CN105275900A - Fluid machine - Google Patents
Fluid machine Download PDFInfo
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- CN105275900A CN105275900A CN201510834477.4A CN201510834477A CN105275900A CN 105275900 A CN105275900 A CN 105275900A CN 201510834477 A CN201510834477 A CN 201510834477A CN 105275900 A CN105275900 A CN 105275900A
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Abstract
The invention relates to the technical field of engineering machines, in particular to a fluid machine. The fluid machine comprises a fluid machine body, a first drive device, a second drive device, a work condition switching device, a first work condition adjusting device and a second work condition adjusting device. The work condition switching device is used for controlling the fluid machine to be switched between a pump work condition and a motor work condition. The first work condition adjusting device is used for enabling the fluid machine to have a pump proportion displacement control function and a pump constant-pressure cut-off control function. The second work condition adjusting device is used for enabling the fluid machine to have a motor proportion displacement control function. The fluid machine can be used as a pump and also as a motor, and has an energy recovery function, multiple control manners such as pump proportion displacement control, pump constant-pressure cut-off control and motor proportion displacement control can be achieved, the structure is simple, and control precision is high.
Description
Technical field
The present invention relates to technical field of engineering machinery, particularly a kind of fluid machinery.
Background technique
In prior art, many engineering machinery are faced with the problem of how energy saving.Such as, the running on wheels such as truck crane and cram packer class engineering machinery, product quantity is large, and oil consumption is high, and it is poor to discharge, and these all cause its power saving urgently to be resolved hurrily.
And by the suitable device of design, to recycle energy be the effective technological means of one solving above-mentioned power saving.
Cam-type axial piston pump and cam-type axial piston motor are fluid machineries conventional in engineering machinery, and because it has, volume is little, lightweight, specific power large, be easy to the advantages such as control, is therefore widely used in various hydraulic system.
Fig. 1-2 shows the working principle of cam-type axial piston pump.Fig. 3-5 shows the working principle of cam-type axial piston motor.As can be seen from Fig. 1-5, cam-type axial piston pump and cam-type axial piston motor include swash plate 1 ', plunger 2 ', cylinder body 3 ', oil distribution casing 4 ' and transmission shaft 5 ', difference is that the direction that the two swash plate 1 ' tilts is contrary, such as, in FIG, the swash plate 1 ' of cam-type axial piston pump deflects δ angle to the left, like this when transmission shaft 5 ' rotates, inlet port b is from fuel tank oil suction, and discharge from force feed mouth a, and in the drawings in 3, the swash plate 1 ' of cam-type axial piston motor deflects β angle to the right, like this when the equidirectional rotation of transmission shaft 5 ', force feed mouth a oil-feed, and discharge from return opening b.
Can find out accordingly, when transmission shaft constant in a kind of rotation direction (left-handed or dextrorotation) and high pressure hydraulic fluid port is constant time, the switching of pump condition and motor operating conditions is realized if want, one end of swash plate can be made to be rocked to the opposite side of zero degree plane by the side of zero degree plane, and zero degree plane herein refers to through swash plate and the intersection point of axis of transmission shaft 5 ' and the plane of the axis perpendicular to transmission shaft 5 '.
But in the prior art, most of cam-type axial piston pump or motor only have corresponding simple function, and namely pump can only realize pumping function, and motor can only realize motor function, and cannot transform between pump condition and motor operating conditions, energy recovery function cannot be realized; Although or also occurred that some can realize the hydraulic element carrying out switching between pump condition and motor operating conditions, but the structure of these hydraulic element existing is general comparatively complicated, cost is higher, and its control effects is also unsatisfactory, such as cannot realize pump proportional displacement control function, motor proportional displacement control function and pump constant voltage cutting-off controlling function simultaneously, thus causing existing this kind of product performance not good, application is subject to larger restriction.Wherein, pump proportional displacement control function refer to can when pump condition the function of proportion adjustment discharge capacity, motor proportional displacement control function refer to can when motor operating conditions the function of proportion adjustment discharge capacity, pump constant voltage cutting-off controlling function refers to when pump condition can the function of the automatic vanishing of discharge capacity after pump discharge pressure reaches setting dangerous pressure value.
Summary of the invention
The present invention aims to provide a kind of fluid machinery, and it can switch between pump condition and motor operating conditions, and can realize pump proportional displacement control function, motor proportional displacement control function and pump constant voltage cutting-off controlling function simultaneously.
To achieve these goals, the invention provides a kind of fluid machinery, it comprises:
Fluid machinery body, the first drive unit, the second drive unit, operating mode COMM communication, the first Working condition regulator and the second Working condition regulator;
Fluid machinery body comprises the first working hole, the second working hole and swash plate, first drive unit is connected to the first end of swash plate and the hydraulic control end of the first drive unit is communicated with the second working hole, and the second drive unit is connected to the second end of swash plate and the hydraulic control end of the second drive unit is connected with operating mode COMM communication;
The hydraulic control end that operating mode COMM communication can control the second drive unit is communicated with the second working hole with in the second oil circuit by the first oil circuit, when the hydraulic control end of the second drive unit is communicated with the second working hole by the first oil circuit, fluid machinery is in pump condition, first working hole oil-feed, second working hole is fuel-displaced, and when the hydraulic control end of the second drive unit is communicated with the second working hole by the second oil circuit, fluid machinery is in motor operating conditions, second working hole oil-feed, the first working hole is fuel-displaced;
First Working condition regulator is arranged on the first oil circuit, and the first Working condition regulator is used for making fluid machinery have pump proportional displacement control function and pump constant voltage cutting-off controlling function;
Second Working condition regulator is arranged on the second oil circuit, and the second Working condition regulator can make fluid machinery have motor proportional displacement control function.
Alternatively, operating mode COMM communication comprises the first selector valve, first selector valve comprises the first hydraulic fluid port, the second hydraulic fluid port and the 3rd hydraulic fluid port, first hydraulic fluid port of the first selector valve is connected with the second Working condition regulator, second hydraulic fluid port of the first selector valve is connected with the first Working condition regulator, and the 3rd hydraulic fluid port of the first selector valve is communicated with the hydraulic control end of the second drive unit; First selector valve has the first working position and the second working position, when the first selector valve is in the first working position the first selector valve first hydraulic fluid port cut-off and the second hydraulic fluid port of the first selector valve be communicated with the 3rd hydraulic fluid port, be communicated with the second working hole by the first oil circuit to make the hydraulic control end of the second drive unit, when the first selector valve is in the second working position, the first hydraulic fluid port of the first selector valve is communicated with the 3rd hydraulic fluid port and the second hydraulic fluid port of the first selector valve ends, and is communicated with by the second oil circuit to make the hydraulic control end of the second drive unit with the second working hole.
