例えばアキシャルピストンポンプのバル
ブの部分においてタンクに接続された液体排出可能なケ
ーシングの中へと漏洩する。If the rotation speed is now constant, the main pump 1 enters the operating state,
If the pressure in the high-pressure conduit 2 is rapidly and strongly increased due to the same situation, as a result a significant amount of liquid is discharged from the closed working circuit (main circuit) to the liquid discharge connected to the tank in the valve part of the pump, for example in an axial piston pump. Possible leakage into the casing.

上記の漏洩は供給ポンプ５の通常の出力範囲においては
同ポンプに依ってはもはや補充されることができない。The above-mentioned leakage can no longer be replenished by the supply pump 5 in its normal power range.

此の結果低圧導管の中に圧力の降下即ちキャビテーショ
ン現象が発生する危険が生じるであろう。This would result in a risk of a pressure drop or cavitation phenomenon occurring in the low-pressure conduit.

低圧導管３の圧力が低下し補助ポンプ１４（サーボ圧力
源）からの圧力よりも低くなると逆止弁１６が開いて液
体は補助ポンプ１４から低圧導管３へと供給され、補助
ポンプ１４と低圧導管３とを結んでいる導管内の圧力が
変動し、外部調節シリンダー１３のピストン１３ａに作
用する圧力が変動し、復帰ばね１７の力との平衡が破れ
るとピストン１３ａは移動する。When the pressure in the low-pressure conduit 3 decreases and becomes lower than the pressure from the auxiliary pump 14 (servo pressure source), the check valve 16 opens and liquid is supplied from the auxiliary pump 14 to the low-pressure conduit 3, and between the auxiliary pump 14 and the low-pressure conduit. 3, the pressure acting on the piston 13a of the external adjustment cylinder 13 changes, and when the equilibrium with the force of the return spring 17 is broken, the piston 13a moves.

ピストン１７のロンドはサーボ切換弁１０の調節レバー
１２と連結されているので、ピストン１３ａの移動によ
り調節レバー１２が動かされ、サーボ切換弁１０が切換
えられて内部調節シリンダー８のピストンが動かされ、
ポンプ１の斜板が制御されてポンプ１の供給出力が低下
される。Since the rond of the piston 17 is connected to the adjustment lever 12 of the servo switching valve 10, the adjustment lever 12 is moved by the movement of the piston 13a, the servo switching valve 10 is switched, and the piston of the internal adjustment cylinder 8 is moved.
The swash plate of pump 1 is controlled to reduce the supply output of pump 1.

斯くして供給液量が減少しポンプ１の主回路における急
激な圧力上昇が回避される。In this way, the amount of liquid to be supplied is reduced and a sudden pressure increase in the main circuit of the pump 1 is avoided.

油の漏洩が供給ポンプ５と補助ポンプ１４による供給量
を越える間はポンプ１の供給量を低下させる制御が行な
われる。While oil leakage exceeds the amount supplied by the supply pump 5 and the auxiliary pump 14, control is performed to reduce the amount supplied by the pump 1.

此の共同作用に依ってポンプの油の漏洩の上昇分が補償
されるのみならず同時に斜板の作動角度が中立位置に向
けて復帰する結果，圧力の上昇は供給量の減少により制
御される。This synergy not only compensates for the increase in oil leakage from the pump, but also simultaneously returns the swash plate operating angle to the neutral position, so that the pressure increase is controlled by reducing the supply amount. .

圧力の上昇速度は簡単な方法で、供給ポンプ５と補助ポ
ンプの供給量が相互に調和されることに依り調節される
ことができる。The rate of pressure rise can be adjusted in a simple manner by coordinating the feed rates of the feed pump 5 and the auxiliary pump.

例えば供給ポンプ５は所定の回転数では一定の供給量を
吐出すことができる。For example, the supply pump 5 can deliver a constant supply amount at a predetermined rotation speed.

主ポンプは此の場合高回転速度高圧力負荷においても圧
力上昇がおだやかに増大するように作動する。In this case, the main pump operates in such a way that the pressure rise increases slowly even at high rotational speeds and high pressure loads.

