TWI608172B - Hydraulic drive - Google Patents
Hydraulic drive Download PDFInfo
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- TWI608172B TWI608172B TW100147245A TW100147245A TWI608172B TW I608172 B TWI608172 B TW I608172B TW 100147245 A TW100147245 A TW 100147245A TW 100147245 A TW100147245 A TW 100147245A TW I608172 B TWI608172 B TW I608172B
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- pump
- pressure
- torque
- hydraulic
- stroke volume
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Classifications
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- 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
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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- 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
- F04B49/06—Control using electricity
- F04B49/065—Control using electricity and making use of computers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
- F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
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- 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
- F04B2203/00—Motor parameters
- F04B2203/02—Motor parameters of rotating electric motors
- F04B2203/0207—Torque
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- 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
- F04B2205/00—Fluid parameters
- F04B2205/06—Pressure in a (hydraulic) circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
- F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/26—Power control functions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6655—Power control, e.g. combined pressure and flow rate control
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Computer Hardware Design (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Reciprocating Pumps (AREA)
Description
本發明關於申請專利範圍第1項引文的一種油壓耗能器用的油壓驅動器。 The invention relates to a hydraulic actuator for a hydraulic consumer according to the first reference of the patent application.
依EP 1387 090 A2有一種習知之此類油壓驅動器,它設有一轉速可變的電馬達,它在此情形中驅動二個恆速泵。至少一泵依實際上的耗能器壓力而定啟動/關掉,其中泵宜用較大的行程體積選擇性地切換轉動。用此方式,該馬達驅動器設計成力矩較小。 According to EP 1 387 090 A2, there is a known hydraulic drive of this type which is provided with a variable speed electric motor which in this case drives two constant speed pumps. At least one pump is activated/turned off depending on the actual kerometer pressure, wherein the pump preferably selectively switches rotation with a larger stroke volume. In this way, the motor drive is designed to have a low torque.
EP 0 805 922 B1發表了一種飛機用的油壓泵控制系統,它使用一排擠體積(行程體積)可變的油壓泵,該泵被一轉速可變的馬達驅動。在此,馬達轉速調整成使它在系統要求減少時,其減少速率小於當系統要求加大時它的提高速率。這表示,例如在要求壓力遞減時,泵的行程體積先減少,而當要求壓力提高時,馬達轉速先提高。 EP 0 805 922 B1 discloses a hydraulic pump control system for aircraft which uses a hydraulic pump with a variable displacement (stroke volume) which is driven by a variable speed motor. Here, the motor speed is adjusted such that when the system requirements are reduced, the rate of decrease is less than the rate at which the system increases as the system requirements increase. This means that, for example, when the pressure is required to decrease, the stroke volume of the pump is first reduced, and when the required pressure is increased, the motor speed is first increased.
另一先前技術為EP 404 286 B1,其中同樣提到一電油壓驅動單元,此驅動單元使用一可用轉速可變方式操作的電馬達以驅動一調整泵。在此,調整泵利用一彈簧調整到一具最大行程體積的位置,如果油壓系統內的壓力升高到超過一定壓力值,則它由此位置向最小行程體積方向調整。 Another prior art is EP 404 286 B1, in which an electric oil pressure drive unit is also mentioned, which uses an electric motor that can be operated in a variable speed manner to drive an adjustment pump. Here, the adjustment pump is adjusted to a position with a maximum stroke volume by means of a spring, and if the pressure in the oil pressure system rises above a certain pressure value, it is adjusted in this direction to the direction of the minimum stroke volume.
US 6,048,177揭示了一種油壓系統,其泵係用一內燃機驅動者。 US 6,048,177 discloses an oil pressure system in which the pump is driven by an internal combustion engine.
最後,DE 10 2007 007 005 A1發表了一種電油壓控制裝置,具有一行程體積可變泵,它被一轉速可變之電馬達驅動,為了控制泵,設有一個二點調節器,它將泵切換到一最大或最小運送位置,而且相對於一壓力臨限值之高過及低於該值狀態而定切換。 Finally, DE 10 2007 007 005 A1 discloses an electric oil pressure control device having a variable displacement pump which is driven by a variable speed electric motor. To control the pump, a two-point regulator is provided. The pump switches to a maximum or minimum transport position and is switched relative to a pressure threshold that is above and below this value.