Alternatively, the first selector valve is solenoid directional control valve, and the Electromagnetic Control end of the first selector valve switches between the first working position and the second working position for controlling the first selector valve.
Alternatively, first Working condition regulator comprises proportional electromagnetic valve, proportional electromagnetic valve comprises the first hydraulic fluid port, second hydraulic fluid port and the first control end, first hydraulic fluid port of proportional electromagnetic valve is communicated with the second working hole, second hydraulic fluid port of proportional electromagnetic valve is connected with the second hydraulic fluid port of the first selector valve, proportional electromagnetic valve has the first working position, when proportional electromagnetic valve is in the first working position, the first hydraulic fluid port of proportional electromagnetic valve is communicated with the second hydraulic fluid port, first control end of proportional electromagnetic valve can the valve port openings of sizes of proportion adjustment proportional electromagnetic valve when the first working position, to make fluid machinery, there is pump proportional displacement control function.
Alternatively, first Working condition regulator also comprises pressure shut-off valve, second hydraulic fluid port of proportional electromagnetic valve is connected with the second hydraulic fluid port of the first selector valve by pressure shut-off valve, pressure shut-off valve is used for controlling to make swash plate be rocked to zero angle position by the first oil circuit hydraulic fluid pressure entered in the hydraulic control end of the second drive unit when the pressure of the second working hole reaches setting dangerous pressure, has pump constant voltage cutting-off controlling function to make fluid machinery.
Alternatively, pressure shut-off valve comprises the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and control end, first hydraulic fluid port of pressure shut-off valve is communicated with the second working hole, second hydraulic fluid port of pressure shut-off valve is communicated with the second hydraulic fluid port of proportional electromagnetic valve, and the 3rd hydraulic fluid port of pressure shut-off valve is communicated with the second hydraulic fluid port of the first selector valve; Pressure shut-off valve has the first working position and the second working position, when pressure shut-off valve is in the first working position, first hydraulic fluid port of pressure shut-off valve ends and the second hydraulic fluid port of pressure shut-off valve is communicated with the 3rd hydraulic fluid port, when pressure shut-off valve is in the second working position, the first hydraulic fluid port of pressure shut-off valve is communicated with the 3rd hydraulic fluid port and the second hydraulic fluid port of pressure shut-off valve ends; The control end of pressure shut-off valve is communicated with to enable the pressure when the second working hole to reach the setting pressure of pressure shut-off valve during with the second working hole, the control end pilot pressure cut-off valve of pressure shut-off valve switches to the second working position.
Alternatively, the first Working condition regulator also comprises swash plate angular displacement feedback mechanism, and the angular displacement of swash plate when pump condition can be fed back to second control end relative with its first control end of proportional electromagnetic valve by swash plate angular displacement feedback mechanism.
Alternatively, the second control end of proportional electromagnetic valve is provided with the first feedback spring, and the angular displacement of swash plate when pump condition can be converted to the amount of deformation of the first feedback spring by swash plate angular displacement feedback mechanism.
Alternatively, the second Working condition regulator can also make the hydraulic control end of the second drive unit be communicated with fuel tank, has pump maximum pump discharge controlling functions to make fluid machinery.
Alternatively, second Working condition regulator comprises the second selector valve, second selector valve comprises the first hydraulic fluid port, second hydraulic fluid port and the first control end, first hydraulic fluid port of the second selector valve is communicated with the second working hole, second hydraulic fluid port of the second selector valve is communicated with the first hydraulic fluid port of the first selector valve, second selector valve has the first working position, when the second selector valve is in the first working position, the first hydraulic fluid port of the second selector valve is communicated with the second hydraulic fluid port, first control end of the second selector valve can the valve port openings of sizes of proportion adjustment second selector valve when being in the first working position, to make fluid machinery, there is motor proportional displacement control function.
Alternatively, the second selector valve also comprises the 3rd hydraulic fluid port, and the 3rd hydraulic fluid port of the second selector valve is communicated with fuel tank, when the second selector valve is in the first working position, and the 3rd hydraulic fluid port cut-off of the second selector valve; Second selector valve also has the second working position, when the second selector valve is in the second working position the second selector valve first hydraulic fluid port cut-off and the second hydraulic fluid port of the second selector valve be communicated with the 3rd hydraulic fluid port; First control end of the second selector valve can control the second selector valve and switch to the second working position, has pump maximum pump discharge controlling functions to make fluid machinery.
Alternatively, the angular displacement of swash plate when motor operating conditions can also be fed back to second control end relative with its first control end of the second selector valve by swash plate angular displacement feedback mechanism.
Alternatively, the second control end of the second selector valve is provided with the second feedback spring, and the angular displacement of swash plate when motor operating conditions can be converted to the amount of deformation of the second feedback spring by swash plate angular displacement feedback mechanism.
Alternatively, fluid machinery also comprises the first limit stoper, and the first limit stoper is used for cutting off the active force of the second feedback spring to swash plate angular displacement feedback mechanism when pump condition; And/or fluid machinery also comprises the second limit stoper, the second limit stoper is used for cutting off the active force of the first feedback spring to swash plate angular displacement feedback mechanism when motor operating conditions.
Alternatively, first drive unit comprises the first plunger case, the plunger of the first plunger case is connected with the first end of swash plate, the rodless cavity that the hydraulic control end of the first drive unit is arranged on the first plunger case is communicated with the second working hole to make the rodless cavity of the first plunger case, and is provided with Returnning spring in the rodless cavity of the first plunger case; And/or the second drive unit comprises the second plunger case, the plunger of the second plunger case is connected with the second end of swash plate, and the rodless cavity that the hydraulic control end of the second drive unit is arranged on the second plunger case is connected with operating mode COMM communication to make the rodless cavity of the second plunger case.
Fluid machinery provided by the present invention, can either use as pump, can use as motor again, there is energy recovery function, and make fluid machinery have pump proportional displacement control function and pump constant voltage cutting-off controlling function by arranging the first Working condition regulator, make described fluid machinery have motor proportional displacement control function by arranging the second Working condition regulator.In addition, according to the further embodiment of the present invention, the second Working condition regulator of the present invention can also make fluid machinery have pump maximum pump discharge controlling functions.Fluid mechanics of the present invention is simple, and control accuracy is higher.
By being described in detail exemplary embodiment of the present invention referring to accompanying drawing, further feature of the present invention and advantage thereof will become clear.
