CN107795538A - Running motor shift valve, running motor and engineering machinery - Google Patents

Running motor shift valve, running motor and engineering machinery Download PDF

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Publication number
CN107795538A
CN107795538A CN201711246964.4A CN201711246964A CN107795538A CN 107795538 A CN107795538 A CN 107795538A CN 201711246964 A CN201711246964 A CN 201711246964A CN 107795538 A CN107795538 A CN 107795538A
Authority
CN
China
Prior art keywords
valve element
running motor
chamber
working position
hydraulic fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201711246964.4A
Other languages
Chinese (zh)
Other versions
CN107795538B (en
Inventor
赵斌
吴传玉
李扬
戴维·普鲁斯特
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jiangsu XCMG Construction Machinery Institute Co Ltd
Original Assignee
Construction Machinery Branch of XCMG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Construction Machinery Branch of XCMG filed Critical Construction Machinery Branch of XCMG
Priority to CN201711246964.4A priority Critical patent/CN107795538B/en
Publication of CN107795538A publication Critical patent/CN107795538A/en
Priority to KR1020207013037A priority patent/KR102273877B1/en
Priority to JP2020517249A priority patent/JP7162659B2/en
Priority to DE112018002268.4T priority patent/DE112018002268T5/en
Priority to PCT/CN2018/079068 priority patent/WO2018188449A1/en
Application granted granted Critical
Publication of CN107795538B publication Critical patent/CN107795538B/en
Active legal-status Critical Current
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Classifications

    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/2058—Electric or electro-mechanical or mechanical control devices of vehicle sub-units
    • E02F9/2062—Control of propulsion units
    • E02F9/207—Control of propulsion units of the type electric propulsion units, e.g. electric motors or generators
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K99/00—Subject matter not provided for in other groups of this subclass
    • H02K99/20—Motors
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/763—Control of torque of the output member by means of a variable capacity motor, i.e. by a secondary control on the motor

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Power Engineering (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Multiple-Way Valves (AREA)
  • Operation Control Of Excavators (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Hydraulic Motors (AREA)
  • Control Of Fluid Gearings (AREA)

Abstract

The present invention relates to technical field of engineering machinery, more particularly to a kind of running motor shift valve, running motor and engineering machinery.Running motor shift valve provided by the present invention, including valve element, the first actuator port, the second actuator port, the 3rd actuator port, external control hydraulic fluid port and feedback hydraulic fluid port, and valve element is carried out by low speed under two different preset values to the switching at a high speed and by high speed to low speed respectively, and the motor input value after gearshift is caused to be unsatisfactory for boundary condition of shifting gears, it can effectively prevent the high low speed of running motor from switching repeatedly, reduce the vibration under engineering machinery severe duty.

