CN109441906A - A kind of Electric-hydraulic Proportional Load Sensor pump and pump valve jointly control servo-system - Google Patents
A kind of Electric-hydraulic Proportional Load Sensor pump and pump valve jointly control servo-system Download PDFInfo
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- CN109441906A CN109441906A CN201811612814.5A CN201811612814A CN109441906A CN 109441906 A CN109441906 A CN 109441906A CN 201811612814 A CN201811612814 A CN 201811612814A CN 109441906 A CN109441906 A CN 109441906A
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
-
- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
-
- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
-
- 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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
- F15B2013/0448—Actuation by solenoid and permanent magnet
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Reciprocating Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
The invention discloses a kind of Electric-hydraulic Proportional Load Sensor pumps and pump valve to jointly control servo-system, the Electric-hydraulic Proportional Load Sensor pump specifically includes that plug, shell, valve pocket, spool, pressure spring, push rod, proportion electro-magnet, returning spring, swash plate and control piston, load sensitive pump export pressure PSWith outer load PLAnd pressure difference variation is kept constant, constant pressure difference can be adjusted during the work time by proportion electro-magnet, and pressure difference governing response is fast, be greatly improved Electric-hydraulic Proportional Load Sensor pump dynamic response.And the pump valve jointly controls servo-system without spill losses, is meeting high frequency sound dynamic characteristic while can greatly improve its working efficiency.
Description
Technical field
The present invention relates to hydraulic servo control system field, in particular to a kind of Electric-hydraulic Proportional Load Sensor pump and pump valve connection
Close control servo-system.
Background technique
Pump valve jointly controls the important branch that servo-system is power-by-wire, it can sufficiently combine pump control servo-system
The advantages of with both valve control servo-systems, and corresponding disadvantage is abandoned, it is a kind of ideal electrohydraulic servo system, therefore be also
The hot spot and focus of international expert research.
Load sensitive pump has manual and automatically controlled two ways at present, wherein for manually load sensitive pump, using hand
It is dynamic to adjust outlet pressure PSWith load pressure PLPressure difference value, cannot achieve remote auto adjust pressure difference.When by initial differential pressure
When being adjusted to the larger value, energy saving purpose cannot achieve；When the initial differential pressure is adjusted to minimum, although can be realized raising
System working efficiency, but because load sensitive pump dynamic responding speed is slower, lead to the Dynamic response that valve control servo-system is not achieved
Purpose.
For automatically controlled load sensitive pump, wherein it uses pressure sensor to acquire load signal, direct by controller
Driving electromagnetic proportional valve output action power is compared with the outlet pressure of load sensitive pump, forms constant pressure difference, constant pressure difference
It is also adjusted in the course of work, but load-sensitive pump discharge pressure is larger, active force is also very big, and electromagnetic proportional valve output action
Power is limited, can not form good accelerating ability, to influence the response speed of adjusting constant pressure difference value, that is, influences load-sensitive
The dynamic response of pump.
Summary of the invention
The object of the present invention is to provide a kind of Electric-hydraulic Proportional Load Sensor pumps and pump valve to jointly control servo-system, to reality
Now make load sensitive pump export pressure PSIt can be with the inlet pressure P of outer load cavityLAnd pressure difference variation is kept constant, it is permanent
Level pressure difference can be adjusted during the work time by proportion electro-magnet, and pressure difference governing response is fast, and it is negative to be greatly improved electric-hydraulic proportion
Sensitive pump dynamic response is carried, further, pump valve jointly controls servo-system can when response requires lower without spill losses
It adjusting Electric-hydraulic Proportional Load Sensor pump and keeps minimum differntial pressure, energy-saving efficiency is up to pump control servo-system, when responding more demanding,
Adjustable Electric-hydraulic Proportional Load Sensor pump keeps higher differential pressure, and dynamic response is up to valve control servo-system, and most of servo system
System requires the dynamic response higher period shorter, therefore the pump valve jointly controls servo-system and meeting high frequency sound dynamic characteristic
Its working efficiency can be greatly improved simultaneously, is a kind of ideal electrohydraulic servo system.