Accompanying drawing explanation
In order to be illustrated more clearly in the embodiment of the present invention or technological scheme of the prior art, be briefly described to the accompanying drawing used required in embodiment or description of the prior art below, apparently, accompanying drawing in the following describes is only some embodiments of the present invention, for those of ordinary skill in the art, under the prerequisite not paying creative work, other accompanying drawing can also be obtained according to these accompanying drawings.
Fig. 1 illustrates the fundamental diagram of axial piston pump.
Fig. 2 illustrates the A-A sectional view of Fig. 1.
Fig. 3 illustrates the fundamental diagram of axial piston motor.
Fig. 4 illustrates the B-B sectional view of Fig. 3.
Fig. 5 illustrates the C-C sectional view of Fig. 3.
Fig. 6 illustrates the hydraulic schematic diagram of the fluid machinery of one embodiment of the invention.
In figure:
1 ', swash plate; 2 ', plunger; 3 ', cylinder body; 4 ', oil distribution casing; 5 ', transmission shaft;
1, fluid machinery body; 2, the first plunger case; 3, the second plunger case; 4, swash plate angular displacement feedback mechanism; 6, the first selector valve; 7, pressure shut-off valve; 8, proportional electromagnetic valve; 9, the second selector valve; 10, the first limit stoper; 11, the second limit stoper; 801, the first feedback spring; 901, the second feedback spring.
Embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, be clearly and completely described the technological scheme in the embodiment of the present invention, obviously, described embodiment is only the present invention's part embodiment, instead of whole embodiments.Illustrative to the description only actually of at least one exemplary embodiment below, never as any restriction to the present invention and application or use.Based on the embodiment in the present invention, those of ordinary skill in the art, not carrying out the every other embodiment obtained under creative work prerequisite, belong to the scope of protection of the invention.
May not discuss in detail for the known technology of person of ordinary skill in the relevant, method and apparatus, but in the appropriate case, described technology, method and apparatus should be regarded as a part of authorizing specification.
In describing the invention, it will be appreciated that, the noun of locality is if the indicated orientation such as " forward and backward, upper and lower, left and right ", " laterally, vertical, vertical, level " and " top, the end " or position relationship are normally based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, when not doing contrary explanation, these nouns of locality do not indicate and imply that the device of indication or element must have specific orientation or with specific azimuth configuration and operation, therefore can not be interpreted as limiting the scope of the invention; The noun of locality " inside and outside " refers to inside and outside the profile relative to each parts itself.
In describing the invention; it will be appreciated that; the word such as " first ", " second " is used to limit component; be only used to be convenient to distinguish corresponding component; as there is no Stated otherwise; above-mentioned word does not have particular meaning, therefore can not be interpreted as limiting the scope of the invention.
Fig. 6 shows the hydraulic schematic diagram of one embodiment of the invention.With reference to Fig. 6, fluid machinery provided by the present invention, comprises fluid machinery body 1, first drive unit, the second drive unit, operating mode COMM communication, the first Working condition regulator and the second Working condition regulator, wherein:
Fluid machinery body 1 comprises the first working hole S, the second working hole B and swash plate, first drive unit is connected to the first end of swash plate and the hydraulic control end of the first drive unit is communicated with the second working hole B, and the second drive unit is connected to the second end of swash plate and the hydraulic control end of the second drive unit is connected with operating mode COMM communication.
The hydraulic control end that operating mode COMM communication can control the second drive unit is communicated with the second working hole B with in the second oil circuit by the first oil circuit, when the hydraulic control end of the second drive unit is communicated with the second working hole B by the first oil circuit, fluid machinery is in pump condition, first working hole S oil-feed, second working hole B is fuel-displaced, when the hydraulic control end of the second drive unit is communicated with the second working hole B by the second oil circuit, fluid machinery is in motor operating conditions, second working hole B oil-feed, the first working hole S is fuel-displaced.
First Working condition regulator is arranged on the first oil circuit, and this first Working condition regulator is used for making fluid machinery have pump proportional displacement control function and pump constant voltage cutting-off controlling function.
Second Working condition regulator is arranged on the second oil circuit, and this second Working condition regulator can make fluid machinery have motor proportional displacement control function.
Fluid machinery provided by the present invention, can either use as pump, can use as motor again, there is energy recovery function, and make fluid machinery have pump proportional displacement control function and pump constant voltage cutting-off controlling function by arranging the first Working condition regulator, make fluid machinery have motor proportional displacement control function by arranging the second Working condition regulator, thus make fluid machinery function of the present invention more various, more can practical requirement.
In addition, second Working condition regulator of the present invention can also make the hydraulic control end of the second drive unit be communicated with fuel tank, make fluid machinery have pump maximum pump discharge controlling functions further like this, thus fluid machinery of the present invention can be used as energy recovery pump.
Below in conjunction with the embodiment shown in Fig. 6, the present invention is described further.
As shown in Figure 6, in this embodiment, fluid machinery comprise fluid machinery body 1, the first plunger case 2 as the first drive unit, the second plunger case 3 as the second drive unit, as operating mode COMM communication the first selector valve 6, comprise the first Working condition regulator of proportional electromagnetic valve 8 and pressure shut-off valve 7, comprise the second Working condition regulator of the second selector valve 9.In this embodiment, the hydraulic control end of the first drive unit is arranged on the rodless cavity of the first plunger case 2, the hydraulic control end of the second drive unit is arranged on the rodless cavity of the second plunger case 3, first oil circuit is the oil circuit being provided with proportional electromagnetic valve 8 and pressure shut-off valve 7 between the second working hole B and the first selector valve 6, and the second oil circuit is the oil circuit being provided with the second selector valve 9 between the second working hole B and the first selector valve 6.
As shown in Figure 6, in this embodiment, fluid machinery body 1 adopts the structure of cam-type axial piston pump, it comprises the first working hole S, the second working hole B and swash plate, like this without the need to changing basic components such as its housing, plunger, cylinder bodies, structure is simple, and cost is lower.
The plunger of the first plunger case 2 is connected with the first end (being the lower end of swash plate in figure 6) of swash plate, the rodless cavity of the first plunger case 2 is communicated with the second working hole B, and being provided with Returnning spring in the rodless cavity of the first plunger case 2, this Returnning spring is used for applying to make swash plate remain on the active force of initial position to the first end of swash plate.
The plunger of the second plunger case 3 is connected with second end (being the upper end of swash plate in figure 6) of swash plate, and the rodless cavity of this second plunger case 3 is connected with the first selector valve 6.In order to simplified structure and be convenient to control, in this embodiment, the plunger diameter of the second plunger case 3 is greater than the plunger diameter of the first plunger case 2, and the pivot angle that can control swash plate more conveniently by the difference of the hydraulic fluid pressure in the rodless cavity of the rodless cavity of control second plunger case 3 and the first plunger case 2 like this changes.
