CN109058188A - A kind of hydrostatic transmission of electromagnetic switch - Google Patents
A kind of hydrostatic transmission of electromagnetic switch Download PDFInfo
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- CN109058188A CN109058188A CN201811036313.7A CN201811036313A CN109058188A CN 109058188 A CN109058188 A CN 109058188A CN 201811036313 A CN201811036313 A CN 201811036313A CN 109058188 A CN109058188 A CN 109058188A
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- valve
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- way
- pump
- hydraulic
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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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
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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
- F15B13/16—Special measures for feedback, e.g. by a follow-up device
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
Abstract
A kind of hydrostatic transmission of electromagnetic switch, wherein, unidirectional variable pump and two-way variable displacement plunger pump mechanical series, and the same transmission shaft driven using the same power source is provided between unidirectional variable pump and two-way variable displacement plunger pump, there are two the main hydraulic fluid ports and two secondary hydraulic fluid ports for connecting with solenoid directional control valve oil inlet for setting on two-way variable displacement plunger pump；Main hydraulic fluid port and two secondary hydraulic fluid ports there are two being arranged on hydraulic motor for being connect with solenoid directional control valve oil outlet, and one way component and high pressure kicks component are parallel on two-way variable displacement plunger pump, two-way variable displacement plunger pump pump oil supplies hydraulic motor through solenoid directional control valve, to change the steering of hydraulic motor by the output commutation of two-way variable displacement plunger pump itself, it can also be under the output state for not changing two-way variable displacement plunger pump, by commutation magnet control solenoid directional control valve commutation, to realize the hydrostatic transmissions of electromagnetic switch.
Description
Technical field
The present invention relates to gear technical field more particularly to a kind of hydrostatic transmissions of electromagnetic switch.
Background technique
The endless-track vehicle speed changer of double-current (double power flow) input power, generalling use two sets of planetary gear mechanisms makes speed change
Converge after the power of mechanism input is in parallel with the power that steering mechanism inputs, the power of gear input is by planetary gear mechanism
Gear ring or sun gear input, steering mechanism input power by planetary gear mechanism sun gear or gear ring input, after converging
Power exported by planet carrier.In split path transmission scheme, inputted if turning to input power using hydrostatic stepless speed change device,
Then turning radius can consecutive variations, steering angular velocity and steering mechanism input revolving speed proportion relation, turn to precisely, spirit
Living, superior performance；But the output rotary speed direction of the hydrostatic stepless speed change device only bidirectional variable with hydrostatic variable speed
Oil pump swash plate direction is related, during steering operation, as long as the direction of rotation of bidirectional variable oil pump swash plate is constant, and hydraulic motor
Direction of rotation will not both become, after power double fluid converges, the steering of advance and the reversing of endless-track vehicle rule is opposite, it may be assumed that phase
With steering operation cause and advance when turn to is turned to the right when then moving back to the left, when advance turns to the right turns left when then moving back
To so as to cause operating difficulties, or even there is safety accident.Meanwhile when hydrostatic stepless speed change device is dynamic as what is turned to
When power inputs, since only during steering, hydrostatic stepless speed change device just works, at this time system hydraulic oil displacement
Power consumption penalty is big, and the closed circuit of hydrostatic stepless speed change device is sensitive to the raising of oil temperature.
Summary of the invention
Technical problem solved by the invention is to provide a kind of hydrostatic transmission of electromagnetic switch, above-mentioned to solve
Disadvantage in background technique.