In order to achieve the goal above, the invention is realized by the following technical scheme:
A kind of Electric-hydraulic Proportional Load Sensor pump includes: plug 1, shell 4, valve pocket 6, spool 8, pressure spring 10, push rod
11, proportion electro-magnet 12；The valve pocket 6 is located inside the shell 4, close to the first end of the shell, in the shell 4
Side wall interference fit, the spool 8 are located inside the valve pocket 6；The pressure spring 10 and the push rod 11 are successively set on
Inside the shell 4, close to the second end of the shell 4, the pressure spring 10 be located at the spool 8 and the push rod 11 it
Between；The proportion electro-magnet 12 is arranged at the second end of the shell 4, is fixedly connected with the push rod 11, the ratio electricity
Magnet 12 is also coated with shell, and the shell is connect with the end of the second end of the shell 4, the plug 1 and the shell
The end of the first end of body 4 connects, for cooperating with the shell, by the valve pocket 6 and spool 8, pressure spring 10 and push rod
11 are sealed in inside the shell 4；The Electric-hydraulic Proportional Load Sensor pump further includes the high pressure chest outside the shell 4
17, low pressure chamber 16 and the first control chamber 18；Before the valve pocket 6 is provided with symmetrically on the end face of the first end of the shell 4
Window 2 is set, so that the outlet pressure Ps of load sensitive pump flows into the first end of the spool 8；It is equipped at intervals on the valve pocket 6
Oil sources window 3 controls window 5 and oil return window 7, and the oil sources window 3, control window 5 and oil return window are corresponded on the shell 4
Mouth offers first through hole, the second through-hole and third through-hole at 7 positions respectively；The oil sources window 3 is logical by described first
Hole is connected to the high pressure chest 17, and the control window 5 is connected to by second through-hole with first control chamber 18, described
Oil return window 7 is connected to by the third through-hole with the low pressure chamber 16；The shell 4 is additionally provided with outer load connector, outer negative
It carries through the outer load connector and the valve pocket 6 and second end and the shell 4 close to spool 8 and ratio electricity
The outer load cavity connection of the shell composition of magnet 12, the inlet pressure of the outer load cavity are PL；The spool 8 is equipped with difference
With the oil sources window 3, control window 5 and matched first convex shoulder structure of oil return window 7, first convex shoulder structure controls institute
The opening and closing stated oil sources window 3, control window 5 and oil return window 7；The proportion electro-magnet 12 drives the push rod 11 to adjust
It saves the decrement of the pressure spring 10 and then drives the spool 8 along the central axis direction of the shell 4 to move back
It is dynamic, until the outlet pressure Ps of the load sensitive pump is equal to the inlet pressure P of the outer load cavityLThe sum of with constant pressure difference,
So that first convex shoulder structure closes the control window 5.
Further, multiple second convex shoulder structures are equipped at intervals on the outside of the valve pocket 6, second convex shoulder structure
Gap and 4 inner sidewall of shell are respectively formed with oil sources chamber, the second control chamber and oil back chamber, the oil sources window 3 with it is described
The connection of oil sources chamber, control window 5 are connected to second control chamber, and the oil return window 7 is connected to the oil back chamber.
Further, the number of every kind of oil sources window 3, control window 5 and oil return window 7 is one or more.
Further, the Electric-hydraulic Proportional Load Sensor pump also includes swash plate 14, and is revolved for controlling the swash plate 14
Rotate into and control the high pressure chest 17, low pressure chamber 16 and the first control chamber 18 cavity pressure returning spring 13.
Further, the swash plate 14 is equipped with for adjusting the low pressure chamber 16, high pressure chest 17 and the first control chamber respectively
The first of 18 cavity volumes adjusts section, the second adjusting section and third and adjusts section, and described first, which adjusts section and second, adjusts Duan Kexuan
The third that is mounted on turned is adjusted in section.
Further, the Electric-hydraulic Proportional Load Sensor pump is additionally provided with control piston 15, is nested in first control
On chamber 18, and it is connect with the three adjustings section；The control piston 15 moves back and forth, so that the cavity of first control chamber 18
Volume increaseds or decreases, and then compresses or stretch the returning spring 13.
Further, as the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSWith the inlet pressure P of the outer load cavityL
When keeping constant pressure difference, the spool 8 is in equilbrium position, i.e., the second convex shoulder structure of the described spool 8 closes the control just
When valve port 5 processed, the swash plate 14 keeps default inclination angle, and the constant pressure difference value is determined by the pressure spring 10 at this time；
As the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSGreater than the inlet pressure P of the outer load cavityLWith the perseverance
When the sum of differential pressure value, the spool 8 is mobile to the second end of the shell 4, and the oil sources window 3 is connected to control window 5,
First control chamber, the 18 operating pressure PkIt increases, pushes control piston 15 mobile, so that the third of the swash plate 14 adjusts section
Clockwise oscillation, 14 inclination angle of swash plate are less than the default inclination angle, the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSUnder
Drop, until the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSEqual to the inlet pressure P of the outer load cavityLWith constant pressure difference
The sum of when, the spool 8 is restored to equilbrium position, and the first convex shoulder structure of the spool 8 recloses the control valve port 5,
Swash plate 14 is restored to default inclination angle.As the outlet pressure P of Electric-hydraulic Proportional Load Sensor pumpSLess than the outer load cavity into
Mouth pressure PLWhen with the sum of the constant pressure difference value, the spool 8 is mobile to the first end of the shell 4, the control window 5
It is connected to oil return window 7, the operating pressure P of first control chamber 18kIt reduces, pushes control piston 15 mobile, the reply
Spring 13 pushes 14 counter-clockwise swing of swash plate, and 14 inclination angle of swash plate increases, and the Electric-hydraulic Proportional Load Sensor pump goes out
Mouth pressure PSRise, until the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSEqual to the inlet pressure P of the outer load cavityL
When with the sum of constant pressure difference, when the spool 8 restores to equilbrium position, the first convex shoulder structure of the spool 8 recloses control
When valve port 5 processed, the swash plate 14 restores to the position at default inclination angle.
