CN103477088B - Hydraulic system and operating method - Google Patents
Hydraulic system and operating method Download PDFInfo
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- CN103477088B CN103477088B CN201280019299.4A CN201280019299A CN103477088B CN 103477088 B CN103477088 B CN 103477088B CN 201280019299 A CN201280019299 A CN 201280019299A CN 103477088 B CN103477088 B CN 103477088B
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- pressurized machine
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- subtense angle
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Classifications
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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
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
- F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
- F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
- F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
- F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/01—Absolute values
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
Abstract
A kind of hydraulic system, described hydraulic system comprises: at first subtense angle (23) of the first operate in pressure ranges; And at second subtense angle (24) of the second operate in pressure ranges, the upper limit of described second pressure range is higher than the upper limit of described first pressure range.Described system comprises: for hydraulic fluid being fed to the pump (2) in this system; And for increasing two pressurized machines (10,10 ') of the pressure in described second subtense angle.Described pressurized machine (10,10 ') is the piston super charger with at least two optional pressure ratios.The invention still further relates to the method for operating hydraulic system.
Description
Technical field
The present invention relates to hydraulic system, described hydraulic system at least comprises: at the first subtense angle of the first operate in pressure ranges; And at the second subtense angle of the second operate in pressure ranges, the upper limit of described second pressure range is higher than the upper limit of described first pressure range, described hydraulic system also comprises: pump, and described pump is used for being fed to by hydraulic fluid in described hydraulic system under a first pressure level; And for the pressure in described second subtense angle being increased to the first pressurized machine of the second stress level and being used for the pressure in described second subtense angle to be increased to the second pressurized machine of the second stress level, each pressurized machine includes plunger, and described plunger comprises: the first pressure surface; Second pressure surface; And the 3rd pressure surface, described first pressure surface and described 3rd pressure surface is positioned at the same side of described plunger on the movement direction of described plunger and described second pressure surface is positioned at opposition side, and the wall of described pressurized machine defines: first Room with described first pressure surface; There is the second Room of described second pressure surface; And there is the 3rd Room of described 3rd pressure surface, each room all can be connected to described delivery side of pump with receiving liquid hydraulic fluid, and described second Room and described 3rd Room are also connected to described second subtense angle to be fed to by hydraulic fluid in this second subtense angle.The invention still further relates to the method for operating hydraulic system.
Background technique
Efficiency and low component costs are the key characters of hydraulic system.Many different machines (such as large combustion engine) can comprise several oil hydraulic circuits with different pressures and traffic requirement.This usually means that the several pump of needs is to produce the flow of hydraulic fluid being in different pressures level, which increases the cost of system.Another problem is, the pump that can produce high pressure and high flow capacity usually has poor efficiency.Even if high efficiency pump can be utilized, but they are more expensive.Except comprise there is different pressures requirement several oil hydraulic circuits except, also commonly, a certain oil hydraulic circuit requires different pressures under different operation modes and flow, thus makes system more complicated.
Summary of the invention
The object of the present invention is to provide a kind of hydraulic system of improvement.Be characterised in that according to the characteristics of system of the present invention: in order to provide at least two optional pressure ratios to each pressurized machine, described second pressure surface is greater than described 3rd pressure surface, and described hydraulic system is provided with the gate-controlled switch valve that the flowing for opening and closing between described pump and described first Room of described pressurized machine is communicated with, and described hydraulic system is provided with another gate-controlled switch valve that the flowing for opening and closing between described pump with described 3rd Room is communicated with.Another object of the present invention is a kind of method providing improvement for operating hydraulic system.The characteristic feature of the method is: described method at least comprises the first operator scheme, described first operator scheme comprises the first stage, in this first stage, hydraulic fluid is only introduced in the first Room of described first pressurized machine, with the mobile plunger of this first pressurized machine and the fluid in the second Room of this pressurized machine that pressurizes this fluid is fed to described second subtense angle, and hydraulic fluid is introduced in the second Room of described second pressurized machine, with the plunger of this second pressurized machine mobile, thus move the first Room and the 3rd Room of this second pressurized machine empty, described first operator scheme also comprises second stage, in this second stage, hydraulic fluid is only introduced in described first Room of described second pressurized machine, with the mobile described plunger of this second pressurized machine and the fluid in described second Room of this second pressurized machine that pressurizes and this fluid is fed to described second subtense angle, and hydraulic fluid is introduced in described second Room of described first pressurized machine, with the described plunger of this first pressurized machine mobile, thus move described first Room and the 3rd Room of this first pressurized machine empty, described method also comprises the second operator scheme, described second operator scheme comprises the first stage, in the described first stage of described second operator scheme, in described first Room of hydraulic fluid being introduced described first pressurized machine and described 3rd Room, with the mobile described plunger of this first pressurized machine and the fluid in described second Room of this first pressurized machine that pressurizes and by this fluid to be fed to described second subtense angle higher than the pressure in described first operator scheme, and hydraulic fluid is introduced in described second Room of described second pressurized machine, with the described plunger of this second pressurized machine mobile, thus move described first Room of this second pressurized machine empty and described 3rd Room, described second operator scheme also comprises second stage, in the described second stage of described second operator scheme, in described first Room of hydraulic fluid being introduced described second pressurized machine and described 3rd Room, with the mobile described plunger of this second pressurized machine and the fluid in described second Room of this second pressurized machine that pressurizes and by this fluid to be fed to described second subtense angle higher than the pressure in described first operator scheme, and-hydraulic fluid is introduced in described second Room of described first pressurized machine, with the described plunger of this first pressurized machine mobile, thus move described first Room of this first pressurized machine empty and described 3rd Room.