Technical problem solved by the invention is realized using following technical scheme:
A kind of hydrostatic transmission of electromagnetic switch, including hydraulic motor, fuel tank, two-way variable displacement plunger pump, low pressure are overflow
Flow valve, filter assemblies, unidirectional variable pump, solenoid directional control valve, commutation electromagnet and pilot operated directional control valve, wherein unidirectional variable pump with
Two-way variable displacement plunger pump mechanical series, and same transmission shaft is provided between unidirectional variable pump and two-way variable displacement plunger pump, it adopts
It is driven with the same power source, there are two the main hydraulic fluid ports for connecting with solenoid directional control valve oil inlet for setting on two-way variable displacement plunger pump
With two secondary hydraulic fluid ports, two main hydraulic fluid ports can it is fuel-displaced can also oil return, two main hydraulic fluid ports of two-way variable displacement plunger pump pass through respectively is
Two oil inlets in road and solenoid directional control valve under the overall leadership connect, and one of pair hydraulic fluid port and second replaces pilot-operated proportional relief valve
Oil outlet connection, another secondary hydraulic fluid port connect radiating subassembly oil inlet, and connect in two-way variable displacement plunger pump with radiating subassembly
Temperature sensor is provided on secondary hydraulic fluid port；Main oil there are two being arranged on hydraulic motor for being connect with solenoid directional control valve oil outlet
Mouthful with two secondary hydraulic fluid ports, two main hydraulic fluid ports can it is fuel-displaced can also oil return, one of pair hydraulic fluid port set by system pipeline with first
The oil outlet connection of pilot-operated proportional relief valve is changed, another secondary hydraulic fluid port connects radiating subassembly by system pipeline, in hydraulic horse
Temperature sensor is provided on up to the secondary hydraulic fluid port connecting with radiating subassembly, two-way variable displacement plunger pump pump oil drives hydraulic motor rotation
Output mechanical energy, commutation electromagnet are mounted on solenoid directional control valve；One way component and high pressure are parallel on two-way variable displacement plunger pump
Overflow assemblies, the oil inlet of unidirectional variable pump and the oil outlet of filter assemblies connect, and the oil inlet of filter assemblies connects fuel tank, single
It is connect simultaneously with the oil inlet in one way component to the oil outlet of variable pump by system pipeline, the oil outlet of unidirectional variable pump is also
It is connected by the oil inlet of system pipeline and low pressure relief valve, the oil outlet of low pressure relief valve connects fuel tank；One-way pump set of variables
Part is connect with unidirectional variable pump, and oil inlet A, the oil inlet B of pilot operated directional control valve and two main hydraulic fluid ports of hydraulic motor connect, hydraulic control
The oil outlet of reversal valve is connected by the oil inlet of system pipeline and electro-hydraulic proportional flow valve, the oil outlet of electro-hydraulic proportional flow valve
It is connect with the oil inlet of flow divider-combiner, there are two oil outlet, one of oil outlet and the second displacements for flow divider-combiner setting
The oil inlet of pilot-operated proportional relief valve connects, and the oil inlet of another oil outlet and the first displacement pilot-operated proportional relief valve connects
It connects.
In the present invention, solenoid directional control valve is two four-way electromagnetic reversing valves, and commutation electromagnet is two four-way commutation electricity
Magnet, pilot operated directional control valve are three-position three way hydraulic reversal valve.
In the present invention, one way component is made of the first check valve with second one-way valve, and the first check valve and second is unidirectionally
The oil inlet of valve is connected by system pipeline, and the first check valve and the oil outlet of second one-way valve are separately connected bidirectional variable column
Fill in two hydraulic fluid ports of pump.
In the present invention, an oil outlet of unidirectional variable pump is single with the first check valve and second simultaneously by system pipeline
It is connected to the oil inlet of valve.
In the present invention, high pressure kicks component is made of the first high-pressure overflow valve and the second high-pressure overflow valve, and first is high
Pressurized overflow valve is in parallel with two-way variable displacement plunger pump again with after the second high-pressure overflow valve reverse parallel connection.
In the present invention, filter assemblies include filter.
In the present invention, radiating subassembly is provided between the oil outlet of low pressure relief valve and fuel tank, low pressure relief valve
The oil outlet of the connection of the oil inlet of oil outlet and radiating subassembly, radiating subassembly connects fuel tank.
In the present invention, the corresponding hydraulic motor master of left hydraulic control mouth connection pilot operated directional control valve oil inlet A of pilot operated directional control valve
Hydraulic fluid port, the corresponding main hydraulic fluid port of hydraulic motor of right hydraulic control mouth connection pilot operated directional control valve oil inlet B of pilot operated directional control valve.