Description

Running motor shift valve, running motor and engineering machinery
Technical field
The present invention relates to technical field of engineering machinery, more particularly to a kind of running motor shift valve, running motor and engineering Machinery.
Background technology
Running motor is widely used in the engineering machinery such as excavator, drives engineering machinery walking.Running motor is usual Including motor and swash plate controlling organization, swash plate controlling organization is by controlling the swash plate angle of motor to adjust the output shaft of motor Rotating speed, make running motor possess at a high speed and low speed two-stage speed changing function.Wherein, during low-speed mode, running motor output speed It is relatively low, but discharge capacity is larger, under same input power, can export larger moment of torsion；And during fast mode, running motor output turns Speed is higher, but discharge capacity is smaller, under same input power, can export less moment of torsion.
When the engineering machinery walkings such as excavator are under the severe duties such as ramp, muddy marsh or towing, row is often required that Walk motor and bigger driving moment is provided, that is, require that running motor works in low-speed mode, so that running motor offer is larger Moment of torsion, the powerless phenomenon that can't walk any longer or walk is prevented, and after walking resistance diminishes, need by low-speed mode to be switched again again For fast mode, to improve wheel efficiency.It is therefore desirable to running motor can switch work under fast mode and low-speed mode Make.
In order to control running motor to switch to low-speed mode by fast mode automatically under severe duty, usually walk horse Up to outfit running motor shift valve.Running motor shift valve is passed through hydraulic oil by controlling whether to swash plate controlling organization, to control Whether running motor processed by fast mode switches to low-speed mode, realizes the automatic gear change function of running motor.
However, running motor shift valve of the prior art, it generally by detecting the actual pressure of motor at high speeds Whether power exceedes a certain preset value, to judge whether to be passed through hydraulic oil control gearshift to swash plate controlling organization, and due to engineering machine The peak power that prime mover (engine) of tool is provided is a steady state value, the output torque of running motor and operating pressure and row Measure directly proportional, with operating mode, after switching to low speed at a high speed, motor input port pressure will be less than the pressure before gear shift, that is, be less than Preset value, now shift valve can automatically switch back into fast mode again, therefore, cause running motor occur under severe duty height The phenomenon that switches repeatedly of speed, causes to tremble under engineering machinery severe duty, not only influence shift valve in itself, running motor and Engineering machinery overall life-span and safety, while can also reduce the comfortableness of product.
The content of the invention
A technical problem to be solved by this invention is：Prevent the high low speed of running motor from switching repeatedly, reduce engineering machine Vibration under tool severe duty.
In order to solve the above-mentioned technical problem, first aspect present invention provides a kind of running motor shift valve, and it includes valve Core, the first actuator port, the second actuator port, the 3rd actuator port, external control hydraulic fluid port and feedback hydraulic fluid port, valve element have the first work Position and the second working position, in the first working position, the cut-off of the first actuator port and the second actuator port and the 3rd actuator port connect Logical, in the second working position, the first actuator port connects with the 3rd actuator port and the second actuator port ends；First working oil Mouth is used to connect with oil sources, and the second actuator port is used to connect with fuel tank, and the 3rd actuator port is used for the swash plate with running motor Controlling organization connects；External control hydraulic fluid port is used to guide control oil to act on the axial first end of valve element and valve element is produced by the first work Make the trend that position is moved to the second working position, feedback hydraulic fluid port is used to the actual working pressure of the motor of running motor feeding back to valve Axially the second end of core simultaneously makes valve element produce the trend moved from the second working position to the first working position, also, the running motor Shift valve is provided so that：
The oil pressure of feedback hydraulic fluid port is less than the first preset value PC1When, valve element can be moved to the second work by the first working position Position, the oil pressure for feeding back hydraulic fluid port are more than the second preset value PC2When, valve element can be moved to the first working position by the second working position, its In, the first preset value PC1With the second preset value PC2It is unequal；
Also, after valve element is moved to the second working position by the first working position, the oil pressure for feeding back hydraulic fluid port is the first working value PC3, After valve element switches to the first working position by the second working position, the oil pressure for feeding back hydraulic fluid port is the second working value PC4, wherein, the first work Value PC3With the second preset value PC2Between meet PC3＜ K1PC2, K1≤ 1, and the second working value PC4With the first preset value PC1Between it is full Sufficient PC4＞ K2PC1, K2≥1。
Alternatively, running motor shift valve also includes first chamber, second chamber and the 3rd chamber, first chamber and external control Hydraulic fluid port connects, and the 3rd chamber connects with feedback hydraulic fluid port, and second chamber connects with the 3rd actuator port and in valve element by the first work Connected during position is moved to the second working position with the second actuator port and the first actuator port to switching, and second chamber Effective pressure active area is less than the effective pressure active area of the 3rd chamber.
Alternatively, running motor shift valve also includes spring, and spring is arranged at axially the second end of valve element and valve element is applied Adding makes valve element produce the active force from the second working position to the first working position mobile trend, the first preset value PC1For PC1=(PX× A1-F1)/A3, the second preset value PC2For PC2=(PX×A1-F2)/(A3-A2), the first working value PC3ForSecond Working value isWherein, PXFor the oil pressure of external control hydraulic fluid port, A1、A2And A3Respectively first chamber, second chamber and The effective pressure active area of 3rd chamber, F1And F2Respectively spring applies in the first working position and the second working position to valve element Active force, V1And V2Respectively discharge capacity of the motor in the first working position and the second working position.