由上述先前技術著手,本發明的目的在提供一種油壓系統用的油壓驅動器,它至少由一行程體積可變(可變行程體積)的壓力媒源(油壓泵)及一轉速可變的驅動馬達構成,其中此驅動器比習知技術有更好的性質。其一目的為使油壓驅動器成本低廉。另一個目的為減少調節技術的成本。最後本發明的一目的為依「尺寸減少」(downsizing)原理特別是將驅動馬達的功率減少,而不會危及其下游之油壓系統的功能安全性。 Starting from the above prior art, an object of the present invention is to provide a hydraulic actuator for a hydraulic system which is at least a variable medium (variable stroke volume) pressure medium (hydraulic pump) and a variable speed The drive motor is constructed in which the drive has better properties than the prior art. One purpose is to make the hydraulic drive cost-effective. Another purpose is to reduce the cost of conditioning technology. Finally, it is an object of the present invention to reduce the power of the drive motor, particularly by the "downsizing" principle, without compromising the functional safety of the downstream hydraulic system.
此目的利用具有申請專利範圍第1項特點的油壓驅動器達成,本發明有利之其他特點見於申請專利範圍附屬項。 This object is achieved by a hydraulic actuator having the features of claim 1 of the patent application, and other advantageous features of the invention are found in the dependent claims.
依此,本發明關於一種油壓驅動器,用於一油壓耗能器或一油壓系統,具有一個行程體積可變的泵,將泵與一轉速可變的驅動馬達呈機械方式耦合;及一控制手段,以調整泵的行程體積,依本發明,泵依力矩調節。 Accordingly, the present invention relates to a hydraulic actuator for a hydraulic consuming or hydraulic system having a variable stroke volume pump for mechanically coupling a pump to a variable speed drive motor; A control means for adjusting the stroke volume of the pump, according to the invention, the pump is adjusted according to the torque.
換言之,要驅動器泵,不得超過一定之力矩,只要一力矩(它由系統壓力乘行程體積的乘積得到,我們稱它是泵每轉一圈所需之壓力媒量)即使在最大行程體時仍在此一定力矩之下,則力矩不必調節。如果一壓力(它由負荷測定,或在加速過程及在負載時可在止擋部利用一壓力閥預設)高到使壓力乘行程體積的乘積達到此預設值,則泵向轉小之行程體積方向調整,壓力乘行程體積的乘積至少保持近乎恆定。 In other words, the drive pump must not exceed a certain torque, as long as a torque (which is obtained by multiplying the system pressure by the stroke volume, we call it the pressure medium required for each revolution of the pump) even at the maximum stroke Below this certain torque, the torque does not have to be adjusted. If a pressure (which is measured by the load, or can be preset at the stop with a pressure valve during the acceleration process and during the load) is such that the product of the pressure multiplied by the stroke volume reaches this preset value, the pump turns to small The stroke volume direction is adjusted and the product of the pressure multiplied stroke volume remains at least constant.
在此情形可使用具較小之最大力矩的驅動馬達,如此驅動器整個較廉價,且其操作由於馬達之功率需求減少,故較經濟。 In this case it is possible to drive the motor with a smaller maximum torque, so that the drive is less expensive overall and its operation is less economical due to the reduced power requirements of the motor.
「力矩檢出及/或測定裝置」一詞,此處指該裝置適合回授到驅動馬達之實際力矩負荷。舉例而言,此裝置可為一力矩感測器,它放在驅動馬達或其出力軸上,或為一電流測量裝置,它測量馬達實際上消耗電流量並由此測定其輸出力矩。也可將泵下游的油壓系統中的實際壓力檢出並將行程體積控制或調節而作調整,使預設之最大力矩不會被超過。 The term "torque detection and/or measuring device" is used herein to refer to the actual torque load that the device is suitable for feeding back to the drive motor. For example, the device can be a torque sensor placed on the drive motor or its output shaft, or a current measuring device that measures the amount of current actually consumed by the motor and thereby determines its output torque. It is also possible to detect the actual pressure in the oil pressure system downstream of the pump and adjust or adjust the stroke volume so that the preset maximum torque is not exceeded.