In the present invention, two-way variable displacement plunger pump pump oil supplies hydraulic motor through solenoid directional control valve, and the present apparatus can pass through
The output of two-way variable displacement plunger pump itself commutates to change the steering of hydraulic motor, can also not change two-way variable displacement plunger pump
Under output state, by commutation magnet control solenoid directional control valve commutation, to change the steering of hydraulic motor；
The oil pressure relief of present apparatus mesolow overflow valve is higher than the first displacement pilot-operated proportional relief valve and the second displacement first
The oil pressure relief of conduction proportional pressure control valve, when the oil inlet A for connecting pilot operated directional control valve is higher-pressure region, high pressure oil is through liquid controlled reversing
The left hydraulic control mouth of valve commutates pilot operated directional control valve to left position, at this time the oil inlet B of pilot operated directional control valve and the oil outlet of pilot operated directional control valve
It connects, since the oil pressure relief of low pressure relief valve is higher than the first displacement pilot-operated proportional relief valve and the second displacement pilot proportional
The oil pressure relief of overflow valve, in hydraulic motor oil return, section hydraulic oil is through the first displacement pilot-operated proportional relief valve, electro-hydraulic ratio
Example flow valve shunts after entering flow divider-combiner, and a part enters hydraulic horse after the first displacement pilot-operated proportional relief valve overflow
Up to the intracavitary rear oil return of type to fuel tank, another part enters bidirectional variable column after the second displacement pilot-operated proportional relief valve overflow
The intracavitary rear oil return of plug pump-type is simultaneously back to fuel tank after radiating subassembly radiates, and at the same time, the hydraulic oil that unidirectional variable pump pumps out pushes away
It opens second one-way valve and enters drainback passage, so that supplement is through the first displacement pilot-operated proportional relief valve and the second displacement pilot-operated type ratio
The hydraulic oil of example overflow valve overflow leads to high nip pressures overflowing beyond the first high-pressure overflow valve when hydraulic motor load excessive
When flowing pressure, the pressure oil output of two-way variable displacement plunger pump returned to after the first high-pressure overflow valve overflow two-way variable displacement plunger pump this
When oil return opening, vice versa for hydraulic circuit.
The utility model has the advantages that
1) present invention is provided with solenoid directional control valve, it can be achieved that the output by two-way variable displacement plunger pump itself commutates to change
The steering of hydraulic motor also can pass through the magnet control electromagnetism that commutates under the output state for not changing two-way variable displacement plunger pump
Reversal valve commutation, to realize the hydrostatic transmissions of electromagnetic switch；
2) present invention is changed oil heat dissipation using pilot operated directional control valve to system, and avoiding oil temperature in hydraulic system from increasing leads to failure, and
The amount of changing oil can adjust in real time according to operating condition, avoid blindly changing oil, to cause accidental damage to system job, be effectively reduced simultaneously
Unnecessary power consumption of changing oil；
3) present invention uses variable capacity oil pump, is needed to adjust itself discharge capacity in real time according to system, effectively eliminates unnecessary unload
Lotus loss is conducive to minimize hydraulic power loss；
4) present invention uses temperature sensor real-time monitoring hydraulic motor and two-way variable displacement plunger pump, cooperates rapid cooling side
Case, for preventing the duration of hydrostatic stepless speed change device closed circuit oil temperature from increasing.
Detailed description of the invention
Fig. 1 is the structure connection diagram of presently preferred embodiments of the present invention.
Specific embodiment
In order to be easy to understand the technical means, the creative features, the aims and the efficiencies achieved by the present invention, tie below
Conjunction is specifically illustrating, and the present invention is further explained.