Further, the pressure spring 10 is for adjusting the constant pressure difference；
When voltage that the proportion electro-magnet 12 is passed through increases, 12 iron core of proportion electro-magnet to the shell the
One end is mobile, and the pre compressed magnitude of the pressure spring 10 increases, so that the constant pressure difference value increases；When the proportion electro-magnet
12 are passed through voltage when reducing, and 12 iron core of proportion electro-magnet is mobile to the second end of the shell, and 10 pre compressed magnitude of pressure spring subtracts
It is small, so that the constant pressure difference value reduces；When the proportion electro-magnet 12 be passed through voltage it is constant when, the pressure spring 10
Pre compressed magnitude is constant, and the constant pressure difference value is constant.
On the other hand, a kind of pump valve jointly controls servo-system, includes: motor 100, electric-hydraulic proportion as described above are negative
Carry sensitive pump, coarse filter 400, overflow valve 600, fuel tank 700, check valve 800, fine filter 900, electrohydraulic servo valve 101, shuttle
Valve 110, hydraulic cylinder 120, position sensor 130 and controller 140；The motor 100 is for driving the electric-hydraulic proportion negative
Carry sensitive pump；The outlet of Electric-hydraulic Proportional Load Sensor pump is connected to described electro-hydraulic watch via check valve 800 with fine filter 900
Take the oil inlet of valve 101；The outlet of fuel tank 700 described in the inlet communication of the Electric-hydraulic Proportional Load Sensor pump；The electro-hydraulic ratio
The proportion electro-magnet 12 of example load sensitive pump is connect with the controller 140；The oil return opening of the electrohydraulic servo valve 101 is connected to institute
State the entrance of fuel tank 700；The first control mouth and the second control mouth of the electrohydraulic servo valve 101 are respectively communicated with the hydraulic cylinder
120 first chamber and second chamber；The first of the shuttle valve 110 compares input port and second and compares input port and be respectively communicated with liquid
The first chamber and second chamber of cylinder pressure 120；The pressure signal delivery outlet and the Electric-hydraulic Proportional Load Sensor of the shuttle valve 110
The outer load cavity connection of pump；The outlet of the coarse filter 400 is loaded quick by the first hydraulic runner connection electric-hydraulic proportion
Feel the import of pump；The entrance of the coarse filter 400 is connected to the outlet of the fuel tank 700 by the second hydraulic runner；It is described to overflow
The entrance for flowing valve 600 is connected to the outlet of the Electric-hydraulic Proportional Load Sensor pump by the hydraulic runner of third；The overflow valve 600
Outlet is connected to the entrance of the fuel tank 700 by the 4th hydraulic runner；The position sensor 130 is for acquiring hydraulic cylinder 120
Piston rod displacement；The position sensor 130 is electrically connected the controller 140；The output end of the controller 140
It is electrically connected the control terminal of electrohydraulic servo valve 101, for controlling 101 flow of electrohydraulic servo valve.
Further, when pump valve, which jointly controls servo-system, requires response speed lower, it is negative to adjust the electric-hydraulic proportion
The proportion electro-magnet 12 for carrying sensitive pump reduces the pre compressed magnitude of the pressure spring 10, presets so that constant pressure difference reaches first
Value；When pump valve, which jointly controls servo-system, requires response speed higher, the ratio of the Electric-hydraulic Proportional Load Sensor pump is adjusted
Electromagnet 12 increases 10 pre compressed magnitude of pressure spring, so that constant pressure difference reaches the second preset value, first preset value
Less than second preset value.
The present invention has following technical effect that
The present invention can make load sensitive pump export pressure PSIt can be with the inlet pressure P of outer load cavityLAnd it keeps
Constant pressure difference variation, constant pressure difference can be adjusted during the work time by proportion electro-magnet, and pressure difference governing response is fast, can be significantly
It improves Electric-hydraulic Proportional Load Sensor and pumps dynamic response, further, pump valve jointly controls servo-system without spill losses, is responding
It is required that Electric-hydraulic Proportional Load Sensor pump is adjusted and keeps minimum differntial pressure, energy-saving efficiency is up to pump control servo-system, in sound when lower
When answering more demanding, be adjusted Electric-hydraulic Proportional Load Sensor pump keep higher differential pressure, dynamic response up to valve control servo-system, and
Most of servo-system requires the dynamic response higher period shorter, therefore the pump valve jointly controls servo-system and meeting height
Frequency response dynamic characteristic can greatly improve its working efficiency simultaneously, be a kind of ideal electrohydraulic servo system.
Detailed description of the invention
Fig. 1 is a kind of section signal of the primary structure for Electric-hydraulic Proportional Load Sensor pump that one embodiment of the invention provides
Figure；
Fig. 2 is the primary structure schematic diagram that a kind of pump valve that one embodiment of the invention provides jointly controls servo-system.
Drawing reference numeral explanation: 1 plug, 2 preposition windows, 3 oil sources valve ports, 4 shells, 5 control valve ports, 6 valve pockets, 7 oil return valves
Mouth, 8 spools, 9 load windows, 10 pressure springs, 11 push rods, 12 proportion electro-magnets, 13 returning springs, 14 swash plates, 15 controls are lived
Plug, 16 low pressure chambers, 17 high pressure chests, 18 control chambers.
