CN101871477A - Intermediate-pressure control two-position variable axial plunger hydraulic motor - Google Patents
Intermediate-pressure control two-position variable axial plunger hydraulic motor Download PDFInfo
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Abstract
The invention discloses an intermediate-pressure control two-position variable axial plunger hydraulic motor, which belongs to the technical field of hydraulics. The hydraulic motor comprises a shuttle valve, a reducing valve, a two-position four-way valve, a variable hydraulic cylinder, a damper, a variable axial plunger hydraulic motor, a washing shuttle valve and a washing overflow valve. The pressure of system high-pressure oil is reduced into an intermediate pressure by the shuttle valve and the reducing valve so as to drive a servo piston of the variable hydraulic cylinder to move. Due to the adoption of intermediate-pressure control, the hydraulic motor can simultaneously integrates the advantages of controlling the variable hydraulic cylinder by a system high pressure and a system low pressure so as to easily realize high-speed and low-speed adjustment in the conceptual design of the same variable motor, select relatively greater damper bore diameters, realize proper variable speeds, achieve a wider speed adjustment range and high control performance, and reduce the sensitivity of the variable hydraulic cylinder to pollution. An initial position of motor displacement can be randomly set to be a maximum or minimum displacement position according to the needs of clients. Due to the adoption of the hydraulic cylinder with a medium piston size, the overall dimension of the whole variable motor can be optimally designed.
Description
Technical field
The present invention relates to a kind of two-position variable axial plunger hydraulic motor, the two-position variable axial plunger hydraulic motor of pressure-controlled variable oil hydraulic cylinder belongs to hydraulic transmission technology field in particularly a kind of the employing.
Background technique
Oil hydraulic pump and oil hydraulic motor have been formed the energy conversion device in the hydraulic system, and the former converts the mechanical energy of prime mover to the hydraulic pressure energy of liquid; The latter can convert hydraulic pressure to mechanical energy output, carries out desired action.Oil hydraulic motor is to realize the hydraulic actuator that rotatablely moves continuously.
Divide from function, oil hydraulic pump has the branch of variable displacement and immutable discharge capacity.The variable-displacement oil hydraulic pump is the different flow of output under same speed conditions according to demand, and this kind pump is called variable displacement pump.With variable displacement pump in like manner, change the oil hydraulic motor of discharge capacity by stroking mechanism, be called variable displacement motor.The advantage of variable displacement motor is the secondary adjusting of the system that can realize; Or in some certain applications, the high-voltage performance of performance pump; Or when a hydraulic pump source drove several executive component, variable displacement motor can freely be controlled output speed and output torque, thereby realized different execution requirements.
For the motor of immutable discharge capacity, i.e. fixed displacement motor.The inlet flow rate of governor motor can be regulated the rotating speed of fixed displacement motor.As adopt throttle valve to control the inlet flow rate of fixed displacement motor, can follow the loss of bigger pressure and flow, so this kind mode adopts seldom.And adopt Moderator Variable pump delivery or rotating speed to regulate the rotating speed of fixed displacement motor, and the speed governing of fixed displacement motor can only be according to variable pump delivery and change in rotational speed range regulation, and speed adjustable range is limited.As adopt variable displacement motor, under the constant situation of motor inlet flow, the discharge capacity of governor motor can realize the adjusting of variable displacement motor rotating speed rapidly, or not only changed the inlet flow rate of variable displacement motor but also changed the discharge capacity of variable displacement motor, all can realize the adjusting to the variable displacement motor rotating speed, the employing of variable displacement motor can increase the speed adjustable range of motor.This adjusting is called secondary to be regulated, and can realize online speed-regulating function.Variable displacement motor makes this secondary easy to adjust, fast, and effectively.
When the needs motor is exported big torque during at low speed, when perhaps when high speed, exporting little torque, be fit to very much the application of variable displacement motor.Because if adopt variable displacement pump and fixed displacement motor to form hydraulic speed regulation system, when the little torque of high speed, pump will operate in the big discharge capacity operating mode of low pressure; When low speed high torque, pump will operate in high pressure float amount operating mode.Therefore, pump and whole hydraulic system need be according to high pressure, and big discharge capacity designs.If the employing variable displacement motor, thus can allow motor under float amount operating mode, move the requirement of satisfying the little torque of high speed, in like manner, when variable displacement motor moves in big discharge capacity operating mode, can realize the operating mode of low-speed big.Like this, pump substantially all is in high-voltage operation, gives full play to the high-voltage performance of pump.