Hydraulic system according to the present invention at least comprises: at the first subtense angle of the first operate in pressure ranges; And at the second subtense angle of the second operate in pressure ranges.The upper limit of described second pressure range is higher than the upper limit of described first pressure range.Described hydraulic system also comprises: pump, and described pump is used for being fed to by hydraulic fluid in described hydraulic system under a first pressure level; And two pressurized machines, these two pressurized machines are used for the pressure in described second subtense angle to be increased to the second stress level.Described pressurized machine is the piston super charger with at least two optional pressure ratios.
When according to hydraulic system of the present invention, same pump can be used hydraulic fluid to be fed to two and to have in the subtense angle of different pressures requirement.The maximum delivery pressure of pump can require to select according to low-pressure, it reduces the cost of system.Owing to having two pressurized machines of optional pressure ratio, therefore the second subtense angle can be supplied with steady flow at various pressures.
Method according to the present invention relates to the operation of hydraulic system, and described hydraulic system at least comprises: at the first subtense angle of the first operate in pressure ranges; And at the second subtense angle of the second operate in pressure ranges, the upper limit of wherein said second pressure range is higher than the upper limit of described first pressure range.Described method at least comprises the first operator scheme, described first operator scheme comprises the first stage, in the described first stage, hydraulic fluid is introduced in the first Room of the first pressurized machine, with the plunger of this first pressurized machine mobile and the fluid pressurizeed in the second Room of this first pressurized machine and this fluid is fed to described second subtense angle; And hydraulic fluid is introduced in the second Room of the second pressurized machine, with the plunger of this second pressurized machine mobile, thus move the first Room and the 3rd Room of this second pressurized machine empty.Described first operator scheme also comprises second stage, in described second stage, hydraulic fluid is introduced in described first Room of described second pressurized machine, with the mobile described plunger of described second pressurized machine and the fluid in described second Room of the described pressurized machine that pressurizes and described fluid is fed to described second subtense angle; And hydraulic fluid is introduced in described second Room of described first pressurized machine, with the plunger of mobile described first pressurized machine, thus move described first Room and the 3rd Room of empty described first pressurized machine.
In the method according to the invention, the steady flow be under constant voltage can be supplied to described second subtense angle, this is because a plunger in the plunger of described two pressurized machines is all the time for supplying fluid to described second subtense angle, unless described pressurized machine is in bypass mode.The sky stage of moving of described first Room and the 3rd Room can be used for reloading described pressurized machine or for fluid is fed to described second subtense angle from described 3rd Room.
According to the embodiment of the present invention, each pressurized machine of described system includes plunger, and described plunger comprises the first pressure surface, the second pressure surface and the 3rd pressure surface.Described first pressure surface and described 3rd pressure surface are positioned at the same side of this plunger on the movement direction of described plunger.The wall of described pressurized machine defines: first Room with described first pressure surface; There is the second Room of described second pressure surface; And there is the 3rd Room of described 3rd pressure surface.Each room all can be connected to described delivery side of pump with receiving liquid hydraulic fluid.Described second Room and described 3rd Room are also connected to described second subtense angle to be fed to by hydraulic fluid in this second subtense angle.
According to another embodiment of the present invention, the difference of the ratio between the area of the ratio between the area of described first pressure surface and the area of described second pressure surface and the area of described second pressure surface and described 3rd pressure surface is at most 2 percent.By this selection, the motion in the two directions of described plunger can be used for producing the stream be under substantially the same stress level.
According to another embodiment of the present invention, the difference of the ratio between the area of the ratio between the combined area of described first pressure surface and described 3rd pressure surface and the area of described second pressure surface and the area of described second pressure surface and described 3rd pressure surface is at most 2 percent.
According to another embodiment of the present invention, described system comprises the device that the flowing for opening and closing between described pump and described first Room of described pressurized machine is communicated with, and described system comprises the device that the flowing for opening and closing between described pump and described 3rd Room is communicated with.
According to another embodiment of the present invention, described first subtense angle and described second subtense angle comprise the parts of explosive motor.According to another embodiment of the present invention, described first subtense angle comprises the gas exchange valve of described motor, and described second subtense angle comprises the fuel injector of described motor.
According to another embodiment of the present invention, described pump is variable displacement pump.