Specific embodiment
The present invention is further elaborated by the way that a preferable specific embodiment is described in detail below in conjunction with attached drawing.
As shown in Figure 1, a kind of Electric-hydraulic Proportional Load Sensor pump provided in this embodiment, comprising: plug 1, shell 4, valve pocket
6, spool 8, pressure spring 10, push rod 11, proportion electro-magnet 12, returning spring 13, swash plate 14 and control piston 15；The valve pocket
6 are located inside the shell 4, close to the first end of the shell, are interference fitted with 4 inner sidewall of shell, the spool 8
Inside the valve pocket 6；The pressure spring 10 and the push rod 11 are successively set on inside the shell 4, close to the shell
The second end of body 4, the pressure spring 10 is between the spool 8 and the push rod 11；The proportion electro-magnet 12 is arranged
It at the second end of the shell 4, is fixedly connected with the push rod 11, the proportion electro-magnet 12 is also coated with shell, institute
It states shell to connect with the end of the second end of the shell 4, the plug 1 is connect with the end of the first end of the shell 4, is used
Cooperate in the shell, the valve pocket 6 and spool 8, pressure spring 10 and push rod 11 are sealed in inside the shell 4；Institute
Stating Electric-hydraulic Proportional Load Sensor pump further includes high pressure chest 17, low pressure chamber 16 and the first control chamber 18 outside the shell 4；
The valve pocket 6 is provided with symmetrical preposition window 2 on the end face of the first end of the shell 4, so that load sensitive pump goes out
Mouth pressure Ps flows into the first end of the spool 8；Oil sources window 3, control window 5 and oil return are equipped at intervals on the valve pocket 6
Window 7, corresponds to that offer first respectively at the oil sources window 3, control window 5 and 7 position of oil return window logical on the shell 4
Hole, the second through-hole and third through-hole；The oil sources window 3 is connected to by the first through hole with the high pressure chest 17, described
Control window 5 is connected to by second through-hole with first control chamber 18, and the oil return window 7 passes through the third through-hole
It is connected to the low pressure chamber 16；The shell 4 is additionally provided with outer load connector, and outer load passes through the outer load connector and institute
State the outer load cavity of the shell composition of valve pocket 6 and second end and the shell 4 and the proportion electro-magnet 12 close to spool 8
Connection, the inlet pressure of the outer load cavity are PL；The spool 8 be equipped with respectively with the oil sources window 3, control window 5
With matched first convex shoulder structure of oil return window 7, first convex shoulder structure controls the oil sources window 3, control window 5 and returns
The opening and closing of oily window 7；The proportion electro-magnet 12 drives the push rod 11 to adjust the decrement of the pressure spring 10
And then the spool 8 is driven to move back and forth along the central axis direction of the shell 4, until the load sensitive pump goes out
Mouth pressure Ps is equal to the inlet pressure P of the outer load cavityLThe sum of with constant pressure difference, so that first convex shoulder structure closes institute
State control window 5.
Multiple second convex shoulder structures, the gap of second convex shoulder structure and institute are equipped at intervals on the outside of the valve pocket 6
It states 4 inner sidewall of shell and is respectively formed with oil sources chamber, the second control chamber and oil back chamber, the oil sources window 3 connects with the oil sources chamber
Logical, control window 5 is connected to second control chamber, and the oil return window 7 is connected to the oil back chamber.
The number of every kind of oil sources window 3, control window 5 and oil return window 7 is one or more.
The Electric-hydraulic Proportional Load Sensor pump also includes swash plate 14, and rotates control in turn for controlling the swash plate 14
The high pressure chest 17, low pressure chamber 16 and the first control chamber 18 cavity pressure returning spring 13.
The swash plate 14 is equipped with for adjusting 18 cavity volume of the low pressure chamber 16, high pressure chest 17 and the first control chamber respectively
First adjust section, second adjust section and third and adjust section, the first adjusting section and the second adjusting section are rotatably mounted to
The third is adjusted in section.
The Electric-hydraulic Proportional Load Sensor pump is additionally provided with control piston 15, is nested in first control chamber 18, and
It is connect with the three adjustings section；The control piston 15 moves back and forth, so that the cavity volume of first control chamber 18 increases
Or reduce, and then compress or stretch the returning spring 13.
As the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSWith the inlet pressure P of the outer load cavityLKeep constant pressure
When poor, the spool 8 is in equilbrium position, i.e., when the second convex shoulder structure of the described spool 8 closes the control valve port 5 just,
The swash plate 14 keeps default inclination angle, and the constant pressure difference value is determined by the pressure spring 10 at this time.