ポンプ１の斜板は普通は供給量零の中立状態に保持され
、このことは斜板に調節に作用するばねにより得られる
。The swash plate of the pump 1 is normally held in a neutral state with zero supply, this being achieved by a spring acting on the swash plate for adjustment.

斜板の作動位置はポンプが導管２に圧力を生じない中立
位置に向けて戻されるように構成されている。The operating position of the swash plate is such that the pump is returned towards a neutral position in which no pressure is created in the conduit 2.

低圧導管３の中の圧力が降下すると同導管の中に液体が
外部調節シリンダー１３からのみでなく内部調節シリン
ダー８からも逆止弁１８を介して供給されることができ
る。If the pressure in the low-pressure line 3 drops, liquid can be supplied into this line not only from the external regulating cylinder 13 but also from the internal regulating cylinder 8 via the check valve 18 .

補助ポンプが設けられていない第２図に示された実施例
に於では調節シリンダー１３のケーシングは機械的調節
装置２１と固く結合されている。In the embodiment shown in FIG. 2, in which no auxiliary pump is provided, the housing of the adjusting cylinder 13 is rigidly connected to the mechanical adjusting device 21.

ポンプ１は一方向にのみ供給する。Pump 1 supplies only in one direction.

調節シリンダー１３は此の場合機械的調節千段２１の中
の中間部材の働きをする。The adjusting cylinder 13 in this case serves as an intermediate member in the mechanical adjusting stage 21.

調節シリンダー１３の底側は逆止弁１６を介して低圧導
管３に接続されるとともに調節絞り２２及び逆止弁１１
を介して供給ポンプ５の吐出側とサーボ切換弁１０とを
接続する管路に常に結合されている。The bottom side of the regulating cylinder 13 is connected to the low pressure conduit 3 via a check valve 16, and is also connected to the regulating throttle 22 and the check valve 11.
The servo switching valve 10 is always connected to a pipe line connecting the discharge side of the supply pump 5 and the servo switching valve 10 via the servo switching valve 10.

ポンプが機械的負荷の増大により回転中に急激な圧力の
上昇が生じてポンプの液体漏洩を生じ低圧導管の圧力が
低下すると調節シリンダー１３の液体が逆市弁１６を介
して低圧導管３の中に一時に放出される。When the pump is rotating due to an increase in mechanical load, a sudden pressure increase occurs, which causes liquid leakage in the pump and the pressure in the low-pressure line decreases, causing the liquid in the regulating cylinder 13 to flow through the reverse valve 16 into the low-pressure line 3. released at once.

調節シリンダー１３の制御室の圧力低下により調節レバ
ー１２が動かされて上記の方法でポンプ１の供給量が低
減される。The pressure drop in the control chamber of the regulating cylinder 13 causes the regulating lever 12 to be actuated to reduce the supply rate of the pump 1 in the manner described above.

供給ポンプ５による逆止弁７を介して高圧導管２への液
体補給によって底圧導管３の圧力が所定の圧力に保持で
きる程度になると、逆止弁１６が閉じて調節シリンダー
１３の側からの液体供給が不必要になる。When the pressure in the bottom pressure conduit 3 reaches a predetermined level by replenishing liquid to the high pressure conduit 2 via the check valve 7 by the supply pump 5, the check valve 16 closes and the pressure from the regulating cylinder 13 is removed. Liquid supply becomes unnecessary.

このとき調節シリンダー１３には第１図の例では補助ポ
ンプ１４から、第２図の例では供給ポンプ５から逆止弁
１１を介して液体が流入する。At this time, liquid flows into the regulating cylinder 13 from the auxiliary pump 14 in the example shown in FIG. 1, and from the supply pump 5 in the example shown in FIG. 2 via the check valve 11.