For convenience, in ensuing description, the limit position that swash plate in Fig. 6 second end swings on the right side of zero degree plane is defined as the first angular orientation, and the limit position that swash plate second end swings on the left of zero degree plane is defined as the second angular orientation, and position when being in zero degree plane by swash plate is defined as zero angle position, zero degree plane herein still refers to intersection point through the drive shaft axis of swash plate and fluid machinery body 1 and the plane perpendicular with drive shaft axis.
In this embodiment, second end of swash plate to be initially on the right side of zero degree plane and to be positioned at the first angular orientation, now be in pump condition and be in pump maximum pump discharge operating mode, first working hole S oil-feed, second working hole B is fuel-displaced, control swash plate when the pressure of the second working hole B reaches setting dangerous pressure and be rocked to zero angle position, then can realize pump constant voltage cutting-off controlling function; Fluid machinery then can be made by the second end controlling swash plate to switch to motor operating conditions by pump condition by being rocked on the right side of zero degree plane on the left of zero degree plane, now the second working hole B oil-feed, the first working hole S is fuel-displaced; And passing ratio regulates the angular displacement of swash plate on the right side of zero degree plane and on the left of zero degree plane, then can realize pump proportional displacement control function and motor proportional displacement control function.
The rodless cavity that first selector valve 6 can control the second plunger case 3 is communicated with the second working hole B with in the second oil circuit by the first oil circuit, when the rodless cavity of the second plunger case 3 is communicated with the second working hole B by the first oil circuit, fluid machinery is in pump condition, first working hole S oil-feed, the second working hole B is fuel-displaced; When the hydraulic control end of the second drive unit is communicated with the second working hole B by the second oil circuit, fluid machinery is in motor operating conditions, and the second working hole B oil-feed, the first working hole S is fuel-displaced.
As shown in Figure 6, this first selector valve 6 comprises the first hydraulic fluid port, the second hydraulic fluid port and the 3rd hydraulic fluid port, wherein, first hydraulic fluid port of the first selector valve 6 is connected with the second selector valve 9, second hydraulic fluid port of the first selector valve 6 is connected with the first Working condition regulator, and the 3rd hydraulic fluid port of the first selector valve 6 is communicated with the rodless cavity of the second plunger case 3; And, first selector valve 6 has the first working position and the second working position, when the first selector valve 6 is in the first working position (the right position namely in Fig. 6), first hydraulic fluid port of the first selector valve 6 ends and the second hydraulic fluid port of the first selector valve 6 is communicated with the 3rd hydraulic fluid port, to enable the rodless cavity of the second plunger case 3 be communicated with the second working hole B by the first oil circuit, and then fluid machinery is made to be in pump condition; When the first selector valve 6 is in the second working position (the left position namely in Fig. 6), first hydraulic fluid port of the first selector valve 6 is communicated with the 3rd hydraulic fluid port and the second hydraulic fluid port of the first selector valve 6 ends, to enable the rodless cavity of the second plunger case 3 be communicated with the second working hole B by the second oil circuit, and then fluid machinery is made to be in motor operating conditions.
Realizing the control mode that the first selector valve 6 switches between the first working position and the second working position has multiple, such as hydraulic control, automatically controlled or Mechanical course, in the embodiment shown in fig. 6, adopt automatically controlled mode, namely in this embodiment, the first selector valve 6 is solenoid directional control valve, it has Electromagnetic Control end Y1, switch between the first working position and the second working position by regulating the turn on angle of Electromagnetic Control end Y1 namely can control the first selector valve 6 like this, simple and convenient, be easy to realize.
In this embodiment, proportional electromagnetic valve 8 regulates the angular displacement of the second end on the right side of zero degree plane carrying out proportion adjustment swash plate via the first oil circuit hydraulic fluid pressure entered in the rodless cavity of the second plunger case 3 for passing ratio, thus realize the proportional control of the discharge capacity of convection cell machinery when pump condition, even if also fluid machinery has pump proportional displacement control function.
As shown in Figure 6, proportional electromagnetic valve 8 comprises the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and the first control end Y2, wherein, first hydraulic fluid port of proportional electromagnetic valve 8 is communicated with the second working hole B, second hydraulic fluid port of proportional electromagnetic valve 8 is connected with the second hydraulic fluid port of the first selector valve 6 by pressure shut-off valve 7, and the 3rd hydraulic fluid port of proportional electromagnetic valve 8 is communicated with fuel tank; Proportional electromagnetic valve 8 has the first working position and the second working position, and when proportional electromagnetic valve 8 is in the first working position (the left position namely in Fig. 6), the first hydraulic fluid port of proportional electromagnetic valve 8 is communicated with the second hydraulic fluid port and the 3rd hydraulic fluid port ends; When proportional electromagnetic valve 8 is in the second working position (the right position namely in Fig. 6), the first hydraulic fluid port of proportional electromagnetic valve 8 ends and the second hydraulic fluid port is communicated with the 3rd hydraulic fluid port; First control end Y2 of proportional electromagnetic valve 8 is used for control ratio solenoid valve 8 and switches between the first working position and the second working position, and passing ratio regulates the turn on angle of this first control end Y2 can the valve port openings of sizes of proportion adjustment proportional electromagnetic valve 8 when the first working position, thus proportion adjustment enters the hydraulic fluid pressure in the rodless cavity of the second plunger case 3 via the first oil circuit, realize the pump proportional displacement control function of fluid machinery.
In order to realize more accurate pump proportional displacement control function, as shown in Figure 6, also be provided with swash plate angular displacement feedback mechanism 4 in this embodiment, and be provided with the first feedback spring 801 at second control end relative with its first control end Y2 of proportional electromagnetic valve 8, wherein, one end of swash plate angular displacement feedback mechanism 4 is connected with the plunger of the second plunger case 3, when the second end of swash plate swings on the right side of zero degree plane, the other end of swash plate angular displacement feedback mechanism 4 can be connected with this first feedback spring 801, thus the angular displacement of swash plate can be converted to the amount of deformation of the first feedback spring 801, also the second control end of proportional electromagnetic valve 8 is fed back to by the angular displacement of swash plate when pump condition, and then the closed loop control formed entering the hydraulic fluid pressure in the rodless cavity of the second plunger case 3 via the first oil circuit that to match with the first control end Y2 of proportional electromagnetic valve 8, the control accuracy of further raising pump proportional displacement control.Certainly, swash plate angular displacement feedback mechanism 4 can also adopt other mode of execution, such as can for the sensor of swash plate angular displacement signal can be gathered, as long as the angular displacement of swash plate when pump condition can be fed back to the second control end of proportional electromagnetic valve 8 to form closed loop control by it.