According to the embodiment of the present invention, described method comprises the second operator scheme.Described second operator scheme comprises the first stage, in the described first stage, in described first Room of hydraulic fluid being introduced described first pressurized machine and described 3rd Room, with the plunger of mobile described first pressurized machine and the fluid pressurizeed in the second Room of described first pressurized machine and by described fluid to be fed to described second subtense angle higher than the pressure in described first operator scheme; And hydraulic fluid is introduced in described second Room of described second pressurized machine, with the described plunger of this second pressurized machine mobile, thus move described first Room of empty described second pressurized machine and described 3rd Room.Described second operator scheme also comprises second stage, in described second stage, in described first Room of hydraulic fluid being introduced described second pressurized machine and described 3rd Room, with the described plunger of mobile described second pressurized machine and the fluid pressurizeed in described second Room of described second pressurized machine and by described fluid to be fed to described second subtense angle higher than the pressure in described first operator scheme, and hydraulic fluid is introduced in described second Room of described first pressurized machine, with the described plunger of mobile described first pressurized machine, thus move described first Room of empty described first pressurized machine and described 3rd Room.
According to another embodiment of the present invention, in described second operator scheme, sky and filling are moved by same pipeline in described 3rd Room.When fluid is not released in storage tank via reflux pipeline, can be recovered by the energy of the fluid storage in described 3rd Room.
Accompanying drawing explanation
Fig. 1 shows hydraulic system according to the embodiment of the present invention.
Fig. 2 a to Fig. 2 e shows the part being in the different phase of work cycle of the system of Fig. 1.
Fig. 3 shows the hydraulic system according to another embodiment of the present invention.
Embodiment
In more detail embodiments of the present invention are described referring now to accompanying drawing.
Hydraulic system has according to the embodiment of the present invention been shown in Fig. 1.This hydraulic system is used for operating the fuel injector of large combustion engine and gas exchange valve, and described large combustion engine is all is used as peculiar to vessel or for producing the main of electric power or auxiliary engine in power station motor in this way.This hydraulic system comprises storage tank 1 for storing hydraulic fluid and for pressurizeing described hydraulic fluid and the pump 2 be fed to by described hydraulic fluid in oil hydraulic circuit.This pump 2 is the variable displacement pumps allowing adjust flux.This system is also provided with the pressure pulsation for reducing in loop and therefore contributes to the first accumulator 4 of the steady pressure in keeping system.Also there is the reduction valve for preventing overvoltage in systems in which.
Gas exchange valve forms the first subtense angle 23 needing first pressure range of 235bar to 350bar.Therefore required flow can be approximately 64l/min.Fuel injector forms the second subtense angle 24 needing second pressure range of 250bar to 700bar.The upper limit of the pressure range needed for the second subtense angle 24 is therefore higher than the upper limit of the pressure range needed for the first subtense angle 23.Mean flowrate required in second subtense angle 24 can be approximate 36l/min.Pump 2 is by the traffic requirement of the pressure requirements and whole hydraulic system of selecting to realize the first subtense angle 23.
In order to increase the pressure of the hydraulic fluid advancing to the second subtense angle 24, this Operation system setting has the first pressurized machine 10 and the second pressurized machine 10 '.Hydraulic fluid advances to the first subtense angle 23 under the delivery pressure of pump 2.Each pressurized machine 10,10 ' includes reciprocating type plunger 11,11 '.The wall of pressurized machine 10,10 ' and plunger 11,11 ' define first Room 12a, 12a ', second Room 12b, 12b ' and the 3rd Room 12c, 12c '.First Room 12a, 12a ' and the 3rd Room 12c, 12c ' is positioned at the same side of plunger 11,11 ' on the movement direction of plunger 11,11 '.Second Room 12b, 12b ' is positioned at opposition side.Each room 12a, 12a ', 12b, 12b ', 12c, 12c ' be provided with for fluid being introduced and drawing fluid port 10a, 10a of described room ', 10b, 10b ', 10c, 10c '.First Room 12a, 12a ' is connected to pump 2 by the first pressure line 18,18 ' being provided with the first switch valve 6,6 '.First Room 12a, 12a ' is also connected to storage tank 1 by the first reflux pipeline 19,19 ' being provided with second switch valve 7,7 '.Second Room 12b, 12b ' is connected to pump 2 by the second pressure line 20,20 ' being provided with the first safety check 13,13 '.3rd Room 12c, 12c ' is connected to pump 2 by the 3rd pressure line 21,21 ' comprising the 3rd switch valve 8,8 '.3rd Room 12c, 12c ' is connected to storage tank 1 by the 3rd reflux pipeline 22,22 '.Pressurized machine 10,10 ' also comprises fourth ventricle 12d, the 12d opposed with first Room 12a, 12a ' '.In mode of execution described here, fourth ventricle 12d, 12d ' be not used in supercharging.But if need more optional pressure ratio, then fourth ventricle 12d, 12d ' also can be provided with pressure line.Leakage line 17,17 ' is by fourth ventricle 12d, 12d ' be connected to storage tank 1.