調節シリンダー１３の液体流入によりピストンがばね１
１に抗して押圧され、調節レバー１２が上記と逆に図の
左方へ動かされるのでサーボ切換弁１０は上記と逆に切
換えられ内部調節シリンダー８のピストンロツドが突出
されポンプ１の斜板を供給状態に移動させポンプ１の供
給量かもとの状態へと増大する。Due to the inflow of liquid into the adjusting cylinder 13, the piston is moved by the spring 1.
1, and the adjustment lever 12 is moved to the left in the figure in the opposite direction to the above, so the servo switching valve 10 is switched in the opposite direction to the above, and the piston rod of the internal adjustment cylinder 8 is protruded and the swash plate of the pump 1 is moved. The supply amount of the pump 1 is increased to the original state.

本装置の始動時には第１図の例では補助ポンプ１４より
の液体が零位置にある調節シリンダー１３のピストンを
押圧することにより、第２図の例では機械的調節千段２
２により調節シリンダー１３を零位置から動かすことに
より中立位置にあるポンプ１を供給状態へと切換えてい
く。When starting up this device, the liquid from the auxiliary pump 14 in the example of FIG.
2, by moving the regulating cylinder 13 from the zero position, the pump 1 in the neutral position is switched to the supply state.

圧力の上昇速度は既知の方法でサーボ制御される全ての
ポンプに於で、サーボ切換弁１０の前の流入絞に依って
制限され、同切換弁も調節できる様に構成されている。In all pumps which are servo-controlled in a known manner, the rate of pressure rise is limited by an inlet restriction in front of the servo-switching valve 10, which is also arranged to be adjustable.

此の様な装置は作動中の此の構造の駆動装置に於でも後
で組込むユニットとして簡単に組込むことができる。Such a device can be easily installed as a later unit in a drive of this construction during operation.

本発明の実施状態を述べれば以下の如くである。The state of implementation of the present invention is as follows.

（１）サーボ調節装置１０が外部調節シリンダー１３に
枢着された設置レバー１２を備え内部調節シリンダー８
が同様に逆止弁１８を介して低圧導管３と結合されてい
ることを特徴とする内部油圧サーボ調節手段を有する特
許請求の範囲第１項又は第２項に記載の緩衝装置。(1) The servo adjustment device 10 includes an installation lever 12 pivotally connected to an external adjustment cylinder 13 and an internal adjustment cylinder 8.
3. A damping device according to claim 1, further comprising internal hydraulic servo-adjustment means, characterized in that the low-pressure line (3) is also connected via a check valve (18) to the low-pressure line (3).

（２）調節シリンダー１３がはね７を備え、同ばねの復
帰力がポンプ１の低圧導管の中の圧力よりごくわずかし
か低くない圧力に一致していることを特徴とする特許請
求の範囲第１項又は第２項及び前項に記載の緩衝装置。(2) The adjusting cylinder 13 is provided with a spring 7 whose restoring force corresponds to a pressure which is only slightly lower than the pressure in the low-pressure conduit of the pump 1 The shock absorbing device according to item 1 or 2 and the preceding item.

（３）調節シリンダー１３のみならず逆止弁１６を介し
て低圧導管３及びサーボ弁１０も外部補助ポンプ１４か
ら供給されることを特徴とする特許請求の範囲第１項又
は第２項及び１項より前項に記載の緩衝装置。(3) not only the regulating cylinder 13 but also the low-pressure line 3 and the servo valve 10 via the check valve 16 are supplied from the external auxiliary pump 14; The shock absorber described in the preceding paragraph.

（４）サーボ弁１０が逆止弁１１を介して補助ポンプ１
４と結合されていることを特徴とする特許請求の範囲第
１項又は第２項に記載の装置。(4) The servo valve 10 connects the auxiliary pump 1 via the check valve 11.
3. Device according to claim 1 or 2, characterized in that it is combined with 4.

（５）調節装置１３が機械的調節装置と固く結合されて
おり調節シリンダー１３の底側か調節絞と逆止弁１１と
を介して供給ポンプ５のサーボ制御圧力側と結合されて
いることを特徴とする特許請求の範囲第１項又は第２項
に記載の緩衝装置。(5) that the regulating device 13 is firmly connected to the mechanical regulating device and to the bottom side of the regulating cylinder 13 or via the regulating throttle and check valve 11 to the servo-controlled pressure side of the feed pump 5; A shock absorbing device according to claim 1 or 2.