Oil hydraulic motor can be divided into high-speed hydraulic motor, low speed hydraulic motor and rotary actuator.High-speed hydraulic motor can be divided into high-speed quantitative oil hydraulic motor and high speed variable hydraulic motor.Wherein, the high speed variable hydraulic motor can be divided into according to the structural type difference, variable vane motor, variable radial piston motor and variable axial plunger motor, compare with preceding two types motor, the pressure range of variable axial plunger motor is higher, and the discharge capacity scope is big, rotating speed is higher, peak output mass ratio height, volumetric efficiency height, easier realization variable design.So the variable axial plunger motor has very big ratio in the variable displacement motor in modern times.According to the variation pattern of discharge capacity, the variable mode of variable piston oil hydraulic motor can be divided into two kinds of stepless variable and two-position variables.The stepless variable plunger piston hydraulic motor, the normal method that adopts electrichydraulic control, by velocity transducer or pressure transducer rotating speed or the pressure that changes is fed back to moving of electro-hydraulic proportional valve or servovalve control motor variable servopiston with electric weight, mediate the easily dynamic calibration of process of this control, but, cause the stepless variable plunger piston hydraulic motor to cost an arm and a leg owing to need elements such as employing speed, pressure transducer and electro-hydraulic proportional valve.
Two-position variable axial plunger hydraulic motor because of its variable characteristic and high performance-price ratio at farm machinery, be widely used on the turf machinery.The variable oil hydraulic cylinder of two-position variable axial plunger hydraulic motor in the market can be driven by system high pressure.Adopt this mode, can obtain the servopiston size of little variable oil hydraulic cylinder and the size of less entire variable motor.But, adopt system high pressure to come the controlled variable oil hydraulic cylinder, cause the reaction velocity of variable oil hydraulic cylinder too fast, thereby make that the handling of two-position variable axial plunger hydraulic motor is not steady, sometimes adopt damper to obtain certain control rate in the variable control system, but the aperture size of this damper is very little, is generally 0.2mm～0.5mm, these turbidity test to system require than higher, make control system too responsive.Another current mode is to adopt system low-voltage to drive the variable oil hydraulic cylinder of two-position variable axial plunger hydraulic motor, adopt this mode can obtain stable handling, but the piston size of its variable oil hydraulic cylinder is bigger, influence its use occasion of motor overall size limitations, and, be difficult to realize quick response because its pilot pressure is low.
Summary of the invention
In order to overcome the deficiency of prior art, optimize the handling of two-position variable axial plunger hydraulic motor, enlarge its speed adjustable range and reduce its dependence system's turbidity test.The invention provides a kind of design of adopting medium pressure to control the variable oil hydraulic cylinder of two-position variable axial plunger hydraulic motor.This medium pressure can be realized by reduction valve.Adopt medium pressure to come the controlled variable oil hydraulic cylinder, can adopt the variable oil hydraulic cylinder of medium servopiston size, and can choose bigger damper aperture size, thereby realize speed adjustable range and good handling widely.The present invention realizes by following technical proposals: the present invention includes: shuttle valve, reduction valve, two-position four-way valve, variable oil hydraulic cylinder, damper, variable axial plunger hydraulic motor, flushing shuttle valve, flushing relief valve.The import of variable axial plunger hydraulic motor is connected with the volume adjustable hydraulic pump outlet, the outlet of variable axial plunger hydraulic motor is connected with the volume adjustable hydraulic pump import, two imports of shuttle valve link to each other with the import and export of variable axial plunger hydraulic motor respectively, the outlet of shuttle valve links to each other with the import of reduction valve, the outlet of reduction valve links to each other with variable oil hydraulic cylinder chamber, a left side or right chamber by two-position four-way valve, right chamber of variable oil hydraulic cylinder or left chamber link to each other with motor casing by two-position four-way valve, motor casing communicates with fuel tank, and the servopiston of variable oil hydraulic cylinder links to each other with the stroking mechanism of variable axial plunger hydraulic motor to realize the variable adjusting.Two imports of flushing shuttle valve link to each other with the import and export of variable axial plunger hydraulic motor respectively, and the outlet of flushing shuttle valve links to each other with the import of flushing relief valve, and the outlet of flushing relief valve is connected to motor casing.Damper is the metal cylinder that the center has aperture, is fixed in by screw thread in the connecting pipeline of variable oil hydraulic cylinder and two-position four-way valve.Reduction valve adopts definite value overfalling type reduction valve, its working principle is for passing through pressure differential pressure and input quantity, normally effect of the feedback ratio of spring force, automatic regulating valve mouth orifice size size, make the pressure of output keep constant substantially, thereby obtain stable medium pressure, its relief function is when reduction valve outlet end pressure is higher than the spring setting value, can outlet end pressure be adjusted to the spring setting value by the mode of overflow, guarantee the constant of outlet end pressure.Reduction valve often leaves, and when outlet end pressure did not reach the adjusting pressure of valve, spool was often opened, and only when load cavity pressure reached set pressure, valve core movement turned down valve port, realizes decompression control.