特佳的方式中,「力矩檢出及/或測定裝置」為一種「調整泵」習知的力矩調節器,其中一「調節閥」的一閥活塞沿一調節方向受到一彈簧力(它預設最大力矩)而沿另一方向受另一力(它由一個受泵壓力的活塞作用到一槓桿上的作用點(此點和行程體積有關)產生。 In a particularly preferred manner, the "torque detection and/or measuring device" is a conventionally-adjusted torque regulator in which a valve piston of a "regulating valve" receives a spring force in an adjustment direction (it is pre- The maximum torque is set and in the other direction is generated by another force (which is caused by a piston of the pump pressure acting on a lever (this point is related to the stroke volume).
驅動馬達為轉速可變者,如果依此將泵的行程體積減 少,以限制馬達所需之力矩,則這點會使得一個或數個耗能器(例如一往復缸)的油壓造成之運動變慢。如果我們要維持此運動,則當泵行程體積減少時此驅動馬達的轉速就可提高,如此,由回樞轉之泵產生之體積流依轉速而定再提高,而不會使輸出力矩增加。 The drive motor is variable in speed, if the stroke volume of the pump is reduced accordingly Less, to limit the torque required by the motor, this will slow the movement caused by the oil pressure of one or several energy consuming devices (such as a reciprocating cylinder). If we want to maintain this movement, the speed of the drive motor can be increased when the stroke volume of the pump is reduced. Thus, the volume flow generated by the pump that is pivoted back is increased according to the rotational speed without increasing the output torque.
但如果壓力提高時油壓耗能器在一止擋部只得到一壓力,則驅動馬達的轉速不提高甚至反而減少。 However, if the hydraulic consumer receives only one pressure at a stop when the pressure is increased, the rotational speed of the drive motor does not increase or even decrease.
藉著將壓力媒源直接/間接依轉速調節,馬達的功率消耗可保持在一大致(彷彿)恆定的值以下,因此馬達就其最大可能的功率輸出可設計成較小。 By adjusting the pressure medium directly/indirectly according to the rotational speed, the power consumption of the motor can be kept below a substantially (as if) constant value, so that the motor can be designed to be smaller in its maximum possible power output.
本發明在以下利用一較佳實施例配合附圖詳細說明。 The invention will be described in detail below with reference to the drawings in a preferred embodiment.
依附圖1,左邊係一習知之油壓驅動器,它用二個獨立驅動的恆定泵,各泵被一本身(可為轉速可變)的馬達驅動。此構造較繁複且成本較高,此外空間要求大,因此這種解決方案不經濟。圖1中間為同樣習知之油壓驅動器的改良。此驅動器同樣使用二個恆定泵,但它們被單一馬達共同驅動。其中一恆定馬達可經一閥(此處為一2/2切換閥,具有一開放及一堵塞位置)選擇性地直接切換到一油槽,如此該泵由下游之油壓系統取出,用此方式可將馬達解除負荷。 According to Figure 1, the left side is a conventional hydraulic actuator which uses two independently driven constant pumps, each driven by a motor which is itself variable (variable speed). This configuration is cumbersome and costly, and in addition to the large space requirements, this solution is not economical. The middle of Figure 1 is an improvement of the same conventional hydraulic actuator. This drive also uses two constant pumps, but they are driven together by a single motor. One of the constant motors can be selectively switched directly to an oil sump via a valve (here a 2/2 switching valve with an open and a blocked position) so that the pump is removed by the downstream hydraulic system. The motor can be unloaded.
而此圖右邊為本發明的一油壓驅動器(1)。 The right side of the figure is a hydraulic actuator (1) of the present invention.