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

第１図はアキシャルポンプと補助ポンプの旋回板の内部
サーボ調節手段を有する装置、第２図は補助ポンプを有
しない装置の第１図に相当する図を示したものである。 １……ポンプ、２……高圧（低圧）導管、３……低圧（
高圧）導管、５……供給ポンプ、６……充填圧力安全弁
、γ……逆止弁、８……内部調節シリンダー、１０……
サーボ切換弁、１１……逆止弁、１２……調節レバー、
１３……調節シリンダー、１４……補助ポンプ、１５…
…調節絞り、１６……逆止弁、１８……逆止弁。FIG. 1 shows a device with internal servo adjustment means for the pivot plates of the axial pump and the auxiliary pump, and FIG. 2 shows a view corresponding to FIG. 1 of the device without the auxiliary pump. 1...Pump, 2...High pressure (low pressure) conduit, 3...Low pressure (
High pressure) conduit, 5... Supply pump, 6... Filling pressure safety valve, γ... Check valve, 8... Internal adjustment cylinder, 10...
Servo switching valve, 11...Check valve, 12...Adjustment lever,
13... Adjustment cylinder, 14... Auxiliary pump, 15...
...Adjustment throttle, 16...Check valve, 18...Check valve.

Claims (1)

【特許請求の範囲】 １ 調節可能なアキシャルピストンポンプと、該アキシ
ャルピストンポンプと同じモーターにより駆動される供
給ポンプと、前記アキシャルピストンポンプの内部調節
シリンダーと、該内部調節シリンダーと連結されたサー
ボ切換弁と、該サーボ切換弁と連結された調節シリンダ
ーと、前記アキシャルピストンポンプと接続された低圧
側及び高圧側導管と、前記供給ポンプの吐出口をそれぞ
れ逆止弁７を介してアキシャルピストンポンプの高圧側
導管並びに低圧側導管に接続する導管と、前記供給ポン
プの吐出口に充填圧力安全弁を接続する導管とを備えた
流体静力学的駆動装置において、前記内部調節シリンダ
ー８の複数の室が前記供給ポンプの吐出口と前記サーボ
切換弁１０を介して接続され、そして前記複数の室の１
つが低圧側導管と該低圧側導管の方向に開放している独
立した逆止弁１β，１９を介して接続されており、前記
内部調節シリンダー３から低圧側導管への流体によりア
キシャルピストンポンプの吐出量が減少されることを特
徴とする流体静力学的駆動装置。 ２ 調節可能なアキシャルピストンポンプと、該アキシ
ャルピストンポンプと同じモーターにより駆動される供
給ポンプと、前記アキシャルピストンポンプの内部調節
シリンダーと、該内部調節シリンダーと連結されたサー
ボ切換弁と、該サーボ切換弁と連結された調節シリンダ
ーと、前記アキシャルピストンポンプと接続された低圧
側及び高圧側導管と、前記供給ポンプの吐出口をそれぞ
れ逆止弁Ｔを介してアキシャルピストンポンプの高圧側
導管並びに低圧側導管に接続する導管と、前記供給ポン
プの吐出口に充填圧力安全弁を接続する導管とを備えた
流体静力学的駆動装置において、前記内部調節シリンダ
ー８の１つの室が前記共給ポンプの吐出口と前記サーボ
切換弁１０を介して接続され、調節シリンダー１３の底
側室が低圧側導管３の方に開いた独立した逆止弁１６を
介して低圧側導管３と又供給ポンプ５の吐出口と調節シ
リンダー１３の方に開いた逆止弁１１を介して接続され
ていることを特徴とする流体静力学的駆動装置。Claims: 1. An adjustable axial piston pump, a feed pump driven by the same motor as the axial piston pump, an internal regulating cylinder of the axial piston pump, and a servo-switching device connected to the internal regulating cylinder. A control cylinder connected to the servo switching valve, a low-pressure side and a high-pressure side conduit connected to the axial piston pump, and the discharge port of the supply pump are respectively connected to the axial piston pump through a check valve 7. In a hydrostatic drive with a conduit connecting a high-pressure side conduit as well as a low-pressure side conduit and a conduit connecting a filling pressure relief valve to the outlet of the supply pump, the chambers of the internal regulating cylinder 8 are connected to the connected to the discharge port of the supply pump via the servo switching valve 10, and one of the plurality of chambers.
are connected to the low-pressure side conduit through independent check valves 1β, 19 that are open in the direction of the low-pressure side conduit, and the fluid from the internal regulating cylinder 3 to the low-pressure side conduit causes the discharge of the axial piston pump. Hydrostatic drive device, characterized in that the volume is reduced. 2. an adjustable axial piston pump, a supply pump driven by the same motor as the axial piston pump, an internal regulating cylinder of the axial piston pump, a servo switching valve connected to the internal regulating cylinder, and the servo switching A regulating cylinder connected to a valve, a low-pressure side conduit and a high-pressure side conduit connected to the axial piston pump, and a discharge port of the supply pump connected to the high-pressure side conduit and the low-pressure side of the axial piston pump through a check valve T, respectively. In a hydrostatic drive with a conduit connecting a conduit and a conduit connecting a filling pressure relief valve to the outlet of the feed pump, one chamber of the internal regulating cylinder 8 is connected to the outlet of the cofeed pump. The bottom chamber of the regulating cylinder 13 is connected to the low-pressure conduit 3 and also to the outlet of the supply pump 5 via an independent check valve 16 that opens toward the low-pressure conduit 3. Hydrostatic drive, characterized in that it is connected via a non-return valve 11 which is open towards the regulating cylinder 13.
JP48020288A 1972-02-22 1973-02-21 Hydrostatic drive Expired JPS589301B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US05/442,627 US3942858A (en) 1973-02-16 1974-02-14 Lamp socket
DE19742407516 DE2407516B2 (en) 1973-02-21 1974-02-16 LAMP SOCKET