The middle pressure oil of controlled variable oil hydraulic cylinder is provided by reduction valve among the present invention, system high pressure oil is successively through reducing to tens to handkerchief medium pressures up to a hundred behind shuttle valve and the reduction valve, when the control end of two-position four-way valve does not obtain input control signal, two-position four-way valve is operated in initial position, oil content in this medium pressure fluid and the motor casing does not act on the chamber, the left and right sides of variable oil hydraulic cylinder, the pressure difference in chamber, the variable oil hydraulic cylinder left and right sides moves variable oil hydraulic cylinder servopiston occurred level, displacement variation by stroking mechanism drive variable displacement motor makes two-position variable axial plunger hydraulic motor be in maximum or minimum injection rate position.When to the two-position four-way valve input control signal, the fluid that links to each other with the chamber, the left and right sides of variable oil hydraulic cylinder commutates, thereby the displacement variation that makes two-position variable axial plunger hydraulic motor is to minimum or maximum position.This motor also is furnished with the flushing shuttle valve and washes relief valve to realize the cleaning systems oil circuit and to reduce the warm effect of oil.
Beneficial effect of the present invention: for realizing stable handling, adopt medium pressure control mode of the present invention, the comparable employing high voltage control of the aperture size of damper mode big, reduce the susceptibility of variable oil hydraulic cylinder greatly to polluting, and the size of variable oil hydraulic cylinder is less, but the boundary dimension of the whole variable displacement motor of optimal design.The medium pressure control mode makes and easily to realize in the conceptual design be adjusted in same variable displacement motor fast and at a slow speed, variable speed governing wider more flexible.
Description of drawings
Fig. 1 is of the present invention oil hydraulic motor principle schematic of initial position when maximum pump discharge.
Fig. 2 is of the present invention oil hydraulic motor principle schematic of initial position when minimum injection rate.
Among the figure: 1. shuttle valve, 2. reduction valve, 3. two-position four-way valve, 3a. position, a two-position four-way valve left side, the right position of 3b. two-position four-way valve, 3c. two-position four-way valve control end, 4. variable oil hydraulic cylinder, 4a. chamber, a variable oil hydraulic cylinder left side, 4b. variable oil hydraulic cylinder right chamber, 5. damper, 6. variable axial plunger hydraulic motor, 7. flushing shuttle valve, 7a. flushing shuttle valve is upper, 7b. flushing shuttle valve meta, 7c. the flushing shuttle valve is the next, 8. flushing relief valve, 9. motor casing, 10. volume adjustable hydraulic pump, 11. servopiston, 12. stroking mechanism, A are system's working connection high voltage terminal, B is system's working connection low voltage terminal.
Embodiment
Below in conjunction with accompanying drawing concrete enforcement of the present invention is further described.
As Fig. 1, shown in Figure 2, the present invention includes: shuttle valve 1, reduction valve 2, two-position four-way valve 3, variable oil hydraulic cylinder 4, damper 5, variable axial plunger hydraulic motor 6, flushing shuttle valve 7, flushing relief valve 8.