依此只設單一泵(2),設計成行程體積可變。舉例而言, 泵(2)可做成傾斜盤泵,其傾斜盤斜度可連續式或分段式改變,泵(2)的檢出端接到一油壓系統(4),例如由一「動作閥」(6)構成,利用它將一耗能器(8)(此處為一活塞缸單元)動作。 According to this, only a single pump (2) is provided, which is designed to have a variable stroke volume. For example, The pump (2) can be made into a swash plate pump, the slanting plate inclination can be changed continuously or in sections, and the detection end of the pump (2) is connected to a hydraulic system (4), for example, by an "action valve". (6) The configuration utilizes an energy consuming device (8) (here a piston cylinder unit).
此單一之行程體積可變的泵(2)由單一(宜為轉速可變)的驅動馬達(10)(例如一電馬達)驅動,該馬達經一驅動軸與泵(2)作機械式耦合。 The single stroke variable volume pump (2) is driven by a single (preferably variable speed) drive motor (10) (eg an electric motor) that is mechanically coupled to the pump (2) via a drive shaft .
最後,設有一控制單元(11)以控制驅動馬達(10),至少一力矩感測器及另一感測器〔用於檢出泵(2)之實際調整的行程體積(傾斜盤斜度)〕接到該控制單元(全部感測器未圖示)。在此,控制單元(11)係程式化或可程式化成使油壓驅動器(1)產生成一可預定(可輸入)的耗能器壓力或系統壓力以及維持此壓力。 Finally, a control unit (11) is provided to control the drive motor (10), at least one torque sensor and another sensor (for detecting the actual adjusted stroke volume of the pump (2) (inclination disc inclination) 〕 is connected to the control unit (all sensors are not shown). Here, the control unit (11) is programmed or programmable to cause the hydraulic actuator (1) to generate a predetermined (inputtable) consuming or system pressure and to maintain this pressure.
依本發明建構成一具較小功率驅動馬達(10),它可使最大出力矩很小,因此當達到此最大輸出力矩時或已在其大時(例如當油壓系統中壓力上升時)該行程體積可變的泵(2)移回,換言之其運送容量減少,如此驅動馬達(10)之實際輸出力矩減少,用此方式,泵(2)或其行程體積調整成不受下游之油壓系統的壓力狀態影響地,該馬達(10)的實際輸出力矩不會超出一最大力矩值或保持在其下方,在有利的情形,輸出力矩可保持大致恆定。換言之,它滿足此式:P×V=常數=T According to the invention, a smaller power drive motor (10) is constructed which allows the maximum output torque to be small, so when this maximum output torque is reached or when it is already large (for example, when the pressure in the hydraulic system rises) The variable volume pump (2) is moved back, in other words, its transport capacity is reduced, so that the actual output torque of the drive motor (10) is reduced. In this way, the pump (2) or its stroke volume is adjusted to be unaffected by the downstream oil. The pressure state of the pressure system affects the ground, the actual output torque of the motor (10) does not exceed or remain below a maximum torque value, and in an advantageous case, the output torque can remain substantially constant. In other words, it satisfies this formula: P × V = constant = T
其中:P 油壓系統中之實際壓力 Where: actual pressure in the P hydraulic system
V 泵的實際行程體積 Actual stroke volume of the V pump
T 馬達的實際出力力矩。 The actual output torque of the T motor.
如果泵(2)的運送容量用此方式回移,則結果使耗能器上的油壓壓力下降,或耗油器受油壓動作的運動變慢。為了避免這點,依本發明的一較佳實施例可視需要將驅動馬達(10)變成轉速可變者,因此當泵(2)運送容量減少時,馬達(10)轉速可升高以維持輸出力矩恆定,以保持所需之實際之耗能器壓力或耗能器運動速度。 If the transport capacity of the pump (2) is moved back in this manner, the hydraulic pressure on the damper is lowered, or the sump is slowed by the hydraulic action. In order to avoid this, according to a preferred embodiment of the present invention, the drive motor (10) can be changed to a variable speed as needed, so that when the pump (2) has a reduced transport capacity, the motor (10) can be rotated to maintain the output. The torque is constant to maintain the actual consuming energy or kinetic energy speed required.