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2208172A DE2208172C3 (en) 1972-02-22 1972-02-22 Device for damping the load-related pressure increase in hydrostatic drives

Publications (2)

Publication Number Publication Date
JPS48103961A JPS48103961A (en) 1973-12-26
JPS589301B2 true JPS589301B2 (en) 1983-02-19

Family

ID=5836660

Family Applications (1)

Application Number Title Priority Date Filing Date
JP48020288A Expired JPS589301B2 (en) 1972-02-22 1973-02-21 Hydrostatic drive

Country Status (15)

Country Link
US (1) US3854847A (en)
JP (1) JPS589301B2 (en)
AR (1) AR198072A1 (en)
AU (1) AU5230473A (en)
BR (1) BR7301293D0 (en)
CA (1) CA983815A (en)
CH (1) CH561869A5 (en)
CS (1) CS170452B2 (en)
DE (1) DE2208172C3 (en)
ES (1) ES411597A1 (en)
FR (1) FR2173565A5 (en)
GB (1) GB1401374A (en)
IT (1) IT977429B (en)
SU (1) SU466678A3 (en)
ZA (1) ZA731047B (en)

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Also Published As

Publication number Publication date
CS170452B2 (en) 1976-08-27
ES411597A1 (en) 1976-01-01
IT977429B (en) 1974-09-10
SU466678A3 (en) 1975-04-05
CH561869A5 (en) 1975-05-15
US3854847A (en) 1974-12-17
FR2173565A5 (en) 1973-10-05
JPS48103961A (en) 1973-12-26
GB1401374A (en) 1975-07-16
CA983815A (en) 1976-02-17
DE2208172C3 (en) 1974-07-11
AR198072A1 (en) 1974-05-31
DE2208172B2 (en) 1973-12-13
BR7301293D0 (en) 1974-05-16
DE2208172A1 (en) 1973-09-06
AU5230473A (en) 1974-08-22
ZA731047B (en) 1973-11-28

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