Second safety check 14,14 ' is arranged in be guided to the pipeline 28,28 ' of fuel injector from second Room 12b, 12b ', and the 3rd safety check 15,15 ' is arranged in and guides to the pipeline 29,29 ' of fuel injector from the 3rd Room 12c, 12c '.4th safety check 16,16 ' is arranged between the 3rd Room 12c, 12c ' and the 3rd switch valve 8,8 '.
Plunger 11,11 ' has three pressure surfaces separated.First pressure surface A1, A1 ' and the fluid contact in first Room 12a, 12a '.Second pressure surface A2, A2 ' and the fluid contact in second Room 12b, 12b ', and the 3rd pressure surface A3, A3 ' and the fluid contact in the 3rd Room 12c, 12c '.The size of pressure surface is selected as making the area of the first pressure surface A1 in manufacturing tolerances, to equal the area of area divided by the 3rd pressure surface A3 of the second pressure surface A2 divided by the area of the second pressure surface A2, that is, A1/A2=A2/A3.Allowance depends on application.In mode of execution described here, the difference of ratio A1/A2 and ratio A2/A3 should be at most 2 percent, is more preferably less than one of percentage, and is most preferably less than percent 0.5.
The working principle of hydraulic system is described in more detail by referring to Fig. 2 a to Fig. 2 e now.
The situation of the plunger 11 that wherein the first pressurized machine 10 is shown in Fig. 2 a upwards (that is, towards second fluid port one 0b) movement.Term " upwards " is only for accompanying drawing here, and real pressurized machine 10 can be arranged to work in any direction.Hydraulic fluid is fed to oil hydraulic circuit from storage tank 1 with constant voltage by pump 2.In this example, pressure is in the scope of 235bar to 350bar.The first switch valve 6 in the pressure line 18 of the first Room 12a is opened, thus allows to flow to pressurized machine 10.Fluid is entered in the first Room 12a of pressurized machine 10 by first fluid port one 0a.The second switch valve 7 be arranged in the reflux pipeline 19 of the first Room 12a keeps cutting out in case fluid flows directly in storage tank 1.And the 3rd Room 12c pressure line 21 in the 3rd switch valve 8 keep close.The 4th switch valve 9 in the reflux pipeline 22 of the 3rd Room 12c be open to allow fluid to be inhaled into the 3rd Room 12c from storage tank 1 thus to fill by the void space formed that moves upward of plunger 11.It should be noted, be different from the mode of execution shown in figure, the fluid source that fluid is supplied to the 3rd Room 12c from it also can be different from storage tank 1.Such as, in explosive motor, fluid source can be the fluid pipe-line be connected with lubricant pump.The hydraulic fluid pressurizeed in first Room 12a upwardly plunger 11.Therefore, the pressure in the second Room 12b increases.Ratio between the pressure of the first Room 12a and the pressure of the second Room 12b and the ratio between the area of the first pressure surface A1 and the area of the second pressure surface A2 are inversely proportional to.In this example, pressure theory rises to the level of 341bar to 508bar.The fluid that first safety check 13 prevents from being under the pressure higher than the pressure produced by pump 2 flows to pump 2.Second safety check 14 allows fluid to flow to fuel injector.
Fig. 2 b shows the situation of wherein plunger 11 (that is, towards the 3rd fluid port 10c) movement downwards.Present first switch valve 6 is closed to prevent from flowing in the pressure line 18 of the first Room 12a.And the 3rd switch valve 8 be closed to prevent from flowing in the pressure line 21 of the 3rd Room 12c.First safety check 13 allows fluid pass through the second pressure line 20 and second fluid port one 0b and flow in the second Room 12b.Fluid in second Room 12b promotes plunger 11 downwards.Second switch valve 7 in the reflux pipeline 19 of the first Room 12a stays open to allow fluid freely to flow into storage tank 1 from the first Room 12a.Therefore the stress level in the first Room 12a is identical with the pressure (that is, external pressure) in storage tank 1.The 4th switch valve 9 in the reflux pipeline 22 of the 3rd Room 12c is closed in case fluid flows into storage tank 1 from the 3rd Room 12c.Therefore fluid in 3rd Room 12c flows to fuel injector by the 3rd safety check 15.4th safety check 16 protects the 3rd switch valve 8 not by the impact of the high pressure of pressurized machine 10.Therefore 3rd switch valve 9 can have maximum allowble pressure lower limit, it reduces the cost of hydraulic system.Because the ratio between the area of the area of the first pressure surface A1 and the second pressure surface A2 equals the ratio between the area of the second pressure surface A2 and the area of the 3rd pressure surface A3, the pressure therefore at fuel injector place is identical with the situation of Fig. 2 a.In Fig. 2 a and Fig. 2 b, pressurized machine 10 works with middle pressure pattern.Under middle pressure pattern, pressurized machine 10,10 ' is as double action booster work, and pressure fluid is fed to system by this double action booster on their two movement directions.