Referring to a kind of hydrostatic transmission of electromagnetic switch of Fig. 1, including the first check valve 10, hydraulic motor 11, oil
Case 12, two-way variable displacement plunger pump 13, system pipeline 14, second one-way valve 15, low pressure relief valve 16, the first high-pressure overflow valve 17,
Second high-pressure overflow valve 18, first replaces pilot-operated proportional relief valve 19, second and replaces pilot-operated proportional relief valve 20, filtering group
Part 21, unidirectional variable pump 22, the four-way of four-way electromagnetic reversing valve 31, two of radiating subassembly 23, two commutation electromagnet 32, electro-hydraulic ratio
Example flow valve 33, flow divider-combiner 34, three-position three way hydraulic reversal valve 40 and one-way pump variable component 50, wherein unidirectional variable
Pump 22 and 13 mechanical series of two-way variable displacement plunger pump, and be provided between unidirectional variable pump 22 and two-way variable displacement plunger pump 13 same
Transmission shaft is driven using the same power source, and there are two main hydraulic fluid ports and two secondary hydraulic fluid ports for setting on two-way variable displacement plunger pump 13, and should
Two main hydraulic fluid ports can it is fuel-displaced can also oil return, two main hydraulic fluid ports of two-way variable displacement plunger pump 13 pass through system pipeline 14 and two respectively
Two oil inlets connection of position four-way electromagnetic reversing valve 31, one of pair hydraulic fluid port pass through system pipeline 14 and the second displacement guide
The oil outlet of formula proportional pressure control valve 20 connects, another secondary hydraulic fluid port connects the oil inlet of radiating subassembly 23 by system pipeline 14,
And temperature sensor is provided on the secondary hydraulic fluid port connecting on two-way variable displacement plunger pump 13 with radiating subassembly 23；On hydraulic motor 11
Setting there are two main hydraulic fluid port, and two main hydraulic fluid ports can it is fuel-displaced can also oil return, also set up there are two secondary hydraulic fluid port on hydraulic motor 11,
One of pair hydraulic fluid port is connect by system pipeline 14 with the oil outlet of the first displacement pilot-operated proportional relief valve 19, another is secondary
Hydraulic fluid port connects radiating subassembly 23 by system pipeline 14, is provided with temperature on the secondary hydraulic fluid port that hydraulic motor 11 is connect with radiating subassembly 23
Sensor is spent, two main hydraulic fluid ports of hydraulic motor 11 pass through two of system pipeline 14 and two four-way electromagnetic reversing valves 31 respectively
Oil outlet connection, 13 pump oil of two-way variable displacement plunger pump drive hydraulic motor 11 to rotate output mechanical energy, two four-ways commutation electromagnetism
Iron 32 is mounted on two four-way electromagnetic reversing valves 31；First check valve 10 and the oil inlet of second one-way valve 15 pass through system pipes
Road 14 connects, and the first check valve 10 is separately connected two oil of two-way variable displacement plunger pump 13 with the oil outlet of second one-way valve 15
Mouthful, i.e. it is in parallel with two-way variable displacement plunger pump 13 after the first check valve 10 and the series connection of second one-way valve 15；First high-pressure overflow valve 17
It is in parallel with two-way variable displacement plunger pump 13 with after 18 reverse parallel connection of the second high-pressure overflow valve, i.e. the oil outlet of the first high-pressure overflow valve 17
It is connect with a main hydraulic fluid port of two-way variable displacement plunger pump 13, and this main hydraulic fluid port of the two-way variable displacement plunger pump 13 and the second high pressure
The oil inlet of overflow valve 18 connects, that is, another of the oil outlet of the second high-pressure overflow valve 18 and two-way variable displacement plunger pump 13 master
Hydraulic fluid port connection, and this main hydraulic fluid port of the two-way variable displacement plunger pump 13 is connect with the oil inlet of the first high-pressure overflow valve 17；Unidirectionally
The oil inlet of variable pump 22 is connect with the oil outlet of filter assemblies 21, and the oil inlet of filter assemblies 21 connects fuel tank 12, unidirectional to become
The oil outlet of amount pump 22 is connect with the oil inlet of the first check valve 10 and second one-way valve 15 simultaneously by system pipeline 14, unidirectionally
The oil outlet of variable pump 22 also passes through system pipeline 14 and connect with the oil inlet of low pressure relief valve 16, low pressure relief valve 16 it is fuel-displaced
Mouth is connect with the oil inlet of radiating subassembly 23, and the oil outlet of radiating subassembly 23 connects fuel tank 12, one-way pump by system pipeline 14
Variable component 50 is connect with unidirectional variable pump 22, and the hydraulic control mouth of one-way pump variable component 50 connects unidirectional change by system pipeline 14
The oil outlet of amount pump 22；The oil inlet A and oil inlet B of three-position three way hydraulic reversal valve 40 connect two main oil of hydraulic motor 11
Mouthful, the corresponding hydraulic horse of left hydraulic control mouth connection 40 oil inlet A of three-position three way hydraulic reversal valve of three-position three way hydraulic reversal valve 40
Up to 11 main hydraulic fluid ports, the right hydraulic control mouth connection 40 oil inlet B of three-position three way hydraulic reversal valve of three-position three way hydraulic reversal valve 40 is corresponding
The main hydraulic fluid port of hydraulic motor 11, the oil outlet of three-position three way hydraulic reversal valve 40 passes through system pipeline 14 and electro-hydraulic proportional flow valve
33 oil inlet connection, the oil outlet of electro-hydraulic proportional flow valve 33 are connect with the oil inlet of flow divider-combiner 34, flow divider-combiner
There are two oil outlet, one of oil outlets to connect with the oil inlet of the second displacement pilot-operated proportional relief valve 20 for 34 settings, separately
One oil outlet is connect with the oil inlet of the first displacement pilot-operated proportional relief valve 19.