When the initial position of central pressure-controlled two-position variable axial plunger hydraulic motor discharge capacity is located at maximum pump discharge, (as shown in Figure 1).The import of variable axial plunger hydraulic motor 6 links to each other with the outlet of volume adjustable hydraulic pump 10, and the outlet of variable axial plunger hydraulic motor 6 links to each other with the import of volume adjustable hydraulic pump 10.Two imports of shuttle valve 1 link to each other with the import and export of variable axial plunger hydraulic motor 6 respectively.The outlet of shuttle valve 1 links to each other with the import of reduction valve 2, and the outlet of reduction valve 2 links to each other with the right chamber 4b of A mouth and variable oil hydraulic cylinder by the P mouth of two-position four-way valve 3, and variable oil hydraulic cylinder left side chamber 4a links to each other with motor casing 9 with the T mouth by the B mouth of two-position four-way valve 3.Motor casing 9 communicates with fuel tank.The servopiston 11 of variable oil hydraulic cylinder 4 links to each other with the stroking mechanism 12 of variable axial plunger hydraulic motor, and the to-and-fro motion of servopiston 11 drives the motion of stroking mechanism 12, realizes the displacement variation of variable axial plunger hydraulic motor 6.Two imports of flushing shuttle valve 7 link to each other with the import and export of variable axial plunger hydraulic motor 6 respectively.The outlet of flushing shuttle valve 7 links to each other with the import of flushing relief valve 8.The outlet of flushing relief valve 8 is connected to motor casing 9.Damper 5 is metal cylinders that the center has aperture, is fixed in by screw thread in the A mouth connecting pipeline of right chamber 4b of variable oil hydraulic cylinder and two-position four-way valve 3.Reduction valve 2 adopts the definite value overfalling type, and when it was in stable state, spring force and outlet induced pressure balanced each other, and its delivery pressure is stabilized in setting value.If when the outlet induced pressure of reduction valve 2 surpassed its delivery pressure setting value, the spool of reduction valve 2 moved valve core opening is diminished, regulate the delivery pressure value and reach its setting pressure, promptly stable medium pressure.
The fluid of the high pressure A oil circuit of system and low pressure B oil circuit feeds two imports of shuttle valve 1, under the effect of high pressure oil, the low pressure oil circuit is plugged, the oil of high-pressure oil passage is by the effect of reduction valve 2, reduce to tens to handkerchief medium pressures up to a hundred, when two-position four-way valve control end 3c does not obtain input control signal, the right position of two-position four-way valve 3b is the initialization position, this medium pressure fluid is by P mouth and the right chamber 4b of A mouth entering variable oil hydraulic cylinder of the right position of two-position four-way valve 3b, the oil return that links to each other with motor casing 9 of the B mouth of variable oil hydraulic cylinder left side chamber 4a by two-position four-way valve 3 and T mouth, because the pressure difference in 4 liang of chambeies of variable oil hydraulic cylinder, under the effect of middle pressure fluid, servopiston 11 is moved to the left, and the motion by stroking mechanism 12 makes two-position variable axial plunger hydraulic motor be in displacement.When two-position variable axial plunger hydraulic motor need quicken, from two-position four-way valve control end 3C input control signal, valve core movement made two-position four-way valve left side position 3a become the working position.Then medium pressure oil is by the P mouth and the B mouth entering variable oil hydraulic cylinder left side chamber 4a of two-position four-way valve 3, and the oil in the right chamber 4b of variable oil hydraulic cylinder flows in the motor casing 9 by the A mouth and the T mouth of two-position four-way valve 3.Servopiston 11 moves to right under the effect of left and right sides pressure, and the motion by stroking mechanism 12 makes the two-position variable axial plunger hydraulic motor discharge capacity fade to minimum position, reaches the purpose that motor quickens.In some cases, if the unexpected signal out of hand of two-position four-way valve control end 3c, the two-position four-way valve core is back to initial position, and the two-position variable axial plunger hydraulic motor discharge capacity will be got back to displacement automatically.