The situation that wherein plunger 11 moves up is shown in Fig. 2 c.The 3rd switch valve 8 in the first switch valve 6 in the pressure line 18 of present first Room 12a and the pressure line 21 of the 3rd Room 12c is opened.Therefore the hydraulic fluid carrying out self-pumping 2 can flow in the first Room 12a and the 3rd Room 12c.The 4th switch valve 9 in the reflux pipeline 22 of the second switch valve 7 in the reflux pipeline 19 of the first Room 12a and the 3rd Room 12c is closed in case fluid flows directly in storage tank 1.Fluid upwardly plunger 11 in first Room 12a and the 3rd Room 12c.Therefore pressure in second Room 12b increase.Ratio between the combined area of pressure increase and the first pressure surface A1 and the 3rd pressure surface A3 and the area of the second pressure surface A2 is proportional.Therefore pressure is higher than pressure when Fig. 2 a and Fig. 2 b, is 503bar to 749bar in this example.First safety check 13 prevents the flowing from the second Room 12b to pump 2, and therefore fluid flows to fuel injector by the second safety check 14.
Fig. 2 d shows the situation that wherein plunger 11 moves down.The 3rd switch valve 8 in the first switch valve 6 in the pressure line 18 of the first Room 12a and the pressure line 21 of the 3rd Room 12c cuts out.Therefore fluid to flow into the second Room 12b from pump 2 and promotes plunger 11 downwards.The 4th switch valve 9 in the reflux pipeline 22 of the second switch valve 7 in the reflux pipeline 19 of the first Room 12a and the 3rd Room stays open, and therefore fluid freely can flow into storage tank 1 from the first Room 12a and the 3rd Room 12c.This is the stage of reloading, and pressurized machine 10 can not produce any pressure for fuel injector in this stage.The operation of the pressurized machine 10 in Fig. 2 c and Fig. 2 d defines high pressure pattern.In high pressure pattern, pressurized machine 10,10 ' works as unidirectional pressurized machine, and pressure fluid is only fed to system by this unidirectional pressurized machine in one of the displace-ment directions, and another movement direction of plunger 11,11 ' is used to reload pressurized machine 10,10 '.
When Fig. 2 e, plunger 11 is in its bottom position, that is, be in the end being positioned with the 3rd fluid port 10c.First switch valve 6 is closed to prevent the flowing in the first Room 12a.3rd switch valve 8 is opened and will be allowed to the flowing in the 3rd Room 12c, but because fluid also to flow in the second Room 12b by the first safety check 13 and the area of the second pressure surface A2 is greater than the area of the 3rd pressure surface A3, therefore plunger 11 can not move up.4th switch valve 9 is closed in case fluid is flowed into storage tank 1 from the pressure line 21 of the 3rd Room 12c by the reflux pipeline 22 of the 3rd Room 12c.Therefore fluid flows to fuel injector by two routes: by the first safety check 13 and the second safety check 14; And by the 3rd switch valve 8 and the 4th safety check 16 and the 3rd safety check 15.3rd switch valve 8 also can be closed.In this case, fluid will flow only through the first safety check 13 and the second safety check 14.Second switch valve 7 also can be opened.This is bypass mode, and in this bypass mode, if ignore the pressure loss in system, then the pressure at fuel injector place is identical with the pressure at pump 2 place.If the first switch valve 6 is not opened after plunger 11 moves downward, then prevent plunger 11 move upward and pressurized machine 10 is switched to bypass mode.
Above only describes the function of the first pressurized machine 10.Second pressurized machine 10 ' works in an identical manner, but this second pressurized machine is arranged to work in the stage being different from the first pressurized machine 10.If place needs Intermediate High Pressure at fuel injector, then pressurized machine 10,10 ' works under the operator scheme of Fig. 2 a and Fig. 2 b.When the pressure line 18 of the first Room 12a to the first pressurized machine 10 is opened and plunger 11 moves up, to the first Room 12a ' of the second pressurized machine 10 ' with the pressure line 18 ', 21 ' of the 3rd Room 12c ' is closed and the plunger 11 ' of the second pressurized machine 10 ' moves down.And second the reflux pipeline 22 ' of the 3rd Room 12c ' of pressurized machine 10 ' also close.Pressurized machine 10,10 ' both supplies fluid to fuel injector with identical pressure.Second pressurized machine 10 ' also can operate in the mode described in Fig. 2 d.In this case, the reflux pipeline 22 ' of the 3rd Room 12c ' of the second pressurized machine 10 ' will be opened, and the second pressurized machine 10 ' will not produce any pressure being used for fuel injector.When plunger 11,11 ' arrives their end position, related valves is switched to other position to change the movement direction of plunger 11,11 '.Due to the second accumulator 5, therefore the plunger 11 of the first pressurized machine 10 and the plunger 11 ' of the second pressurized machine 10 ' can be in opposite phase and can change their movement direction simultaneously.Second accumulator 5 guarantees that the fluid being fed to the second subtense angle 24 is not interrupted.But pressurized machine 10,10 ' also can be arranged to work and make plunger 11,11 ' can not arrive their end position simultaneously.The interruption of such fluid supply avoiding being caused by the change of the movement direction of plunger 11,11 '.