In the present embodiment, filter assemblies 21 include filter.
In the present embodiment, 13 pump oil of two-way variable displacement plunger pump supplies hydraulic motor through two four-way electromagnetic reversing valves 31
11, the present apparatus can change the steering of hydraulic motor 11 by the output commutation of two-way variable displacement plunger pump 13 itself, also can be not
Under the output state for changing two-way variable displacement plunger pump 13, two four-way electromagnetics commutations are controlled by two four-ways commutation electromagnet 32
Valve 31 commutates, to change the steering of hydraulic motor 11；
The oil pressure relief of present apparatus mesolow overflow valve 16 is higher than the first displacement pilot-operated proportional relief valve 19 and second and sets
The oil pressure relief for changing pilot-operated proportional relief valve 20, when the oil inlet A for connecting three-position three way hydraulic reversal valve 40 is higher-pressure region,
High pressure oil commutates three-position three way hydraulic reversal valve 40 to left position through the left hydraulic control mouth of three-position three way hydraulic reversal valve 40, and three at this time
The oil inlet B of threeway pilot operated directional control valve 40 and the oil outlet of three-position three way hydraulic reversal valve 40 are connected, due to low pressure relief valve 16
Oil pressure relief be higher than first displacement pilot-operated proportional relief valve 19 and second displacement pilot-operated proportional relief valve 20 overflow pressure
Power, in 11 oil return of hydraulic motor, section hydraulic oil enters through three-position three way hydraulic reversal valve 40, electro-hydraulic proportional flow valve 33 and divides
It is shunted after stream combiner valve 34, it is intracavitary that a part enters 11 type of hydraulic motor after the first displacement 19 overflow of pilot-operated proportional relief valve
Afterwards oil return after the heat dissipation of radiating subassembly 23 to fuel tank 12, another part enter after 20 overflows 13 types it is intracavitary after oil return and through 23
Fuel tank 12 is back to after heat dissipation, at the same time, it is logical into oil return that the hydraulic oil that unidirectional variable pump 22 pumps out pushes second one-way valve 15 open
Road, so that supplement replaces the hydraulic of 20 overflow of pilot-operated proportional relief valve through the first displacement pilot-operated proportional relief valve 19 and second
Oil, when 11 load excessive of hydraulic motor, when high nip pressures being caused to exceed the oil pressure relief of the first high-pressure overflow valve 17, two-way change
The pressure oil output of amount plunger pump 13 returns to the oil return of two-way variable displacement plunger pump 13 at this time after 17 overflow of the first high-pressure overflow valve
Mouthful, vice versa for hydraulic circuit；
Since unidirectional variable pump 22 is uninterrupted pump oil, does not enter into the extra hydraulic oil in circuit and overflow through low pressure relief valve 16
It flows and is back to fuel tank 12 after the heat dissipation of radiating subassembly 23；
The present apparatus can control the second displacement pilot-operated proportional relief valve 20 and the first displacement pilot-operated proportional relief valve respectively
19 oil pressure relief and maximum through-current capacity, by the pair of temperature sensor real-time monitoring hydraulic motor 11 and two-way variable displacement plunger pump 13
Hydraulic fluid port oil temperature cuts off three-position three way hydraulic commutation by electro-hydraulic proportional flow valve 33 when oil temperature is lower is unfavorable for equipment operation
Valve 40 leads to the oil circuit of flow divider-combiner 34, to stop the further drop to hydraulic motor 11 and two-way variable displacement plunger pump 13
Temperature, unidirectional 22 pump oil of variable pump mainly should since 16 off-load of low pressure relief valve generates pressure through 16 off-load of low pressure relief valve at this time
Pressure feeds back to one-way pump variable component 50 by system pipeline 14, and one-way pump variable component 50 is pushed unidirectional by pressure effect
The variable executing agency of variable pump 22, to reduce the power consumption of system unloaded, promotees to reduce the output displacement of unidirectional variable pump 22
It is in the present apparatus in dynamic energy-saving balance；When temperature sensor monitors hydraulic motor 11 and two-way variable displacement plunger pump
When 13 secondary hydraulic fluid port oil temperature is higher than presetting oil temperature range, the present apparatus controls electro-hydraulic ratio according to detected value and the oil temperature difference of setting
The logical oil mass of example flow valve 33, to reduce the processing temperature of hydraulic motor 11 and two-way variable displacement plunger pump 13；When the present apparatus is because prominent
When so load increase causes temperature rise rapidly to rise, pass through the first displacement pilot-operated proportional relief valve 19 of control and the second displacement guide
The oil pressure relief of formula proportional pressure control valve 20 plays what emergency cooled down rapidly to cooperate the big flow of electro-hydraulic proportional flow valve 33
Effect；No matter under which kind of operating condition, one-way pump variable component 50 changes the discharge capacity of unidirectional variable pump 22 according to external pressure always,
To adapt to optimum condition needs.