In this embodiment, pressure shut-off valve 7 for reach at the pressure of the second working hole B setting dangerous pressure time control by the first oil circuit, the hydraulic fluid pressure entered in the rodless cavity of the second plunger case 3 reaches the pressure that swash plate can be driven to be rocked to zero angle position, so just make when pump condition once the pressure of the second working hole B reaches setting dangerous pressure, the flow of fluid machinery just can vanishing automatically, thus realizes the pump constant voltage cutting-off controlling function of fluid machinery.
Particularly, as shown in Figure 6, pressure shut-off valve 7 comprises the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and control end, wherein, first hydraulic fluid port of pressure shut-off valve 7 is communicated with the second working hole B, second hydraulic fluid port of pressure shut-off valve 7 is communicated with the second hydraulic fluid port of proportional electromagnetic valve 8, and the 3rd hydraulic fluid port of pressure shut-off valve 7 is communicated with the second hydraulic fluid port of the first selector valve 6, pressure shut-off valve 7 has the first working position and the second working position, when pressure shut-off valve 7 is in the first working position (the right position namely in Fig. 6), first hydraulic fluid port of pressure shut-off valve 7 ends and the second hydraulic fluid port of pressure shut-off valve 7 is communicated with the 3rd hydraulic fluid port, such second actuator port B can the first working position of passing ratio solenoid valve 8, first working position of pressure shut-off valve 7 and the first working position of the first selector valve 6 are communicated with the rodless cavity of the second plunger case 3, now passing ratio regulates the turn on angle of the first control end Y2 of proportional electromagnetic valve 8 just can realize pump proportional displacement control function, and when pressure shut-off valve 7 is in the second working position (the left position namely in Fig. 6), first hydraulic fluid port of pressure shut-off valve 7 is communicated with the 3rd hydraulic fluid port and the second hydraulic fluid port of pressure shut-off valve 7 ends, and such second actuator port B can be communicated with the rodless cavity of the second plunger case 3 by the second working position of pressure shut-off valve 7 and the first working position of the first selector valve 6, the control end of pressure shut-off valve 7 is communicated with the second working hole B, like this when the pressure of the second working hole B reaches the setting pressure of pressure shut-off valve 7, the control end of pressure shut-off valve 7 then can switch to the second working position by pilot pressure cut-off valve 7, and after pressure shut-off valve 7 switches to the second working position, the hydraulic fluid pressure entered in the rodless cavity of the second plunger case 3 can promote swash plate and be rocked to zero angle position, thus realizes pump constant voltage cutting-off controlling function.
In this embodiment, second selector valve 9 one aspect can regulate the angular displacement of the second end on the left of zero degree plane carrying out proportion adjustment swash plate via the second oil circuit hydraulic fluid pressure entered in the rodless cavity of the second plunger case 3 by passing ratio, thus realizes the motor proportional displacement control function of fluid machinery; On the other hand, the second selector valve 9 can also be communicated with by making the rodless cavity of the second plunger case 3 the pump maximum pump discharge controlling functions realizing fluid machinery with fuel tank by drain tap L.For convenience, the operating mode that these two kinds are regulated by the second selector valve 9 is referred to as pump motor operating conditions, also namely when pump motor operating conditions, the maximum pump discharge function of pump can be realized, motor proportional displacement control function can be realized again.
Particularly, as shown in Figure 6, second selector valve 9 comprises the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and the first control end Y3, first hydraulic fluid port of the second selector valve 9 is communicated with the second working hole B, second hydraulic fluid port of the second selector valve 9 is communicated with the first hydraulic fluid port of the first selector valve 6, and the 3rd hydraulic fluid port of the second selector valve 9 is communicated with fuel tank, first control end Y3 of the second selector valve 9 can control the second selector valve 9 and switch between the first working position and the second working position, when the second selector valve 9 is in the first working position (the left position namely in Fig. 6), first hydraulic fluid port of the second selector valve 9 is communicated with the second hydraulic fluid port and the 3rd hydraulic fluid port cut-off, when the first selector valve 6 switches to the second working position simultaneously, second working hole B can be communicated with the rodless cavity of the second plunger case 3 by the first working position of the second selector valve 9 and the second working position of the first selector valve 6, so the second plunger case 3 can drive the second end of swash plate to be rocked on the left of zero degree plane, thus make fluid machinery switch to motor operating conditions, and when the second selector valve 9 is in the second working position (the right position namely in Fig. 6), first hydraulic fluid port of the second selector valve 9 ends and the second hydraulic fluid port is communicated with the 3rd hydraulic fluid port, the rodless cavity of such second plunger case 3 can be communicated with fuel tank by the second working position of the first selector valve 6 and the second working position of the second selector valve 9, by the hydraulic oil earial drainage in the rodless cavity of the second plunger case 3 to fuel tank, thus the swash plate that makes removing the 3 pairs of swash plates applyings of the second plunger case leaves the active force of the first angular orientation, so swash plate is in the first angular orientation under the effect of the first plunger case 2, and then realize pump maximum pump discharge controlling functions, in addition, first control end Y3 of the second selector valve 9 can the valve port openings of sizes of proportion adjustment second selector valve 9 when being in the first working position, also namely this first control end Y3 can enter hydraulic fluid pressure in the rodless cavity of the second plunger case 3 by proportion adjustment via the second oil circuit, so the second plunger case 3 can the angular displacement of the second end on the left of zero degree plane of proportion adjustment swash plate, thus the discharge capacity of proportion adjustment fluid machinery when motor operating conditions, realize the motor proportional displacement control function of fluid machinery.
Like pump proportional displacement control function class, in order to improve the control accuracy of motor proportional displacement control function further, in this embodiment, the angular displacement of swash plate when motor operating conditions can also be fed back to second control end relative with its first control end Y3 of the second selector valve 9 by swash plate angular displacement feedback control strategies 4.As shown in Figure 6, second control end of the second selector valve 9 is provided with the second feedback spring 901, when the second end of swash plate is rocked on the left of zero degree plane, swash plate angular displacement feedback mechanism 4 can be connected with the second feedback spring 901, thus the angular displacement of swash plate when motor operating conditions is fed back to the second control end of the second selector valve 9 by the amount of deformation that swash plate angular displacement is now converted to the second feedback spring 901.Based on this, first control end Y3 of the second selector valve 9 coordinates the closed loop control that can be formed entering the hydraulic fluid pressure in the rodless cavity of the second plunger case 3 via the second oil circuit with the second feedback spring 901, thus makes the proportional control of the discharge capacity of convection cell machinery when motor operating conditions more accurate.