As the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSGreater than the inlet pressure P of the outer load cavityLWith the perseverance
When the sum of differential pressure value, the spool 8 is mobile to the second end of the shell 4, and the oil sources window 3 is connected to control window 5,
First control chamber, the 18 operating pressure PkIt increases, pushes control piston 15 mobile, so that the third of the swash plate 14 adjusts section
Clockwise oscillation, 14 inclination angle of swash plate are less than the default inclination angle, the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSUnder
Drop, until the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSEqual to the inlet pressure P of the outer load cavityLWith constant pressure difference
The sum of when, the spool 8 is restored to equilbrium position, and the first convex shoulder structure of the spool 8 recloses the control valve port 5,
Swash plate 14 is restored to default inclination angle.As the outlet pressure P of Electric-hydraulic Proportional Load Sensor pumpSLess than the outer load cavity into
Mouth pressure PLWhen with the sum of the constant pressure difference value, the spool 8 is mobile to the first end of the shell 4, the control window 5
It is connected to oil return window 7, the operating pressure P of first control chamber 18kIt reduces, pushes control piston 15 mobile, the reply
Spring 13 pushes 14 counter-clockwise swing of swash plate, and 14 inclination angle of swash plate increases, and the Electric-hydraulic Proportional Load Sensor pump goes out
Mouth pressure PSRise, until the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSEqual to the inlet pressure P of the outer load cavityL
When with the sum of constant pressure difference, when the spool 8 restores to equilbrium position, the first convex shoulder structure of the spool 8 recloses control
When valve port 5 processed, the swash plate 14 restores to the position at default inclination angle.
The pressure spring 10 is for adjusting the constant pressure difference；When the voltage that the proportion electro-magnet 12 is passed through increases
When, 12 iron core of proportion electro-magnet is mobile to the first end of the shell, and the pre compressed magnitude of the pressure spring 10 increases, and makes
The constant pressure difference value is obtained to increase；When the proportion electro-magnet 12, which is passed through voltage, to be reduced, 12 iron core of proportion electro-magnet is to described
The second end of shell is mobile, and 10 pre compressed magnitude of pressure spring reduces, so that the constant pressure difference value reduces；When the ratio electromagnetism
Iron 12 be passed through voltage it is constant when, the pre compressed magnitude of the pressure spring 10 is constant, and the constant pressure difference value is constant.
The outlet pressure of the low pressure chamber 16 is Pt, high pressure chest 17 outlet pressure be Ps (Electric-hydraulic Proportional Load Sensor pump
Outlet pressure PS) and the first control chamber 18 outlet pressure be Pk, the inlet pressure of outer load cavity is PL(outer load pressure PL)。
In the present embodiment, the left end for defining described Fig. 1 is first end, and the right end of described Fig. 1 is second end.
The working principle of the present embodiment is: as Electric-hydraulic Proportional Load Sensor pump discharge pressure PSWith load pressure PLKeep permanent
When level pressure difference, the spool 8 is in equilbrium position, i.e., the first convex shoulder structure of the described spool 8 closes the control valve port 5 just
When, the swash plate 14 keeps default inclination angle, and the constant pressure difference value is determined by the pressure spring 10 at this time.When the electric-hydraulic proportion
Load-sensitive pump discharge pressure PSGreater than outer load pressure PLWhen with the sum of the constant pressure difference value, the spool 8 is moved right,
The oil sources window 3 is connected to control window 5, and 18 operating pressure of the first control chamber increases, and pushes 14 up time of swash plate
Needle is swung, and 14 inclination angle of swash plate is less than the default inclination angle, and the outlet oil liquid flow of the Electric-hydraulic Proportional Load Sensor pump subtracts
It is small, i.e., the described outlet pressure PSDecline, until the outlet pressure PSWith the outer load pressure PLIt is kept with the sum of constant pressure difference
When equal, the spool 8 is restored to equilbrium position, and the first convex shoulder structure of the spool 8 closes the control valve port 5 just,
Swash plate 14 is restored to default inclination angle.Similarly, as the outlet pressure P of Electric-hydraulic Proportional Load Sensor pumpSLess than outer load pressure PL
When with the sum of constant pressure difference value, the spool 8 is moved downward, and the control window 5 is connected to oil return window 7, first control
The operating pressure of chamber 18 processed reduces, and the returning spring 13 pushes 14 counter-clockwise swing of swash plate, and 14 inclination angle of swash plate increases
Greatly, the oil liquid flow of the outlet of the Electric-hydraulic Proportional Load Sensor pump increases, i.e., the described outlet pressure PSRise, until it is described go out
Mouth pressure PSWith outer load pressure PLWhen equal with the sum of constant pressure difference, when the spool 8 restores to equilbrium position, the spool 8
The first convex shoulder structure lucky closed control valve mouth 5 when, the swash plate 14 restores to the position at default inclination angle.
Therefore when 10 pre compressed magnitude of pressure spring it is constant, i.e., proportion electro-magnet 12 be passed through voltage it is constant when, Novel electric ratio
Load-sensitive pump discharge pressure PSWith load pressure PLAlways it is able to maintain constant pressure difference.When proportion electro-magnet 12 is passed through voltage
When increase, 12 iron core of proportion electro-magnet is moved downward, and 10 pre compressed magnitude of pressure spring increases, and constant pressure difference value increases, i.e., identical
Load pressure PL need bigger pump discharge pressure PS, therefore system throttles lose bigger, work efficiency drop, when ratio electricity
When magnet 12 is passed through voltage reduction, 12 iron core of proportion electro-magnet is moved right, and 10 pre compressed magnitude of pressure spring reduces, constant pressure difference
Value reduces, i.e., identical load pressure PLNeed smaller pump discharge pressure PS, therefore system throttles loss reduces, working efficiency
Rise.