The above shows and describes the basic principles and main features of the present invention and the advantages of the present invention.The technology of the industry
Personnel are it should be appreciated that the present invention is not limited to the above embodiments, and the above embodiments and description only describe this
The principle of invention, without departing from the spirit and scope of the present invention, various changes and improvements may be made to the invention, these changes
Change and improvement all fall within the protetion scope of the claimed invention.The claimed scope of the invention by appended claims and its
Equivalent thereof.
Claims (10)
1. a kind of hydrostatic transmission of electromagnetic switch, including hydraulic motor, fuel tank, two-way variable displacement plunger pump, low pressure spill
Valve, filter assemblies, unidirectional variable pump, solenoid directional control valve, commutation electromagnet and pilot operated directional control valve, which is characterized in that unidirectional variable
Pump and two-way variable displacement plunger pump mechanical series, and be provided between unidirectional variable pump and two-way variable displacement plunger pump using same dynamic
The same transmission shaft of power source driving, there are two the masters for connecting with solenoid directional control valve oil inlet for setting on two-way variable displacement plunger pump
Hydraulic fluid port and two secondary hydraulic fluid ports, one of pair hydraulic fluid port are connect with the oil outlet of the second displacement pilot-operated proportional relief valve, another
Secondary hydraulic fluid port connects radiating subassembly oil inlet, and is provided with temperature on the secondary hydraulic fluid port connecting in two-way variable displacement plunger pump with radiating subassembly
Sensor；It is arranged on hydraulic motor there are two the main hydraulic fluid port for being connect with solenoid directional control valve oil outlet and two secondary hydraulic fluid ports,
In a secondary hydraulic fluid port connect with the oil outlet of the first displacement pilot-operated proportional relief valve, another pair hydraulic fluid port connection radiating subassembly,
Temperature sensor is provided on the secondary hydraulic fluid port connecting in hydraulic motor with radiating subassembly, commutation electromagnet is mounted on solenoid directional control valve
On；One way component and high pressure kicks component, the oil inlet and filter assemblies of unidirectional variable pump are parallel on two-way variable displacement plunger pump
Oil outlet connection, the oil inlets of filter assemblies connects fuel tank, and an oil outlet of unidirectional variable pump is simultaneously and in one way component
Oil inlet connection, the oil inlet of another oil outlet of unidirectional variable pump and low pressure relief valve connects, and low pressure relief valve goes out
Hydraulic fluid port connects fuel tank；One-way pump variable component is connect with unidirectional variable pump, oil inlet A, the oil inlet B of pilot operated directional control valve with it is hydraulic
The main hydraulic fluid port connection of two of motor, the oil outlet of pilot operated directional control valve and the oil inlet of electro-hydraulic proportional flow valve connect, electric-hydraulic proportion
The oil outlet of flow valve and the oil inlet of flow divider-combiner connect, and there are two oil outlets for flow divider-combiner setting, one of them goes out
Hydraulic fluid port is connect with the oil inlet of the second displacement pilot-operated proportional relief valve, another oil outlet and the first displacement pilot proportional overflow
Flow the oil inlet connection of valve.