In this embodiment, the first control end Y3 of the second selector valve 9 is electric proportional control end, can regulate the turn on angle of the first control end Y3 like this according to the amount of deformation of the second feedback spring 901, and then realizes the more accurate proportional control of motor operating conditions discharge capacity.
In addition, the fluid machinery of this embodiment also comprises the first limit stoper 10 and the second limit stoper 11, wherein, first limit stoper 10 is for cutting off the active force of the second feedback spring 901 pairs of swash plate angular displacement feedback mechanisms 4 when pump condition, with the degree of regulation avoiding the second feedback spring 901 when pump condition to affect proportional electromagnetic valve 8 pairs of discharge capacities, second limit stoper 11 is then for cutting off the active force of the first feedback spring 801 pairs of swash plate angular displacement feedback mechanisms 4 when motor operating conditions, with the degree of regulation avoiding the first feedback spring 801 when motor operating conditions to affect the second selector valve 9 pairs of discharge capacities.Visible, by arranging the first limit stoper 10 and the second limit stoper 11, the proportional displacement control function of pump condition and motor operating conditions is independent of one another, thus can avoid mutual interference therebetween, further raising degree of regulation, ensures the functional reliability of fluid machinery of the present invention.
Based on the oil hydraulic circuit shown in Fig. 6, the working principle of fluid machinery of the present invention is as follows:
(1) when fluid machinery inputs without rotating speed, input without hydraulic oil in the rodless cavity of the second plunger case 3, it is 0 that the plunger of the second plunger case 3 stretches out displacement, although also input without pressure oil in the first plunger case 2 rodless cavity, but owing to being provided with Returnning spring in the first plunger case 2 rodless cavity, therefore, the plunger of the first plunger case 2 can stretch out and make swash plate be in the first angular orientation under the effect of Returnning spring, and now fluid machinery is in the displacement of pump condition.
(2) giving tacit consent to operating mode is pump condition, under this operating mode, can realize pump proportional displacement control function and pump constant voltage cutting-off controlling function.Specific implementation process is as follows: the first control end Y1 dead electricity of the first selector valve 6, first selector valve 6 is in the first working position, and pressure shut-off valve 7 and proportional electromagnetic valve 8 are all in the first working position, now give fluid machinery input speed, oil in fuel tank enters fluid machinery body 1 from the first working hole S, and flow out from the second working hole B, and be divided into three tunnels from the hydraulic oil that the second working hole B flows out, the first via exports actuator to, second tunnel enters the rodless cavity of the first plunger case 2, apply to make swash plate remain on the active force of the first angular orientation to the first end of swash plate together with the Returnning spring in the first plunger case 2 rodless cavity, first working position of the 3rd tunnel then passing ratio solenoid valve 8, first working position of pressure shut-off valve 7 and the first working position of the first selector valve 6 arrive the rodless cavity of the second plunger case 3, active force is applied to the second end of swash plate, after the difference of the hydraulic oil active force in the hydraulic oil active force in the second plunger case 3 rodless cavity and the first plunger case 2 rodless cavity reaches certain value, second plunger case 3 just can promote swash plate and be swung to zero angle position by the first angular orientation, reduce pump delivery gradually, in the process, first limit stoper 10 cuts off the active force of the second feedback spring 901 pairs of swash plate angular displacement feedback mechanisms 4, so the angular displacement of swash plate between the first angular orientation to zero angle position is only converted to the amount of deformation of the first feedback spring 801 by swash plate angular displacement feedback mechanism 4, and the turn on angle of the first control end Y2 of proportional electromagnetic valve 8 is regulated according to this ratio feedback signal, just can more adequately proportion adjustment proportional electromagnetic valve 8 in the valve port openings of sizes of the first working position, thus more adequately can enter the hydraulic fluid pressure in the second plunger case 3 rodless cavity via the first oil circuit by proportion adjustment, so the second plunger case 3 can the angular displacement of the second end on the right side of zero degree plane of proportion adjustment swash plate, the discharge capacity being exported to the first via hydraulic oil of actuator by the second working hole B is made to be that ratio changes, realize the pump proportional displacement control function of fluid machinery, and when the pressure of the second working hole B reaches dangerous setting pressure, pressure shut-off valve 7 switches to the second working position, from the 3rd road hydraulic oil no longer passing ratio solenoid valve 8 that the second working hole B flows out, but the rodless cavity of the second plunger case 3 is directly arrived by the second working position of pressure shut-off valve 7 and the first working position of the first selector valve 8, so the second plunger case 3 drives swash plate to be rocked to zero angle position, fluid machinery no longer output flow to actuator, realize pump constant voltage cutting-off controlling function, prevent overload, improve the job security of fluid machinery.
(3) pump motor operating conditions, under this operating mode, can realize motor proportional displacement control function and pump maximum pump discharge controlling functions.Specific implementation process is as follows: the first control end Y1 of the first selector valve 6 obtains electric, the first selector valve 8 is made to switch to the second working position, and the first control end Y3 dead electricity of the second selector valve 9, the second selector valve 9 is made to be in the second working position, hydraulic oil in the rodless cavity of then the second plunger case 3 is communicated with fuel tank by the second working position of the first selector valve 6 and the second working position of the second selector valve 9, by the hydraulic oil earial drainage in the second plunger case 3 rodless cavity to fuel tank, the piston rod of the second plunger case 3 is regained completely, swash plate is in the first angular orientation all the time under the effect of the first plunger case 2, fluid machinery is made to be in pump maximum pump discharge working state in this case all the time, thus make fluid machinery have pump maximum pump discharge controlling functions, can be used as energy recovery pump to use, and when the first control end Y1 of the first selector valve 6 obtains electric, when first selector valve 8 switches to the second working position, if the first control end Y3 of the second selector valve 9 also electric, control the second selector valve 9 and switch to the first working position, then the second working hole B enters in the rodless cavity of the second plunger case 3 by the first working position of the second selector valve 9 and the second working position of the first selector valve 6, second plunger case 3 drives the second end of swash plate to be rocked on the left of zero degree plane, fluid machinery is made to switch to motor operating conditions by pump condition, now hydraulic oil enters fluid machinery body 1 from the second working hole B, and flow out from the first working hole S, in the process, second limit stoper 11 cuts off the active force of the first feedback spring 801 pairs of swash plate angular displacement feedback mechanisms 4, so the angular displacement of the second end on the left of zero degree plane of swash plate is only converted to the amount of deformation of the second feedback spring 901 by swash plate angular displacement feedback mechanism 4, and the turn on angle of the first control end Y3 of the second selector valve 9 is regulated according to this ratio feedback signal, just can more adequately proportion adjustment second selector valve 9 in the valve port openings of sizes of the first working position, thus more adequately can enter the hydraulic fluid pressure in the second plunger case 3 rodless cavity via the second oil circuit by proportion adjustment, so the second plunger case 3 can the angular displacement of the second end on the left of zero degree plane of proportion adjustment swash plate, the discharge capacity of fluid machinery when motor operating conditions is made to be ratio change, realize the motor proportional displacement control function of fluid machinery.