Based on the above embodiment, as shown in Fig. 2, the invention also discloses a kind of pump valves to jointly control servo-system, include:
Motor 100, Electric-hydraulic Proportional Load Sensor pump as described above, coarse filter 400, overflow valve 600, fuel tank 700, check valve
800, fine filter 900, electrohydraulic servo valve 101, shuttle valve 110, hydraulic cylinder 120, position sensor 130 and controller 140；Institute
Motor 100 is stated for driving the Electric-hydraulic Proportional Load Sensor to pump；The outlet of the Electric-hydraulic Proportional Load Sensor pump is via unidirectional
Valve 800 is connected to the oil inlet of the electrohydraulic servo valve 101 with fine filter 900；The import of the Electric-hydraulic Proportional Load Sensor pump
It is connected to the outlet of the fuel tank 700；The proportion electro-magnet 12 and the controller 140 of the Electric-hydraulic Proportional Load Sensor pump connect
It connects；The oil return opening of the electrohydraulic servo valve 101 is connected to the entrance of the fuel tank 700；First control of the electrohydraulic servo valve 101
Mouth and the second control mouth are respectively communicated with the first chamber and second chamber of the hydraulic cylinder 120；The first of the shuttle valve 110 is compared
Compare first chamber and second chamber that input port is respectively communicated with hydraulic cylinder 120 in input port and second；The pressure of the shuttle valve 110
Signal output is connect with the outer load cavity that the Electric-hydraulic Proportional Load Sensor pumps；The outlet of the coarse filter 400 passes through the
One hydraulic runner is connected to the import of the Electric-hydraulic Proportional Load Sensor pump；The entrance of the coarse filter 400 is hydraulic by second
Runner is connected to the outlet of the fuel tank 700；The entrance of the overflow valve 600 is connected to the electric-hydraulic proportion by the hydraulic runner of third
The outlet of load sensitive pump；The outlet of the overflow valve 600 is connected to the entrance of the fuel tank 700 by the 4th hydraulic runner；Institute
State the displacement of piston rod of the position sensor 130 for acquiring hydraulic cylinder 120；The position sensor 130 is electrically connected institute
State controller 140；The control terminal of the output end electrical connection electrohydraulic servo valve 101 of the controller 140, for controlling the electricity
101 flow of hydraulic servo.
When pump valve, which jointly controls servo-system, requires response speed lower, the Electric-hydraulic Proportional Load Sensor pump is adjusted
Proportion electro-magnet 12 reduces the pre compressed magnitude of the pressure spring 10, so that constant pressure difference reaches the first preset value (constant pressure
The minimum value of difference), at this point, pump valve, which jointly controls the servo-system pressure loss, reaches minimum value, although pump valve jointly controls servo
System dynamic response slows down, but pump valve jointly controls servo-system working efficiency close to pump control servo-system.
When pump valve, which jointly controls servo-system, requires response speed higher, the Electric-hydraulic Proportional Load Sensor pump is adjusted
Proportion electro-magnet 12 increases 10 pre compressed magnitude of pressure spring, so that constant pressure difference reaches the second preset value, described first is pre-
If value is less than second preset value.I.e. when constant pressure difference increases to certain value, although at this point, pump valve jointly controls servo-system
The pressure loss increase, but pump valve jointly controls the dynamic characteristic of servo-system and is fully able to reach valve control servo-system dynamic frequency
It rings, and most of servo-system requires the frequency response higher period shorter, therefore pump valve jointly controls servo-system overall work effect
Rate is very high, and to reach valve control servo-system in demand horizontal for Dynamic response, is that a kind of ideal pump valve jointly controls
Servo-system.
It is discussed in detail although the contents of the present invention have passed through above preferred embodiment, but it should be appreciated that above-mentioned
Description is not considered as limitation of the present invention.After those skilled in the art have read above content, for of the invention
A variety of modifications and substitutions all will be apparent.Therefore, protection scope of the present invention should be limited to the appended claims.