2. a kind of hydrostatic transmission of electromagnetic switch according to claim 1, which is characterized in that solenoid directional control valve is
Two four-way electromagnetic reversing valves.
3. a kind of hydrostatic transmission of electromagnetic switch according to claim 1, which is characterized in that commutation electromagnet be
Two four-ways commutation electromagnet.
4. a kind of hydrostatic transmission of electromagnetic switch according to claim 1, which is characterized in that pilot operated directional control valve is
Three-position three way hydraulic reversal valve.
5. a kind of hydrostatic transmission of electromagnetic switch according to claim 1, which is characterized in that one way component is by
One check valve and second one-way valve form, and the first check valve is connected with the oil inlet of second one-way valve by system pipeline, and the
One check valve and the oil outlet of second one-way valve are separately connected two hydraulic fluid ports of two-way variable displacement plunger pump.
6. a kind of hydrostatic transmission of electromagnetic switch according to claim 5, which is characterized in that unidirectional variable pump
One oil outlet is connect with the oil inlet of the first check valve and second one-way valve simultaneously by system pipeline.
7. a kind of hydrostatic transmission of electromagnetic switch according to claim 1, which is characterized in that high pressure kicks component
It is made of the first high-pressure overflow valve and the second high-pressure overflow valve, and the first high-pressure overflow valve and the second high-pressure overflow valve reverse parallel connection
It is in parallel with two-way variable displacement plunger pump again afterwards.
8. a kind of hydrostatic transmission of electromagnetic switch according to claim 1, which is characterized in that filter assemblies include
Filter.
9. a kind of hydrostatic transmission of electromagnetic switch according to claim 1, which is characterized in that in low pressure relief valve
Oil outlet and fuel tank between be provided with radiating subassembly, the oil outlet of low pressure relief valve and the oil inlet of radiating subassembly connect, and dissipate
The oil outlet of hot component connects fuel tank.
10. the hydrostatic transmission of described in any item a kind of electromagnetic switch according to claim 1~9, which is characterized in that double
Hydraulic motor is supplied through two four-way electromagnetic reversing valves to Variable plunger pump pump oil, the present apparatus passes through two-way variable displacement plunger pump itself
Output commutation to change the steering of hydraulic motor, can also be under the output state for not changing two-way variable displacement plunger pump, by changing
To two four-way electromagnetic reversing valve commutations of magnet control, to change the steering of hydraulic motor；
The oil pressure relief of present apparatus mesolow overflow valve is higher than the first displacement pilot-operated proportional relief valve and the second displacement pilot-operated type
The oil pressure relief of proportional pressure control valve, when the oil inlet A for connecting three-position three way hydraulic reversal valve is higher-pressure region, high pressure oil is through three
The left hydraulic control mouth of threeway pilot operated directional control valve commutates three-position three way hydraulic reversal valve to left position, at this time three-position three way hydraulic reversal valve
The oil outlet of oil inlet B and three-position three way hydraulic reversal valve is connected, since the oil pressure relief of low pressure relief valve is higher than the first displacement
The oil pressure relief of pilot-operated proportional relief valve and the second displacement pilot-operated proportional relief valve, the section hydraulic in hydraulic motor oil return
Oil shunts after the first displacement pilot-operated proportional relief valve, electro-hydraulic proportional flow valve enter flow divider-combiner, and a part is through first
Enter the intracavitary rear oil return of hydraulic motor type to fuel tank after replacing pilot-operated proportional relief valve overflow, another part is through the second displacement
Enter the intracavitary rear oil return of two-way variable displacement plunger pump type after pilot-operated proportional relief valve overflow and is back to oil after radiating subassembly radiates
Case, at the same time, the hydraulic oil that unidirectional variable pump pumps out push second one-way valve open and enter drainback passage, so that supplement is set through first
The hydraulic oil for changing pilot-operated proportional relief valve and the second displacement pilot-operated proportional relief valve overflow, when hydraulic motor load excessive,
When high nip pressures being caused to exceed the oil pressure relief of the first high-pressure overflow valve, the pressure oil output of two-way variable displacement plunger pump is through first