To sum up, the present invention is based on the body of common cam-type axial piston pump, by setting up selector valve, proportional electromagnetic valve, swash plate angular displacement feedback mechanism etc., make fluid machinery not only have pumping function and motor function simultaneously, and by the design to inner control logic, achieve the Variable Control of the several functions such as pump proportional displacement control function, motor proportional displacement control function and pump constant voltage cutting-off controlling function, and do not interfere with each other each other, control accuracy is high, and structure is simple, and cost is lower.
This fluid machinery can be applied to Brake energy recovery hydraulic system or other potential energy (or inertia energy) energy-recuperation system of road running class vehicle or construction machinery product, effectively solves the power saving of these engineering machinery.
These are only exemplary embodiment of the present invention, not in order to limit the present invention, within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (15)
1. a fluid machinery, is characterized in that, comprising:
Fluid machinery body (1), the first drive unit, the second drive unit, operating mode COMM communication, the first Working condition regulator and the second Working condition regulator;
Described fluid machinery body (1) comprises the first working hole (S), the second working hole (B) and swash plate, described first drive unit is connected to the first end of described swash plate and the hydraulic control end of described first drive unit is communicated with described second working hole (B), and described second drive unit is connected to the second end of described swash plate and the hydraulic control end of described second drive unit is connected with described operating mode COMM communication;
The hydraulic control end that described operating mode COMM communication can control described second drive unit is communicated with described second working hole (B) with in the second oil circuit by the first oil circuit, when the hydraulic control end of described second drive unit is communicated with described second working hole (B) by described first oil circuit, described fluid machinery is in pump condition, the oil-feed of described first working hole (S), described second working hole (B) is fuel-displaced, when the hydraulic control end of described second drive unit is communicated with described second working hole (B) by described second oil circuit, described fluid machinery is in motor operating conditions, the oil-feed of described second working hole (B), described first working hole (S) is fuel-displaced,
Described first Working condition regulator is arranged on described first oil circuit, and described first Working condition regulator is used for making described fluid machinery have pump proportional displacement control function and pump constant voltage cutting-off controlling function;
Described second Working condition regulator is arranged on described second oil circuit, and described second Working condition regulator can make described fluid machinery have motor proportional displacement control function.
2. fluid machinery according to claim 1, it is characterized in that, described operating mode COMM communication comprises the first selector valve (6), described first selector valve (6) comprises the first hydraulic fluid port, the second hydraulic fluid port and the 3rd hydraulic fluid port, first hydraulic fluid port of described first selector valve (6) is connected with described second Working condition regulator, second hydraulic fluid port of described first selector valve (6) is connected with described first Working condition regulator, and the 3rd hydraulic fluid port of described first selector valve (6) is communicated with the hydraulic control end of described second drive unit, described first selector valve (6) has the first working position and the second working position, first hydraulic fluid port of the first selector valve (6) described in when described first selector valve (6) is in the first working position ends and the second hydraulic fluid port of described first selector valve (6) is communicated with the 3rd hydraulic fluid port, be communicated with described second working hole (B) by described first oil circuit to make the hydraulic control end of described second drive unit, first hydraulic fluid port of the first selector valve (6) described in when described first selector valve (6) is in the second working position is communicated with the 3rd hydraulic fluid port and the second hydraulic fluid port of described first selector valve (6) ends, be communicated with described second working hole (B) by described second oil circuit to make the hydraulic control end of described second drive unit.
3. fluid machinery according to claim 2, it is characterized in that, described first selector valve (6) is solenoid directional control valve, and the Electromagnetic Control end (Y1) of described first selector valve (6) switches between the first working position and the second working position for controlling described first selector valve (6).
4. fluid machinery according to claim 2, it is characterized in that, described first Working condition regulator comprises proportional electromagnetic valve (8), described proportional electromagnetic valve (8) comprises the first hydraulic fluid port, second hydraulic fluid port and the first control end (Y2), first hydraulic fluid port of described proportional electromagnetic valve (8) is communicated with described second working hole (B), second hydraulic fluid port of described proportional electromagnetic valve (8) is connected with the second hydraulic fluid port of described first selector valve (6), described proportional electromagnetic valve (8) has the first working position, when described proportional electromagnetic valve (8) is in the first working position, the first hydraulic fluid port of described proportional electromagnetic valve (8) is communicated with the second hydraulic fluid port, first control end (Y2) of described proportional electromagnetic valve (8) can the valve port openings of sizes of proportional electromagnetic valve (8) when the first working position described in proportion adjustment, to make described fluid machinery, there is pump proportional displacement control function.
5. fluid machinery according to claim 4, it is characterized in that, described first Working condition regulator also comprises pressure shut-off valve (7), second hydraulic fluid port of described proportional electromagnetic valve (8) is connected with the second hydraulic fluid port of described first selector valve (6) by described pressure shut-off valve (7), control to make described swash plate be rocked to zero angle position by the described first oil circuit hydraulic fluid pressure entered in the hydraulic control end of described second drive unit described pressure shut-off valve (7) is for reaching setting dangerous pressure during at the pressure of described second working hole (B), to make described fluid machinery, there is pump constant voltage cutting-off controlling function.
6. fluid machinery according to claim 5, it is characterized in that, described pressure shut-off valve (7) comprises the first hydraulic fluid port, the second hydraulic fluid port, the 3rd hydraulic fluid port and control end, first hydraulic fluid port of described pressure shut-off valve (7) is communicated with described second working hole (B), second hydraulic fluid port of described pressure shut-off valve (7) is communicated with the second hydraulic fluid port of described proportional electromagnetic valve (8), and the 3rd hydraulic fluid port of described pressure shut-off valve (7) is communicated with the second hydraulic fluid port of described first selector valve (6); Described pressure shut-off valve (7) has the first working position and the second working position, when described pressure shut-off valve (7) is in the first working position, first hydraulic fluid port of described pressure shut-off valve (7) ends and the second hydraulic fluid port of described pressure shut-off valve (7) is communicated with the 3rd hydraulic fluid port, when described pressure shut-off valve (7) is in the second working position, the first hydraulic fluid port of described pressure shut-off valve (7) is communicated with the 3rd hydraulic fluid port and the second hydraulic fluid port of described pressure shut-off valve (7) ends; The control end of described pressure shut-off valve (7) is communicated with to enable the pressure when described second working hole (B) to reach the setting pressure of described pressure shut-off valve (7) during with described second working hole (B), the control end of described pressure shut-off valve (7) controls described pressure shut-off valve (7) and switches to the second working position.