When needing high pressure at fuel injector place, pressurized machine 10,10 ' works under the operator scheme of Fig. 2 c and Fig. 2 d.When the pressure line 18 of the first Room 12a to the first pressurized machine 10 and the pressure line 21 of the 3rd Room 12c are opened and the plunger 11 of the first pressurized machine 10 moves up so that high pressure fluid is fed to fuel injector, what the second pressurized machine 10 ' was in Fig. 2 d reloads the stage.The pressure line 18 ' of the first Room 12a ' of therefore to the second pressurized machine 10 ' and the pressure line 21 ' of the 3rd Room 12c ' are closed and the plunger 11 ' of the second pressurized machine 10 ' moves down.When the position of related valves is switched, the movement direction of plunger 11,11 ' also changes.When plunger 11,11 ' arrives its end position, the change from pressure supply stage to the stage of reloading can be carried out.The endurance of reloading the stage is shorter than the endurance in pressure supply stage, and therefore plunger 11,11 ' can maintain the bypass mode of Fig. 2 e after the stage of reloading, until other plungers 11,11 ' being in the pressure supply stage arrive its end position.Pressurized machine 10,10 ' can be provided with position transducer, and these position transducers are for determining the suitable timing that the position of switching related switch valve is used.
If do not need pressure to strengthen, then the plunger 11,11 ' of two pressurized machines 10,10 ' can operate under the bypass mode of Fig. 2 e.
Second accumulator 5 is arranged in the upstream of fuel injector between the first pressurized machine 10 and the second pressurized machine 10 '.An object of the second accumulator 5 is reduce pressure pulsation and prevent the fluid supply discontinuity when the plunger 11,11 ' of pressurized machine 10,10 ' changes their movement direction.
Mode of execution shown in Fig. 3 works in the mode identical with the mode of execution shown in Fig. 1 to Fig. 2 e.In figure 3, the first accumulator 4 and reduction valve 3 are not illustrated, but this mode of execution also can be provided with these devices.The main distinction between these mode of executions is, in the system of figure 3, the reflux pipeline 22,22 ' from the 3rd Room 12c, 12c ' is provided with the 5th safety check 25,25 ' not allowing flowing in storage tank 1.Reflux pipeline 22,22 ' therefore only for by fluid is introduced first Room 12a, 12a ' and upwards drive plunger 11,11 ' time fluid is sucked in the 3rd Room 12c, 12c '.Therefore the 4th switch valve 9,9 ' is not needed.In the stage of reloading, the 3rd Room 12c, 12c ' is moved sky by the 3rd pressure line 21,21 '.The advantage of this layout is, is recovered by the energy of the fluid storage in the 3rd Room 12c, 12c '.Because the 3rd pressure line 21,21 ' must allow to flow in the two directions, therefore it not at the 3rd switch valve 8, the 4th safety check 16,16 ' is set between 8 ' and pressurized machine 10,10 '.On the contrary, there is the 6th safety check 26,26 ' at the opposite side of the 3rd switch valve 8,8 '.Throttle valve 27,27 ' is parallel to the 6th safety check 26,26 ' and arranges with the flowing of balance from pump 2 to two plungers 11,11 '.The functional situation preventing the major part of wherein pump stream to be only directed into one of them plunger 11,11 ' of throttle valve 27,27 '.6th safety check 26,26 ' allows from pump 2 to the flowing of pressurized machine 10,10 ', but does not allow the flowing on other direction.When the 3rd Room 12c, 12c ' is moved sky in the stage of reloading, fluid flows through throttle valve 27,27 '.
According to another embodiment of the present invention, the size of pressure surface is selected as making the combined area of the first pressure surface A1 and the 3rd pressure surface A3 in manufacturing tolerances, to equal the area of area divided by the 3rd pressure surface A3 of the second pressure surface A2 divided by the area of the second pressure surface A2, that is, (A1+A3)/A2=A2/A3.By this selection, pressurized machine 10,10 ' all can supply high pressure fluid to fuel injector 24 between moving period up and down at plunger 11,11 '.When fluid is introduced in first Room 12a, 12a ' of pressurized machine 10,10 ', pressure fluid in supplying to fuel injector 24.Fig. 2 b and Fig. 2 c therefore the high pressure pattern of pressurized machine 10 will be shown and Fig. 2 a and Fig. 2 d will illustrate middle pressure pattern.In this embodiment, pressurized machine 10,10 ' works as unidirectional pressurized machine under middle pressure pattern as double action booster work under high pressure pattern.
It will be appreciated by those skilled in the art that and the invention is not restricted to above-mentioned mode of execution, but can change in the scope of appended claim.Such as, hydraulic system there is no need in explosive motor, but it may be used for any hydraulic equipment of action need different pressures level.Can also with the area on aforesaid way differently selection pressure surface.Therefore the different pressure ratio of two or more can be obtained.