The oil return opening of two-way variable displacement plunger pump at this time is returned to after high-pressure overflow valve overflow, vice versa for hydraulic circuit；
The oil pressure relief and most of the second displacement pilot-operated proportional relief valve of control simultaneously and the first displacement pilot-operated proportional relief valve
Big through-current capacity, by the secondary hydraulic fluid port oil temperature of temperature sensor real-time monitoring hydraulic motor and two-way variable displacement plunger pump, when oil temperature is lower
When being unfavorable for equipment operation, the oil that three-position three way hydraulic reversal valve leads to flow divider-combiner is cut off by electro-hydraulic proportional flow valve
Road, to stop the further cooling to hydraulic motor and two-way variable displacement plunger pump, unidirectional variable pump pump oil is mainly through low at this time
Pressurized overflow valve off-load, since low pressure relief valve off-load generates pressure, which feeds back to one-way pump set of variables by system pipeline
Part, one-way pump variable component is pushed the variable executing agency of unidirectional variable pump by pressure effect, to reduce unidirectional variable pump
Output displacement, to reduce the power consumption of system unloaded, and then the present apparatus is promoted to be in dynamic energy-saving balance；Work as temperature
When sensor monitors that the secondary hydraulic fluid port oil temperature of hydraulic motor and two-way variable displacement plunger pump is higher than presetting oil temperature range, present apparatus root
According to the logical oil mass of detected value and the oil temperature difference of setting control electro-hydraulic proportional flow valve, to reduce hydraulic motor and bidirectional variable column
Fill in the processing temperature of pump；When the present apparatus increases because of load suddenly, and temperature rise is caused rapidly to rise, pass through the first displacement guide of control
The oil pressure relief of formula proportional pressure control valve and the second displacement pilot-operated proportional relief valve, to cooperate the big stream of electro-hydraulic proportional flow valve
Amount plays the role of emergency and cools down rapidly；No matter under which kind of operating condition, one-way pump variable component changes according to external pressure always
The discharge capacity of unidirectional variable pump, to adapt to optimum condition needs.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811036313.7A CN109058188B (en) | 2018-09-06 | 2018-09-06 | Electromagnetic reversing hydrostatic transmission device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811036313.7A CN109058188B (en) | 2018-09-06 | 2018-09-06 | Electromagnetic reversing hydrostatic transmission device |
Publications (2)
| Publication Number | Publication Date |
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| CN109058188A true CN109058188A (en) | 2018-12-21 |
| CN109058188B CN109058188B (en) | 2019-12-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811036313.7A Active CN109058188B (en) | 2018-09-06 | 2018-09-06 | Electromagnetic reversing hydrostatic transmission device |
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| CN (1) | CN109058188B (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1994005915A1 (en) * | 1992-09-04 | 1994-03-17 | Kabushiki Kaisha Komatsu Seisakusho | Hydraulic braking system |
| JP2000186762A (en) * | 1998-12-22 | 2000-07-04 | Shin Caterpillar Mitsubishi Ltd | Travel control method and device for the same |
| CN102536927A (en) * | 2010-11-25 | 2012-07-04 | 林德材料控股有限责任公司 | Load-sensing regulating type hydrostatic drive system |
| CN202789784U (en) * | 2012-08-09 | 2013-03-13 | 郑州新大方重工科技有限公司 | Hydraulic system with fine adjustment function |
| CN208749698U (en) * | 2018-09-06 | 2019-04-16 | 湖南农业大学 | A kind of low-power consumption hydrostatic transmission |
-
2018
- 2018-09-06 CN CN201811036313.7A patent/CN109058188B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1994005915A1 (en) * | 1992-09-04 | 1994-03-17 | Kabushiki Kaisha Komatsu Seisakusho | Hydraulic braking system |
| JP2000186762A (en) * | 1998-12-22 | 2000-07-04 | Shin Caterpillar Mitsubishi Ltd | Travel control method and device for the same |
| CN102536927A (en) * | 2010-11-25 | 2012-07-04 | 林德材料控股有限责任公司 | Load-sensing regulating type hydrostatic drive system |
| CN202789784U (en) * | 2012-08-09 | 2013-03-13 | 郑州新大方重工科技有限公司 | Hydraulic system with fine adjustment function |
| CN208749698U (en) * | 2018-09-06 | 2019-04-16 | 湖南农业大学 | A kind of low-power consumption hydrostatic transmission |
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| Publication number | Publication date |
|---|---|
| CN109058188B (en) | 2019-12-27 |
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