7. fluid machinery according to claim 4, it is characterized in that, described first Working condition regulator also comprises swash plate angular displacement feedback mechanism (4), and the angular displacement of described swash plate when described pump condition can be fed back to second control end relative with its first control end (Y2) of described proportional electromagnetic valve (8) by described swash plate angular displacement feedback mechanism (4).
8. fluid machinery according to claim 7, it is characterized in that, second control end of described proportional electromagnetic valve (8) is provided with the first feedback spring (801), and the angular displacement of described swash plate when described pump condition can be converted to the amount of deformation of described first feedback spring (801) by described swash plate angular displacement feedback mechanism (4).
9. fluid machinery according to claim 1, is characterized in that, described second Working condition regulator can also make the hydraulic control end of described second drive unit be communicated with fuel tank, has pump maximum pump discharge controlling functions to make described fluid machinery.
10. according to the arbitrary described fluid machinery of claim 2-9, it is characterized in that, described second Working condition regulator comprises the second selector valve (9), described second selector valve (9) comprises the first hydraulic fluid port, second hydraulic fluid port and the first control end (Y3), first hydraulic fluid port of described second selector valve (9) is communicated with described second working hole (B), second hydraulic fluid port of described second selector valve (9) is communicated with the first hydraulic fluid port of described first selector valve (6), described second selector valve (9) has the first working position, described in when described second selector valve (9) is in the first working position, the first hydraulic fluid port of the second selector valve (9) is communicated with the second hydraulic fluid port, first control end (Y3) of described second selector valve (9) can the valve port openings of sizes of the second selector valve (9) described in proportion adjustment when being in the first working position, to make described fluid machinery, there is motor proportional displacement control function.
11. fluid machineries according to claim 10, it is characterized in that, described second selector valve (9) also comprises the 3rd hydraulic fluid port, 3rd hydraulic fluid port of described second selector valve (9) is communicated with fuel tank, when described second selector valve (9) is in the first working position, the 3rd hydraulic fluid port cut-off of described second selector valve (9); Described second selector valve (9) also has the second working position, and the first hydraulic fluid port of the second selector valve (9) described in when described second selector valve (9) is in the second working position ends and the second hydraulic fluid port of described second selector valve (9) is communicated with the 3rd hydraulic fluid port; First control end (Y3) of described second selector valve (9) can control described second selector valve (9) and switch to the second working position, has pump maximum pump discharge controlling functions to make described fluid machinery.
12. fluid machineries according to claim 11, it is characterized in that, when claim 10 quotes claim 7 or 8, the angular displacement of described swash plate when described motor operating conditions can also be fed back to second control end relative with its first control end (Y3) of described second selector valve (9) by described swash plate angular displacement feedback mechanism (4).
13. fluid machineries according to claim 12, it is characterized in that, second control end of described second selector valve (9) is provided with the second feedback spring (901), and the angular displacement of described swash plate when described motor operating conditions can be converted to the amount of deformation of described second feedback spring (901) by described swash plate angular displacement feedback mechanism (4).
14. fluid machineries according to claim 13, it is characterized in that, when claim 10 quotes claim 8, described fluid machinery also comprises the first limit stoper (10), and described first limit stoper (10) is for cutting off the active force of described second feedback spring (901) to described swash plate angular displacement feedback mechanism (4) when described pump condition; And/or, described fluid machinery also comprises the second limit stoper (11), and described second limit stoper (11) is for cutting off the active force of described first feedback spring (801) to described swash plate angular displacement feedback mechanism (4) when described motor operating conditions.
15. according to the arbitrary described fluid machinery of claim 1-9, it is characterized in that, described first drive unit comprises the first plunger case (2), the plunger of described first plunger case (2) is connected with the first end of described swash plate, the rodless cavity that the hydraulic control end of described first drive unit is arranged on described first plunger case (2) is communicated with described second working hole (B) to make the rodless cavity of described first plunger case (2), and is provided with Returnning spring in the rodless cavity of described first plunger case (2); And/or, described second drive unit comprises the second plunger case (3), the described plunger of the second plunger case (3) is connected with the second end of described swash plate, and the rodless cavity that the hydraulic control end of described second drive unit is arranged on described second plunger case (3) is connected with described operating mode COMM communication to make the rodless cavity of described second plunger case (3).
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| CN201510834477.4A CN105275900B (en) | 2015-11-26 | 2015-11-26 | Fluid machine |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106194680A (en) * | 2016-08-28 | 2016-12-07 | 中航力源液压股份有限公司 | The axial plunger pump installation of a kind of high accuracy electric proportional control and control method |
| CN106762506A (en) * | 2016-12-15 | 2017-05-31 | 徐州重型机械有限公司 | A kind of control valve and open hydraulic pump that can realize bidirectional variable |
| CN108533545A (en) * | 2018-06-29 | 2018-09-14 | 潍柴动力股份有限公司 | Hydraulic variable displacement pump mechanical proportional controller and hydraulic variable displacement pump |
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| CN1737408A (en) * | 2004-08-16 | 2006-02-22 | 伊顿公司 | Hydraulic kicker control piston |
| US20110146259A1 (en) * | 2009-12-17 | 2011-06-23 | Wolfgang Bauer | Hydraulic system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106194680A (en) * | 2016-08-28 | 2016-12-07 | 中航力源液压股份有限公司 | The axial plunger pump installation of a kind of high accuracy electric proportional control and control method |
| CN106194680B (en) * | 2016-08-28 | 2018-02-06 | 中航力源液压股份有限公司 | The axial plunger pump installation and control method of a kind of high-precision electric proportional control |
| CN106762506A (en) * | 2016-12-15 | 2017-05-31 | 徐州重型机械有限公司 | A kind of control valve and open hydraulic pump that can realize bidirectional variable |
| CN106762506B (en) * | 2016-12-15 | 2018-10-02 | 徐州重型机械有限公司 | A kind of control valve that can realize bidirectional variable and open hydraulic pump |
| CN108533545A (en) * | 2018-06-29 | 2018-09-14 | 潍柴动力股份有限公司 | Hydraulic variable displacement pump mechanical proportional controller and hydraulic variable displacement pump |
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| CN105275900B (en) | 2017-05-24 |
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