Claims (10)
1. a kind of Electric-hydraulic Proportional Load Sensor pump, characterized by comprising: plug (1), shell (4), valve pocket (6), spool (8),
Pressure spring (10), push rod (11), proportion electro-magnet (12)；The valve pocket (6) is located at the shell (4) inside, close to described
The first end of shell (4) is interference fitted with the shell (4) inner sidewall, and it is internal that the spool (8) is located at the valve pocket (6)；
The pressure spring (10) and the push rod (11) are successively set on the shell (4) inside, close to the shell (4)
Second end, the pressure spring (10) is between the spool (8) and the push rod (11)；
The proportion electro-magnet (12) is arranged at the second end of the shell (4), is fixedly connected with the push rod 11, the ratio
Example electromagnet (12) is also coated with shell, and the shell is connect with the end of the second end of the shell (4), the plug
(1) connect with the end of the first end of the shell (4), for cooperating with the shell, by the valve pocket (6) and spool (8),
It is internal that pressure spring (10) and push rod (11) are sealed in the shell (4)；
Electric-hydraulic Proportional Load Sensor pump further include positioned at the shell (4) external high pressure chest (17), low pressure chamber (16) and
First control chamber (18)；
The valve pocket (6) is provided with symmetrical preposition window (2) on the end face of the first end of the shell (4), so that load
The outlet pressure Ps of sensitive pump flows into the end close to the shell (4) first end of the spool (8)；
It is equipped at intervals with oil sources window (3) on the valve pocket (6), controls window (5) and oil return window (7), on the shell (4)
The corresponding oil sources window (3), control offer first through hole, the second through-hole at window (5) and oil return window (7) position respectively
And third through-hole；
The oil sources window (3) is connected to by the first through hole with the high pressure chest (17), and the control window (5) passes through institute
It states the second through-hole to be connected to first control chamber (18), the oil return window (7) passes through the third through-hole and the low pressure
Chamber (16) connection；
The shell (4) is additionally provided with outer load connector, and outer load is by the outer load connector and the valve pocket (6) and leans on
The second end of nearly spool (8) is connected to the outer load cavity that the shell of the shell (4) and the proportion electro-magnet (12) forms,
The inlet pressure of the outer load cavity is PL；
The spool (8) be equipped with respectively with the oil sources window (3), control window (5) and oil return window (7) matched first
Convex shoulder structure, first convex shoulder structure control the opening of the oil sources window (3), control window (5) and oil return window (7) with
It closes；
The proportion electro-magnet (12) drives the push rod (11) to adjust the decrement of the pressure spring (10) and then drives institute
It states the spool (8) to move back and forth along the central axis direction of the shell (4), until the outlet pressure of the load sensitive pump
Ps is equal to the inlet pressure P of the outer load cavityLThe sum of with constant pressure difference, so that first convex shoulder structure closes the control
Window (5).
2. Electric-hydraulic Proportional Load Sensor pump as described in claim 1, which is characterized in that
Be equipped at intervals with multiple second convex shoulder structures on the outside of the valve pocket (6), the gap of second convex shoulder structure with it is described
Shell (4) inner sidewall is respectively formed with oil sources chamber, the second control chamber and oil back chamber, the oil sources window (3) and the oil sources chamber
Connection, control window (5) are connected to second control chamber, and the oil return window (7) is connected to the oil back chamber.
3. Electric-hydraulic Proportional Load Sensor pump as claimed in claim 1 or 2, which is characterized in that every kind of oil sources window (3),
The number for controlling window (5) and oil return window (7) is one or more.
4. Electric-hydraulic Proportional Load Sensor pump as claimed in claim 3, which is characterized in that the Electric-hydraulic Proportional Load Sensor pump is also
Comprising swash plate (14), and for control the swash plate (14) rotate so that control the high pressure chest (17), low pressure chamber (16) and
The returning spring (13) of the cavity pressure of first control chamber (18).
5. Electric-hydraulic Proportional Load Sensor pump as claimed in claim 4, which is characterized in that the swash plate (14) is equipped with for distinguishing
It adjusts the first of the low pressure chamber (16), high pressure chest (17) and the first control chamber (18) cavity volume and adjusts section, the second adjusting section
Section is adjusted with third, the first adjusting section and the second adjusting section are rotatably mounted to the third and adjust in section.
6. Electric-hydraulic Proportional Load Sensor pump as claimed in claim 5, which is characterized in that the Electric-hydraulic Proportional Load Sensor pump is also
It equipped with control piston (15), is nested on first control chamber (18), and is connect with the three adjustings section；The control is lived
It fills in (15) to move back and forth, so that the cavity volume of second control chamber (18) increaseds or decreases, so that the reply bullet
Spring (13) compression or stretching, extension.
7. Electric-hydraulic Proportional Load Sensor pump as claimed in claim 6, which is characterized in that
As the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSWith the inlet pressure P of the outer load cavityLKeep constant pressure difference
When, the spool (8) is in equilbrium position, i.e., the second convex shoulder structure of the described spool (8) closes the control valve port (5) just
When, the swash plate (14) keeps default inclination angle, and the constant pressure difference value is determined by the pressure spring (10) at this time；
As the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSGreater than the inlet pressure P of the outer load cavityLWith the constant pressure
When the sum of difference, the second end of spool (8) the Xiang Suoshu shell (4) is mobile, the oil sources window (3) and control window (5)
Connection, the first control chamber (18) operating pressure PkIt increases, pushes control piston (15) mobile, so that the swash plate (14)
Third adjusts section clockwise oscillation, and swash plate (14) inclination angle is less than the default inclination angle, the Electric-hydraulic Proportional Load Sensor pump
Outlet pressure PSDecline, until the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSEqual to the inlet pressure of the outer load cavity
PLWhen with the sum of constant pressure difference, the spool (8) is restored to equilbrium position, and the first convex shoulder structure of the spool (8) seals again
The control valve port (5) is closed, swash plate (14) is restored to default inclination angle；
As the outlet pressure P of Electric-hydraulic Proportional Load Sensor pumpSLess than the inlet pressure P of the outer load cavityLWith it is described constant
When the sum of pressure difference, the first end of spool (8) the Xiang Suoshu shell (4) is mobile, the control window (5) and oil return window
(7) it is connected to, the operating pressure P of second control chamber (18)kIt reduces, pushes control piston (15) mobile, the returning spring
(13) swash plate (14) counter-clockwise swing is pushed, swash plate (14) inclination angle increases, the Electric-hydraulic Proportional Load Sensor pump
Outlet pressure PSRise, until the Electric-hydraulic Proportional Load Sensor pump discharge pressure PSEqual to the inlet pressure of the outer load cavity
PLWhen with the sum of constant pressure difference, when the spool (8) is restored to equilbrium position, the first convex shoulder structure of the spool (8) is again
When closed control valve mouth (5), the swash plate (14) is restored to the position at default inclination angle.