關於這種壓力媒源或行程體積可變的泵(2)的控制可參考圖2的管路圖,它顯示本發明的壓力媒泵的一示圖。圖中,在一殼體(12)中有油壓驅動器,它具有一圓筒轉鼓(40)、一驅動軸(22)、一傾斜盤(43)、一外樞轉活塞(75)(它圍成一調整室(101):在外樞轉活塞(75)止的一回復彈簧(85)、及一內樞轉活塞(76)〔它圍成一調整室(102)〕殼體(12)內有一高壓通道(103)及一低壓(或吸取)通道(104)。調整室(101)經一通道(105)長期與一高壓通道(103)連接。一調節閥(80)建構到殼體(12)上,調節閥由一「力矩調節部分閥」(106)及一「壓力調節部分閥」(107)構成,後者在靜止位置時經一第一輸入端及其「調節輸出端」將力矩調節部分閥(106)的一調節輸出端接通到一控制管路(108),控制管路通到「內樞轉活塞」(76)的調整室(102)。壓力調節部分閥(107)的第二輸入端與高壓通道(103)連接。同樣,力矩調節部分閥(106)之一輸入端與高壓通道(103)連接,而此力矩調節部分閥(106)之一第二輸入端對殼體(12)內部(它具有槽壓力)開 放。壓力調節部分閥(107)之一「調節活塞」受高壓管路(103)的壓力作用,使傾斜盤(43)的樞轉角度減少,且受一可調之彈簧沿相反方向施力。 Regarding the control of such a pressure medium or a variable stroke pump (2), reference may be made to the piping diagram of Fig. 2, which shows a diagram of the pressure medium pump of the present invention. In the figure, there is a hydraulic actuator in a casing (12) having a cylinder drum (40), a drive shaft (22), a swash plate (43), and an outer pivot piston (75) (it Enclosing an adjustment chamber (101): a return spring (85) stopping at the outer pivoting piston (75), and an inner pivoting piston (76) (which encloses an adjustment chamber (102)) housing (12) There is a high pressure channel (103) and a low pressure (or suction) channel (104). The adjustment chamber (101) is connected to a high pressure channel (103) for a long time via a channel (105). A regulating valve (80) is constructed to the housing. (12) The regulating valve is composed of a "torque adjusting part valve" (106) and a "pressure regulating part valve" (107), which in a rest position passes through a first input end and its "regulated output end" A regulating output of the torque regulating portion valve (106) is connected to a control line (108), and the control line leads to an adjustment chamber (102) of the "internal pivoting piston" (76). The pressure regulating portion valve (107) The second input end is connected to the high pressure passage (103). Similarly, one input end of the torque adjustment portion valve (106) is connected to the high pressure passage (103), and the second input end of one of the torque adjustment portion valves (106) To the inside of the housing (12) Pressure groove) open put. One of the pressure regulating portion valves (107) "adjusting the piston" is subjected to the pressure of the high pressure line (103) to reduce the pivoting angle of the swash plate (43) and is biased in the opposite direction by an adjustable spring.