When the initial position of central pressure-controlled two-position variable axial plunger hydraulic motor discharge capacity is located at minimum injection rate, (as shown in Figure 2).The import of variable axial plunger hydraulic motor 6 links to each other with the outlet of volume adjustable hydraulic pump 10, and the outlet of variable axial plunger hydraulic motor 6 links to each other with the import of volume adjustable hydraulic pump 10.Two imports of shuttle valve 1 link to each other with the import and export of variable axial plunger hydraulic motor 6 respectively.The outlet of shuttle valve 1 links to each other with the import of reduction valve 2, and the outlet of reduction valve 2 links to each other with variable oil hydraulic cylinder left side chamber 4a with the A mouth by the P mouth of two-position four-way valve 3, and the right chamber 4b of variable oil hydraulic cylinder links to each other with motor casing 9 with the T mouth by the B mouth of two-position four-way valve 3.Motor casing 9 communicates with fuel tank.The servopiston 11 of variable oil hydraulic cylinder 4 links to each other with the stroking mechanism 12 of variable axial plunger hydraulic motor, and the to-and-fro motion of servopiston 11 drives the motion of stroking mechanism 12, realizes the displacement variation of variable axial plunger hydraulic motor 6.Two imports of flushing shuttle valve 7 link to each other with the import and export of variable axial plunger hydraulic motor 6 respectively.The outlet of flushing shuttle valve 7 links to each other with the import of flushing relief valve 8.The outlet of flushing relief valve 8 is connected to motor casing 9.Damper 5 is metal cylinders that the center has aperture, be fixed in by screw thread in the A mouth connecting pipeline of variable oil hydraulic cylinder left side chamber 4a and two-position four-way valve 3, reduction valve 2 adopts the definite value overfalling type, when it is in stable state, spring force and outlet induced pressure balance each other, and its delivery pressure is stabilized in setting value.If when the outlet induced pressure of reduction valve 2 surpassed its delivery pressure setting value, the spool of reduction valve 2 moved valve core opening is diminished, regulate the delivery pressure value and reach its setting pressure.
The fluid of the high pressure A oil circuit of system and low pressure B oil circuit feeds two imports of shuttle valve 1, under the effect of high pressure oil, the low pressure oil circuit is plugged, the oil of high-pressure oil passage is by the effect of reduction valve 2, reduce to tens to handkerchief medium pressures up to a hundred, when two-position four-way valve control end 3C does not obtain input control signal, the right position of two-position four-way valve 3b is the initialization position, this medium pressure fluid is by P mouth and the A mouth entering variable oil hydraulic cylinder left side chamber 4a of the right position of two-position four-way valve 3b, the oil return that links to each other with motor casing 9 of the B mouth of the right chamber 4b of variable oil hydraulic cylinder by two-position four-way valve 3 and T mouth, because the pressure difference in 4 liang of chambeies of variable oil hydraulic cylinder, under the effect of middle pressure fluid, servopiston 11 moves right, and the motion by stroking mechanism 12 makes two-position variable axial plunger hydraulic motor be in the minimum injection rate position.When two-position variable axial plunger hydraulic motor need slow down, from two-position four-way valve control end 3C input control signal, valve core movement made two-position four-way valve left side position 3a become the working position.Then medium pressure oil is by the P mouth and the right chamber 4b of B mouth entering variable oil hydraulic cylinder of two-position four-way valve 3, and the oil in the chamber 4a of a variable oil hydraulic cylinder left side flows in the motor casing 9 by the A mouth and the T mouth of two-position four-way valve 3.Servopiston 11 moves to left under the effect of left and right sides pressure, and the motion by stroking mechanism 12 makes the two-position variable axial plunger hydraulic motor discharge capacity fade to maximum position, reaches the purpose that motor slows down.In some cases, if the unexpected signal out of hand of two-position four-way valve control end 3c, the two-position four-way valve core is back to initial position, and the two-position variable axial plunger hydraulic motor discharge capacity will be got back to the minimum injection rate position automatically.
Reduction valve adopts definite value overfalling type reduction valve, its working principle is for passing through pressure differential pressure and input quantity, normally effect of the feedback ratio of spring force, automatic regulating valve mouth orifice size size, make the pressure of output keep constant substantially, thereby obtain stable medium pressure, its relief function is when reduction valve outlet end pressure is higher than the spring setting value, can outlet end pressure be adjusted to the spring setting value by the mode of overflow, guarantee the constant of outlet end pressure.Reduction valve often leaves, and when outlet end pressure did not reach the adjusting pressure of valve, spool was often opened, and only when load cavity pressure reached set pressure, valve core movement turned down valve port, realizes decompression control.When being 55cc for the maximum pump discharge of variable axial plunger hydraulic motor 6, reach at the maximum system induced pressure under the situation of 450bar, according to calculating, reduction valve outlet pressure setting value is about 60bar.The maximum pump discharge of reduction valve outlet pressure setting value and variable axial plunger hydraulic motor 6 and rotating speed, the work area of servopiston 11, the design of stroking mechanism 12, maximum system induced pressure and system condition are relevant.