Claims (9)
1. a hydraulic system, described hydraulic system at least comprises:
-at first subtense angle (23) of the first operate in pressure ranges; And
-at second subtense angle (24) of the second operate in pressure ranges, the upper limit of described second pressure range is higher than the upper limit of described first pressure range, and described hydraulic system also comprises:
-pump (2), described pump is used for being fed to by hydraulic fluid in described hydraulic system under a first pressure level; And
-for the pressure in described second subtense angle being increased to first pressurized machine (10) of the second stress level and the second pressurized machine (10 ') for the pressure in described second subtense angle being increased to the second stress level,
Each pressurized machine includes plunger (11,11 '), and described plunger (11,11 ') comprising:
-the first pressure surface (A1, A1 ');
-the second pressure surface (A2, A2 '); And
-three pressure surface (A3, A3 '),
Described first pressure surface (A1, A1 ') and described 3rd pressure surface (A3, A3 ') at described plunger (11,11 ') movement direction is positioned at described plunger (11,11 ') the same side and described second pressure surface (A2, A2 ') be positioned at opposition side, and the wall of described pressurized machine (10,10 ') defines:
-there is first Room (12a, 12a ') of described first pressure surface (A1, A1 ');
-there is second Room (12b, 12b ') of described second pressure surface (A2, A2 '); And
-there is the 3rd Room (12c, 12c ') of described 3rd pressure surface (A3, A3 '),
Each room (12a, 12a ', 12b, 12b ', 12c, 12c ') all can be connected to the outlet of described pump (2) with receiving liquid hydraulic fluid, described second Room (12b, 12b ') and described 3rd Room (12c, 12c ') be also connected to described second subtense angle (24) to be fed to by hydraulic fluid in this second subtense angle
The feature of described hydraulic system is, in order to each pressurized machine (10, 10 ') at least two optional pressure ratios are provided, described second pressure surface (A2, A2 ') be greater than described 3rd pressure surface (A3, A3 '), and described hydraulic system is provided with for opening and closing described pump (2) and described pressurized machine (10, 10 ') described first Room (12a, 12a ') between flowing be communicated with gate-controlled switch valve (6, 6 '), and described hydraulic system is provided with for opening and closing described pump (2) and described 3rd Room (12c, 12c ') between flowing be communicated with another gate-controlled switch valve (8, 8 ').
2. hydraulic system according to claim 1, it is characterized in that, described first pressure surface (A1, A1 ') area and described second pressure surface (A2, A2 ') area between ratio and described second pressure surface (A2, A2 ') area and the area of described 3rd pressure surface (A3, A3 ') between the difference of ratio be at most 0.02.
3. hydraulic system according to claim 1, it is characterized in that, described first pressure surface (A1, A1 ') and described 3rd pressure surface (A3, A3 ') combined area and described second pressure surface (A2, A2 ') area between ratio and the area of the area of described second pressure surface (A2, A2 ') and described 3rd pressure surface (A3, A3 ') between the difference of ratio be at most 0.02.
4. the hydraulic system according to any one in aforementioned claim, is characterized in that, described first subtense angle (23) and described second subtense angle (24) comprise the parts of explosive motor.
5. hydraulic system according to claim 4, is characterized in that, described first subtense angle (23) comprises the gas exchange valve of described motor, and described second subtense angle (24) comprises the fuel injector of described motor.
6. the hydraulic system according to any one in claims 1 to 3, is characterized in that, described pump (2) is variable displacement pump.
7., for operating a method for hydraulic system, described hydraulic system at least comprises:
-at first subtense angle (23) of the first operate in pressure ranges; And
-at second subtense angle (24) of the second operate in pressure ranges, the upper limit of described second pressure range is higher than the upper limit of described first pressure range, and described hydraulic system also comprises:
-for the pressure in described second subtense angle being increased to first pressurized machine (10) of the second stress level and the second pressurized machine (10 ') for the pressure in described second subtense angle being increased to the second stress level, described first pressurized machine (10) and described second pressurized machine (10 ') are piston super charger, and each pressurized machine (10,10 ') all there are at least two optional pressure ratios
Described method at least comprises the first operator scheme, and described first operator scheme comprises the first stage, in this first stage,
-hydraulic fluid is only introduced in first Room (12a) of described first pressurized machine (10), with the plunger (11) of this first pressurized machine (10) mobile and the fluid pressurizeed in second Room (12b) of this pressurized machine (10) this fluid is fed to described second subtense angle (24); And
-hydraulic fluid is introduced in second Room (12b ') of described second pressurized machine (10 '), with the plunger (11 ') of this second pressurized machine (10 ') mobile, thus move first Room (12a ') of this second pressurized machine (10 ') empty and the 3rd Room (12c ')