在閥(80)的殼體(95)中支承著一支雙臂槓桿(115),其一槓桿臂上嵌著一活塞(116),活塞在一回移元件的殼體中導進,且經由通道(105)、調整室(101)和外樞轉活塞(75)中的孔(92)供以高壓通道(103)中的壓力,嵌合點的距離隨傾斜盤(43)的樞轉角度改變。槓桿(115)另一臂位於力矩調節部分閥(106)之一調節活塞的一端以及一可調整的彈簧(17)間,彈簧(117)至少大致對立地嵌合在槓桿臂上,此外,力矩調節部分閥(106)的調節活塞向槓桿臂的方向被一可調的彈簧(118)施力,彈簧(117)與彈簧(118)〔它比彈簧(117)調成更弱〕在槓桿(115)上沿一方向產生一固定的力矩,通道(103)中的高壓利用活塞(116)在槓桿(115)上的作用面積產生一力矩,它和上述固定力矩抗拮,且舉外樞轉活塞(75)的位置或一般與傾斜盤(43)的樞轉角度有關。在一所予壓力時,只有在一定之樞轉角度時,由二彈簧產生的力矩才會保持平衡。當壓力改變破壞了平衡,則力矩調節部分閥(106)的閥活塞由其調節位置移出,因此壓力媒可流到調整室(102)或由調整室(102)流出,直到達到另一樞轉角度為止(在此樞轉角度時,槓桿(115)上的力矩再達平衡)。 A two-arm lever (115) is supported in the housing (95) of the valve (80), a piston (116) is embedded in a lever arm, and the piston is guided in a housing of the reversing element, and The pressure in the high pressure passage (103) is supplied via the passage (105), the adjustment chamber (101) and the hole (92) in the outer pivot piston (75), and the distance of the fitting point is pivoted with the swash plate (43). The angle changes. The other arm of the lever (115) is located between one end of the adjustment piston (106) adjusting the piston and an adjustable spring (117), the spring (117) being at least substantially oppositely fitted on the lever arm, in addition, the moment The adjustment piston of the adjustment portion valve (106) is biased toward the lever arm by an adjustable spring (118) which is in contact with the spring (118) which is weaker than the spring (117). 115) a fixed moment is generated in one direction of the upper edge, and the high pressure in the passage (103) generates a moment by the action area of the piston (116) on the lever (115), which is resistant to the above fixed torque and externally pivoted The position of the piston (75) is generally related to the pivoting angle of the swashplate (43). At a given pressure, the torque generated by the two springs will remain balanced only at a certain pivot angle. When the pressure change breaks the balance, the valve piston of the torque adjustment portion valve (106) is moved out of its adjustment position, so that the pressure medium can flow to the adjustment chamber (102) or flow out of the adjustment chamber (102) until another pivot is reached. Up to the angle (at this pivoting angle, the torque on the lever (115) is again balanced).
因此如果油壓系統壓力提高,因此管路(103)中壓力提高,則依圖2,力矩調節部分閥(106)的閥活塞被向右拉,如此系統壓力經管路(108)作用到「內樞轉活塞」(76)。它因 此將此傾斜盤(43)的斜度減少,直到在槓桿臂(115)的力矩平衡為止,因此要由馬達輸出到軸(22)的驅動力矩可保持恆定。 Therefore, if the pressure of the hydraulic system is increased, the pressure in the pipeline (103) is increased, and according to Fig. 2, the valve piston of the torque regulating portion valve (106) is pulled to the right, so that the system pressure acts through the pipeline (108) to the inside. Pivot the piston" (76). It This reduces the inclination of the swash plate (43) until the torque of the lever arm (115) is balanced, so that the driving torque to be output from the motor to the shaft (22) can be kept constant.
(1)‧‧‧油壓驅動器 (1)‧‧‧Hydraulic drive
(2)‧‧‧泵 (2) ‧‧ ‧ pump
(4)‧‧‧油壓系統 (4) ‧‧‧Hydraulic system
(8)‧‧‧耗能器 (8) ‧‧‧ energy consuming devices
(10)‧‧‧驅動馬達 (10)‧‧‧Drive motor
(12)‧‧‧殼體 (12) ‧‧‧Shell
(22)‧‧‧驅動軸 (22)‧‧‧Drive shaft
(40)‧‧‧圓筒轉鼓 (40) ‧‧‧Cylinder Drum