Damper 5 is used to regulate the flow of entering variable oil hydraulic cylinder 4, regulates with the reaction velocity that realizes stroking mechanism.The flow coefficient of the definite and damping hole of damper 5 aperture sizes, the pressure reduction before and after the damping hole, the density of fluid is relevant with the flow of the damping hole of flowing through, as the formula (1).
Wherein:
The flow through flow of damping hole of q--
C
d--the flow coefficient of damping hole
A (x)--valve port opening, the i.e. area in damper 5 apertures
The density of ρ--fluid
--the pressure reduction before and after the damping hole
And the structural type of the flow of the damping hole of flowing through and variable oil hydraulic cylinder 4, the size of servopiston 11 and stroke, the design of stroking mechanism 12 and variable governing speed are relevant.When the maximum pump discharge of variable axial plunger hydraulic motor 6 is 55cc, reach at the maximum system induced pressure under the situation of 450bar, according to calculating, the employing diameter is that the damping hole of 2.5mm can be realized the switching of two-position variable axial plunger hydraulic motor between maximum pump discharge and minimum injection rate in 0.2 second, diameter is that the damping hole of 1mm can be implemented in the switching between maximum pump discharge and the minimum injection rate in 1 second, and the damping hole of diameter 0.8mm can be implemented in the switching between maximum pump discharge and the minimum injection rate in 2 seconds.Under equal discharge capacity and system load pressure condition, as adopt the high voltage control method, if will reach 2 seconds variable governing speed, must adopt diameter is the damping hole of 0.2mm, these turbidity test for whole hydraulic system have proposed very high requirement, and the inevitable pollutant of some in the hydraulic system very likely stops up damping hole.
Definite formula (1) of damper 5 aperture sizes is suitable for the different system induced pressure among the present invention, and the middle pressure-controlled two-position variable axial plunger hydraulic motor of different displacements reaches the requirement of different variable governing speeds.
Two-position four-way valve 3 adopts two-position four-way solenoid valve or two-position four-way hydraulic control valve.The control end 3c of two-position four-way solenoid valve input is thereby that voltage or current signal make valve core movement change the fluid direction, thereby the two-position four-way hydraulic control valve adopts inner or outside oil sources makes valve core movement change the fluid direction.
The fluid of the high pressure A oil circuit of system and low pressure B oil circuit feeds the two ends of flushing shuttle valve 7, the flushing shuttle valve spool is pushed under the high low pressure effect, the upper 7a of flushing shuttle valve is the working position, at this moment, the high pressure A oil circuit of system is plugged, the system low-voltage oil circuit will be communicated to the inlet of flushing relief valve 8, according to the setting value overflow of flushing relief valve 8.Then higher fluid and some impurity of the temperature in the hydraulic system will be overflowed hydraulic system, realize the effect of cleaning systems oil circuit and reduction oil temperature.
Claims (4)
1. pressure-controlled two-position variable axial plunger hydraulic motor in a kind, comprise: shuttle valve (1), two-position four-way valve (3), variable oil hydraulic cylinder (4), damper (5), variable axial plunger hydraulic motor (6), flushing shuttle valve (7), flushing relief valve (8), it is characterized in that also comprising reduction valve (2), the import of variable axial plunger hydraulic motor (6) is connected with volume adjustable hydraulic pump (10) outlet, the outlet of variable axial plunger hydraulic motor (6) is connected with volume adjustable hydraulic pump (10) import, two imports of shuttle valve (1) link to each other with the import and export of variable axial plunger hydraulic motor (6) respectively, the outlet of shuttle valve (1) links to each other with the import of reduction valve (2), the outlet of reduction valve (2) links to each other with variable oil hydraulic cylinder chamber (4a), a left side or right chamber (4b) by two-position four-way valve (3), the right chamber (4b) of variable oil hydraulic cylinder or left chamber (4a) link to each other with motor casing (9) by two-position four-way valve (3), motor casing (9) communicates with fuel tank, the servopiston (11) of variable oil hydraulic cylinder (4) links to each other with the stroking mechanism (12) of variable axial plunger hydraulic motor (6), two imports of flushing shuttle valve (7) link to each other with the import and export of variable axial plunger hydraulic motor (6) respectively, the outlet of flushing shuttle valve (7) links to each other with the import of flushing relief valve (8), the outlet of flushing relief valve (8) is connected to motor casing (9), damper (5) is the metal cylinder that the center has aperture, is fixed in by screw thread in the connecting pipeline of variable oil hydraulic cylinder (4) and two-position four-way valve (3).