Described first operator scheme also comprises second stage, in this second stage,
-hydraulic fluid is only introduced in described first Room (12a ') of described second pressurized machine (10 '), the fluid with the described plunger (11 ') of this second pressurized machine (10 ') mobile and in described second Room of this second pressurized machine (10 ') that pressurizes (12b ') and this fluid is fed to described second subtense angle (24); And
-hydraulic fluid is introduced in described second Room (12b) of described first pressurized machine (10), with the described plunger (11) of this first pressurized machine (10) mobile, thus move described first Room (12a) and the 3rd Room (12c) of this first pressurized machine (10) empty
Described method also comprises the second operator scheme, and described second operator scheme comprises the first stage, in the described first stage of described second operator scheme,
-hydraulic fluid is introduced described first pressurized machine (10) described first Room (12a) and described 3rd Room (12c) in, with the mobile described plunger (11) of this first pressurized machine (10) and the fluid in described second Room (12b) of this first pressurized machine (10) that pressurizes and by this fluid to be fed to described second subtense angle (24) higher than the pressure in described first operator scheme; And
-hydraulic fluid is introduced in described second Room (12b ') of described second pressurized machine (10 '), with the described plunger (11 ') of this second pressurized machine (10 ') mobile, thus move described first Room (12a ') of this second pressurized machine (10 ') empty and described 3rd Room (12c ')
Described second operator scheme also comprises second stage, in the described second stage of described second operator scheme,
-hydraulic fluid is introduced in described first Room (12a ') of described second pressurized machine (10 ') and described 3rd Room (12c '), the fluid with the described plunger (11 ') of this second pressurized machine (10 ') mobile and in described second Room of this second pressurized machine (10 ') that pressurizes (12b ') and by this fluid to be fed to described second subtense angle (24) higher than the pressure in described first operator scheme; And
-hydraulic fluid is introduced in described second Room (12b) of described first pressurized machine (10), with the described plunger (11) of this first pressurized machine (10) mobile, thus move described first Room (12a) of this first pressurized machine (10) empty and described 3rd Room (12c).
8. method according to claim 7, it is characterized in that, described plunger (11,11 ') empty described first Room (12a is moved, 12a ') and described 3rd Room (12c, 12c ') motion this fluid is fed to described second subtense angle (24) for the fluid in described 3rd Room of pressurizeing (12c, 12c ').
9. the method according to claim 7 or 8, is characterized in that, in described second operator scheme, described 3rd Room (12c, 12c ') be filled by same pipeline (21,21 ') and move sky.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FI20115392A FI20115392A0 (en) | 2011-04-21 | 2011-04-21 | Hydraulic system and operating procedure |
| FI20115392 | 2011-04-21 | ||
| PCT/FI2012/050388 WO2012143614A1 (en) | 2011-04-21 | 2012-04-19 | Hydraulic system and operating method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103477088A CN103477088A (en) | 2013-12-25 |
| CN103477088B true CN103477088B (en) | 2015-12-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280019299.4A Active CN103477088B (en) | 2011-04-21 | 2012-04-19 | Hydraulic system and operating method |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2699805B1 (en) |
| KR (1) | KR101941723B1 (en) |
| CN (1) | CN103477088B (en) |
| FI (1) | FI20115392A0 (en) |
| WO (1) | WO2012143614A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103851037A (en) * | 2012-11-29 | 2014-06-11 | 何荣志 | Multi-pressure source energy-saving hydraulic pressure station |
| EP3904699B1 (en) * | 2013-03-25 | 2022-12-14 | miniBOOSTER HYDRAULICS A/S | Hydraulic system |
| CN104074812B (en) * | 2014-07-14 | 2016-08-03 | 青岛大学 | A kind of hydraulic booster energy-recuperation system and control device |
| CN108527524A (en) * | 2018-05-08 | 2018-09-14 | 沈阳奥拓福科技股份有限公司 | A kind of double-core super-pressure pump of the spare booster of band |
| CN110374939B (en) * | 2019-07-19 | 2020-05-19 | 南京理工军邦特种智能装备研究院有限公司 | Hydraulic system for providing two different pressures and pressure supply method |
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| US3570101A (en) * | 1968-07-01 | 1971-03-16 | Skyhi Ltd | Hydraulic and pneumatic system for controlling tools |
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- 2012-04-19 WO PCT/FI2012/050388 patent/WO2012143614A1/en active Application Filing
- 2012-04-19 KR KR1020137030707A patent/KR101941723B1/en active IP Right Grant
- 2012-04-19 CN CN201280019299.4A patent/CN103477088B/en active Active
- 2012-04-19 EP EP12721884.0A patent/EP2699805B1/en active Active
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| US2508298A (en) * | 1948-04-16 | 1950-05-16 | Oliver J Saari | Fluid pressure intensifying device |
| US3234882A (en) * | 1964-06-03 | 1966-02-15 | Rexall Drug Chemical | Intensifier assembly system and method |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2012143614A1 (en) | 2012-10-26 |
| KR101941723B1 (en) | 2019-01-23 |
| FI20115392A0 (en) | 2011-04-21 |
| CN103477088A (en) | 2013-12-25 |
| KR20140034195A (en) | 2014-03-19 |
| EP2699805A1 (en) | 2014-02-26 |
| EP2699805B1 (en) | 2015-05-27 |
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