(43)‧‧‧傾斜盤 (43)‧‧‧Sloping disk
(75)‧‧‧外樞轉活塞 (75) ‧‧‧ external pivoting piston
(76)‧‧‧內樞轉活塞 (76) ‧‧‧ pivoting piston
(80)‧‧‧調節閥 (80)‧‧‧Regulators
(85)‧‧‧回復彈簧 (85)‧‧‧Return spring
(92)‧‧‧孔 (92) ‧‧‧ holes
(95)‧‧‧殼體 (95) ‧‧‧Shell
(101)‧‧‧調整室 (101) ‧ ‧ adjustment room
(102)‧‧‧調整室 (102) ‧ ‧ adjustment room
(103)‧‧‧高壓通道 (103)‧‧‧High-pressure passage
(104)‧‧‧低壓(吸取)通道 (104)‧‧‧Low pressure (suction) channel
(105)‧‧‧通道 (105) ‧‧‧ channels
(106)‧‧‧力矩調節部分閥 (106)‧‧‧Torque adjustment part valve
(107)‧‧‧壓力調節部分閥 (107)‧‧‧Pressure regulating part valve
(108)‧‧‧控制管路 (108)‧‧‧Control lines
(115)‧‧‧雙臂槓桿 (115) ‧ ‧ arms lever
(116)‧‧‧活塞 (116) ‧‧‧Pistons
(117)‧‧‧彈簧 (117) ‧ ‧ spring
(118)‧‧‧彈簧 (118) ‧ ‧ spring
圖1顯示之對立位置為:--一依先前技術之一油壓驅動器,具有小行程體積的二個個別驅動的泵;--一依先前技術的一油壓驅動器,具一永久或及一可切換的恆定泵;--一依本發明一較佳實施例的一油壓驅動器,具一受力矩控制之行程體積可變的泵及一轉速可變的驅動器。 Figure 1 shows the opposite position: - one hydraulic drive according to the prior art, two individually driven pumps with a small stroke volume; - a hydraulic drive according to the prior art, with a permanent or a A switchable constant pump; a hydraulic actuator according to a preferred embodiment of the present invention, having a torque-controlled variable stroke volume pump and a variable speed drive.
圖2係依本發明之一壓力媒源(特別行程體積可變的泵)用的油壓調整/控制手段。 Figure 2 is a hydraulic pressure adjustment/control means for a pressure medium (a pump having a variable stroke volume) according to the present invention.
(12)‧‧‧殼體 (12) ‧‧‧Shell
(22)‧‧‧驅動軸 (22)‧‧‧Drive shaft
(40)‧‧‧圓筒轉鼓 (40) ‧‧‧Cylinder Drum
(43)‧‧‧傾斜盤 (43)‧‧‧Sloping disk
(75)‧‧‧外樞轉活塞 (75) ‧‧‧ external pivoting piston
(76)‧‧‧內樞轉活塞 (76) ‧‧‧ pivoting piston
(80)‧‧‧調節閥 (80)‧‧‧Regulators
(85)‧‧‧回復彈簧 (85)‧‧‧Return spring
(92)‧‧‧孔 (92) ‧‧‧ holes
(95)‧‧‧殼體 (95) ‧‧‧Shell
(101)‧‧‧調整室 (101) ‧ ‧ adjustment room
(102)‧‧‧調整室 (102) ‧ ‧ adjustment room
(103)‧‧‧高壓通道 (103)‧‧‧High-pressure passage
(104)‧‧‧低壓(吸取)通道 (104)‧‧‧Low pressure (suction) channel
(105)‧‧‧通道 (105) ‧‧‧ channels
(106)‧‧‧力矩調節部分閥 (106)‧‧‧Torque adjustment part valve
(107)‧‧‧壓力調節部分閥 (107)‧‧‧Pressure regulating part valve
(108)‧‧‧控制管路 (108)‧‧‧Control lines
(115)‧‧‧雙臂槓桿 (115) ‧ ‧ arms lever
(116)‧‧‧活塞 (116) ‧‧‧Pistons
(117)‧‧‧彈簧 (117) ‧ ‧ spring
(118)‧‧‧彈簧 (118) ‧ ‧ spring
Claims (1)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102010055864 | 2010-12-22 | ||
DE102011108285A DE102011108285A1 (en) | 2010-12-22 | 2011-07-21 | Hydraulic drive |
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Publication Number | Publication Date |
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TW201239206A TW201239206A (en) | 2012-10-01 |
TWI608172B true TWI608172B (en) | 2017-12-11 |
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TW100147245A TWI608172B (en) | 2010-12-22 | 2011-12-20 | Hydraulic drive |
Country Status (5)
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US (1) | US20130336812A1 (en) |
EP (1) | EP2655895B1 (en) |
DE (1) | DE102011108285A1 (en) |
TW (1) | TWI608172B (en) |
WO (1) | WO2012084093A1 (en) |
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EP2557233B2 (en) * | 2011-08-12 | 2022-06-01 | ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH | Tool with hydraulic drive for civil engineering work |