2. pressure-controlled two-position variable axial plunger hydraulic motor in according to claim 1 is characterized in that described reduction valve (2) is to adopt definite value overfalling type reduction valve.
3. pressure-controlled two-position variable axial plunger hydraulic motor in according to claim 1 is characterized in that described two-position four-way valve (3) is to adopt two-position four-way electrically-controlled valve or two-position four-way hydraulic control valve.
4. pressure-controlled two-position variable axial plunger hydraulic motor in according to claim 1 is characterized in that described damper (5) aperture size is to be determined by (1) formula.
Wherein:
The flow through flow of damping hole of q--
G
d--the flow coefficient of damping hole
A (x)--valve port opening, the i.e. area in damper 5 apertures
The density of ρ--fluid
--the pressure reduction before and after the damping hole.
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| CN2010102045850A CN101871477B (en) | 2010-06-22 | 2010-06-22 | Intermediate-pressure control two-position variable axial plunger hydraulic motor |
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| CN2010102045850A CN101871477B (en) | 2010-06-22 | 2010-06-22 | Intermediate-pressure control two-position variable axial plunger hydraulic motor |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN87105549A (en) * | 1987-08-15 | 1988-02-10 | 石家庄煤矿机械厂 | Hydraulic control speed changing and governing loop |
| CN101113597A (en) * | 2007-07-27 | 2008-01-30 | 浙江工业大学 | Prime move output torque equalising control device |
| US7430860B2 (en) * | 2004-09-28 | 2008-10-07 | Parker-Hannifin Corporation | Hydrostatic transmission circuit |
| CN101398019A (en) * | 2007-09-30 | 2009-04-01 | 贵州力源液压股份有限公司 | Hydraulic control method of hydraulic motor rotating speed and device thereof |
| CN201339536Y (en) * | 2009-01-20 | 2009-11-04 | 胡世璇 | Current distributor for axial plunger variable hydraulic motor |
| WO2010046209A2 (en) * | 2008-10-20 | 2010-04-29 | Zf Friedrichshafen Ag | Arrangement for hydraulic eccentric adjustment to set a predefined displacement for a hydrostatic motor |
-
2010
- 2010-06-22 CN CN2010102045850A patent/CN101871477B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN87105549A (en) * | 1987-08-15 | 1988-02-10 | 石家庄煤矿机械厂 | Hydraulic control speed changing and governing loop |
| US7430860B2 (en) * | 2004-09-28 | 2008-10-07 | Parker-Hannifin Corporation | Hydrostatic transmission circuit |
| CN101113597A (en) * | 2007-07-27 | 2008-01-30 | 浙江工业大学 | Prime move output torque equalising control device |
| CN101398019A (en) * | 2007-09-30 | 2009-04-01 | 贵州力源液压股份有限公司 | Hydraulic control method of hydraulic motor rotating speed and device thereof |
| WO2010046209A2 (en) * | 2008-10-20 | 2010-04-29 | Zf Friedrichshafen Ag | Arrangement for hydraulic eccentric adjustment to set a predefined displacement for a hydrostatic motor |
| CN201339536Y (en) * | 2009-01-20 | 2009-11-04 | 胡世璇 | Current distributor for axial plunger variable hydraulic motor |
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| EP3385536A1 (en) | 2017-04-07 | 2018-10-10 | Danfoss Power Solutions Inc. | Motor soft shift feature |
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| CN111102260A (en) * | 2018-10-25 | 2020-05-05 | 丹佛斯动力系统有限责任两合公司 | Displacement control device |
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| CN109404510A (en) * | 2018-12-11 | 2019-03-01 | 力源液压（苏州）有限公司 | A kind of fluid power system of engineering truck and its running gear |
| CN110371876A (en) * | 2019-04-26 | 2019-10-25 | 南通力威机械有限公司 | A kind of hydraulic control system of geological winch |
| CN112377382A (en) * | 2020-11-13 | 2021-02-19 | 浙江大学 | Variable axial plunger pump based on proportional pressure reducing valve control |
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