8. Electric-hydraulic Proportional Load Sensor pump as claimed in claim 7, which is characterized in that the pressure spring (10) is for adjusting
The constant pressure difference；
When voltage that the proportion electro-magnet (12) is passed through increases, proportion electro-magnet (12) iron core to the shell the
One end is mobile, and the pre compressed magnitude of the pressure spring (10) increases, so that the constant pressure difference value increases；When the ratio electromagnetism
When iron (12) is passed through voltage reduction, proportion electro-magnet (12) iron core is mobile to the second end of the shell, and pressure spring (10) is pre-
Decrement reduces, so that the constant pressure difference value reduces；When the proportion electro-magnet (12) be passed through voltage it is constant when, the tune
The pre compressed magnitude of pressing spring (10) is constant, and the constant pressure difference value is constant.
9. a kind of pump valve jointly controls servo-system, characterized by comprising: any in motor (100), such as claim 1~8
The pump of Electric-hydraulic Proportional Load Sensor described in one, coarse filter (400), overflow valve (600), fuel tank (700), check valve (800),
Fine filter (900), electrohydraulic servo valve (101), shuttle valve (110), hydraulic cylinder (120), position sensor (130) and controller
(140)；
The motor (100) is for driving the Electric-hydraulic Proportional Load Sensor to pump；
The outlet of Electric-hydraulic Proportional Load Sensor pump is connected to described electro-hydraulic watch via check valve (800) with fine filter (900)
Take the oil inlet of valve (101)；
The outlet of fuel tank (700) described in the inlet communication of the Electric-hydraulic Proportional Load Sensor pump；
The proportion electro-magnet (12) of the Electric-hydraulic Proportional Load Sensor pump is connect with the controller (140)；
The oil return opening of the electrohydraulic servo valve (101) is connected to the entrance of the fuel tank (700)；
The first control mouth and the second control mouth of the electrohydraulic servo valve (101) are respectively communicated with the first of the hydraulic cylinder (120)
Chamber and second chamber；
The first of the shuttle valve (110) compares input port and second compares the first chamber that input port is respectively communicated with hydraulic cylinder (120)
Room and second chamber；
The pressure signal delivery outlet of the shuttle valve (110) is connect with the outer load cavity that the Electric-hydraulic Proportional Load Sensor pumps；
The outlet of the coarse filter (400) is connected to the import of the Electric-hydraulic Proportional Load Sensor pump by the first hydraulic runner；
The entrance of the coarse filter (400) is connected to the outlet of the fuel tank (700) by the second hydraulic runner；
The entrance of the overflow valve (600) is connected to the outlet of the Electric-hydraulic Proportional Load Sensor pump by the hydraulic runner of third；
The outlet of the overflow valve (600) is connected to the entrance of the fuel tank (700) by the 4th hydraulic runner；
The position sensor (130) is used to acquire the displacement of the piston rod of hydraulic cylinder (120)；
The position sensor (130) is electrically connected the controller (140)；
The control terminal of output end electrical connection electrohydraulic servo valve (101) of the controller (140), for controlling described electro-hydraulic watch
Take valve (101) flow.
10. pump valve as claimed in claim 9 jointly controls servo-system, which is characterized in that
When pump valve, which jointly controls servo-system, requires response speed lower, the ratio of the Electric-hydraulic Proportional Load Sensor pump is adjusted
Electromagnet (12) reduces the pre compressed magnitude of the pressure spring (10), so that constant pressure difference reaches the first preset value；Work as pump valve
When jointly controlling servo-system and requiring response speed higher, the proportion electro-magnet (12) of Electric-hydraulic Proportional Load Sensor pump is adjusted
Increase the pressure spring (10) pre compressed magnitude, so that constant pressure difference reaches the second preset value, first preset value is less than institute
State the second preset value.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811612814.5A CN109441906B (en) | 2018-12-27 | 2018-12-27 | Electro-hydraulic proportional load sensitive pump and pump valve combined control servo system |
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| CN201811612814.5A CN109441906B (en) | 2018-12-27 | 2018-12-27 | Electro-hydraulic proportional load sensitive pump and pump valve combined control servo system |
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| CN109441906B CN109441906B (en) | 2020-05-08 |
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| CN110285048A (en) * | 2019-07-19 | 2019-09-27 | 宁波克泰液压有限公司 | Screw thread inserting type speed sensitive load control valve |
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|---|---|
| CN109441906B (en) | 2020-05-08 |
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