DE102013224657A1 (en) * | 2013-12-02 | 2015-06-03 | Robert Bosch Gmbh | Hydraulic arrangement |
DE102014009420B4 (en) * | 2014-06-25 | 2023-03-23 | Zf Cv Systems Hannover Gmbh | Compressed air supply system, pneumatic system and method for controlling a compressed air supply system |
DE102020112660A1 (en) * | 2020-05-11 | 2021-11-11 | MOOG Gesellschaft mit beschränkter Haftung | Method for determining a current state of wear of a hydrostatic machine |
DE102021200100A1 (en) * | 2021-01-08 | 2022-07-14 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydraulic gear unit, especially for deep sea applications |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6048177A (en) * | 1995-10-17 | 2000-04-11 | Brueninghaus Hydromatik Gmbh | Output regulation with load sensing |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1911695C3 (en) * | 1969-03-03 | 1975-01-02 | Mannesmann-Meer Ag, 4050 Moenchengladbach | Power controller with pressure cut-off for hydraulic pumps or motors of the axial piston swashplate design |
DE1922145A1 (en) * | 1969-04-25 | 1970-10-29 | Bellows Valvair Kaemper Gmbh | Combination controller |
US3935707A (en) * | 1974-07-22 | 1976-02-03 | General Signal Corporation | Hydraulic control system |
DE3919175A1 (en) * | 1989-06-12 | 1990-12-13 | Hydromatik Gmbh | CONTROL DEVICE FOR AN ADJUSTABLE PUMP |
US5052909A (en) | 1990-01-19 | 1991-10-01 | Cincinnati Milacron Inc. | Energy-conserving injection molding machine |
US5141402A (en) * | 1991-01-29 | 1992-08-25 | Vickers, Incorporated | Power transmission |
GB9119448D0 (en) * | 1991-09-12 | 1991-10-23 | Vickers Systems Ltd | System controls |
JP3707742B2 (en) * | 1994-12-09 | 2005-10-19 | 株式会社小松製作所 | Control device for variable displacement hydraulic pump |
EP0805922B1 (en) | 1995-03-14 | 2001-11-21 | The Boeing Company | Aircraft hydraulic pump control system |
US6748739B1 (en) * | 1999-07-14 | 2004-06-15 | Yuken Kogyo Kabushiki Kaisha | Hydraulic power system |
EP1387090B1 (en) | 2002-08-02 | 2014-04-30 | Bosch Rexroth AG | Hydraulic drive |
DE102007007005B4 (en) | 2007-02-08 | 2021-12-02 | Robert Bosch Gmbh | Electro-hydraulic control arrangement |
JP4424370B2 (en) * | 2007-05-02 | 2010-03-03 | ダイキン工業株式会社 | Hydraulic unit and construction machine having the same |
-
2011
- 2011-07-21 DE DE102011108285A patent/DE102011108285A1/en not_active Ceased
- 2011-11-11 EP EP11784424.1A patent/EP2655895B1/en active Active
- 2011-11-11 US US13/994,845 patent/US20130336812A1/en not_active Abandoned
- 2011-11-11 WO PCT/EP2011/005668 patent/WO2012084093A1/en active Application Filing
- 2011-12-20 TW TW100147245A patent/TWI608172B/en active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6048177A (en) * | 1995-10-17 | 2000-04-11 | Brueninghaus Hydromatik Gmbh | Output regulation with load sensing |
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Publication number | Publication date |
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EP2655895B1 (en) | 2020-01-22 |
US20130336812A1 (en) | 2013-12-19 |
CN103261706A (en) | 2013-08-21 |
TW201239206A (en) | 2012-10-01 |
EP2655895A1 (en) | 2013-10-30 |
WO2012084093A1 (en) | 2012-06-28 |
DE102011108285A1 (en) | 2012-06-28 |
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