Alternatively, second chamber and the 3rd chamber are arranged on valve element and are located at axial first end and the axial direction of valve element respectively Second end.
Alternatively, the axial first end of valve element and the second end of axial direction are respectively equipped with the first plunger cavity and the second plunger cavity, the The first plunger is provided with one plunger cavity, the second plunger is provided with the second plunger cavity, second chamber is located at the first plunger and the first post Between the inwall for filling in chamber, the 3rd chamber is between the second plunger and the inwall of the second plunger cavity.
Alternatively, first passage is additionally provided with valve element, second chamber passes through first passage and the first actuator port and second A connection in actuator port；And/or second channel is additionally provided with valve element, the 3rd chamber passes through second channel and feedback oil Mouth connection.
Alternatively, running motor shift valve also includes the first closeouts, and the first closeouts are arranged at the axial direction second of valve element End, the spring of running motor shift valve, which supports between the first closeouts and axially the second end of valve element and valve element is applied, makes valve Core produces the active force from the second working position to the first working position mobile trend.
Alternatively, the surface of the close valve element of the first closeouts is provided with spring accommodating chamber, and spring is arranged at spring receiving In chamber.
Alternatively, first through hole is additionally provided with the first closeouts, first through hole connects with spring accommodating chamber.
Alternatively, the surface of the remote valve element of the first closeouts is provided with binding groove.
Alternatively, the axial first end of valve element has necking section.
Alternatively, the peripheral surface of necking section is provided with groove.
Second aspect of the present invention additionally provides a kind of running motor, it include motor and with the swash plate drive connection of motor Swash plate controlling organization, also, it also includes the running motor shift valve of the present invention, and running motor shift valve is arranged at the shell of motor Internal portion.
Alternatively, housing is provided with the second through hole, and the valve element of running motor shift valve is placed in the second through hole, and walks The first actuator port, the second actuator port, the 3rd actuator port, external control hydraulic fluid port and the feedback hydraulic fluid port of motor shift valve may be contained within On the inwall of housing.
Third aspect present invention additionally provides a kind of engineering machinery, and it includes the running motor of the present invention.
The present invention to running motor shift valve by being improved so that the valve element of running motor shift valve is respectively at two Carried out under different preset values by low speed to the switching at a high speed and by high speed to low speed, and cause the motor input after gearshift Value is unsatisfactory for boundary condition of shifting gears, and can effectively prevent the high low speed of running motor from switching repeatedly, reduces engineering machinery heavy duty work Vibration under condition.
By referring to the drawings to the present invention exemplary embodiment be described in detail, further feature of the invention and Its advantage will be made apparent from.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing There is the required accompanying drawing used in technology description to be briefly described, it should be apparent that, drawings in the following description are only this Some embodiments of invention, for those of ordinary skill in the art, without having to pay creative labor, may be used also To obtain other accompanying drawings according to these accompanying drawings.
Fig. 1 shows the hydraulic schematic diagram of the running motor system of one embodiment of the invention.
Fig. 2 shows the sectional view when gearshift valve core of running motor in Fig. 1 is in the first working position.
Fig. 3 shows the sectional view when gearshift valve core of running motor in Fig. 1 is in the second working position.
Fig. 4 shows the structural representation of valve element in Fig. 2 and Fig. 3.
In figure：
100th, running motor shift valve；200th, balanced valve；300th, shuttle valve；400th, motor；500th, swash plate controlling organization；
1st, valve element；21st, the first plunger；22nd, the second plunger；31st, the first closeouts；32nd, the second closeouts；4th, spring；5、 Housing；6th, sealing ring；
11st, the first sealing section；12nd, the second sealing section；13rd, the 3rd sealing section；14th, the 4th sealing section；15th, it is recessed Groove；16th, spring base；
1a, first chamber；1b, second chamber；1c, the 3rd chamber；1d, first passage；1e, second channel；1f, the first post Fill in chamber；1g, the second plunger cavity；
31a, first through hole；31b, binding groove；31c, spring accommodating chamber；
51st, the second through hole；
Y, the first actuator port；L, the second actuator port；Z, the 3rd actuator port；X, external control hydraulic fluid port；C, hydraulic fluid port is fed back.
Embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is carried out clear, complete Site preparation describes, it is clear that described embodiment is only part of the embodiment of the present invention, rather than whole embodiments.Below Description only actually at least one exemplary embodiment is illustrative, is never used as to the present invention and its application or makes Any restrictions.Based on the embodiment in the present invention, those of ordinary skill in the art are in no development creative work premise Lower obtained every other embodiment, belongs to the scope of protection of the invention.
It may be not discussed in detail for technology, method and apparatus known to person of ordinary skill in the relevant, but suitable In the case of, the technology, method and apparatus should be considered as authorizing part for specification.
In the description of the invention, it is to be understood that the noun of locality such as " forward and backward, upper and lower, left and right ", " laterally, vertical, Vertically, orientation or position relationship indicated by level " and " top, bottom " etc. are normally based on orientation or position shown in the drawings and closed System, it is for only for ease of the description present invention and simplifies description, in the case where not making opposite explanation, these nouns of locality do not indicate that There must be specific orientation with the device or element for implying meaning or with specific azimuth configuration and operation, therefore can not manage Solve as limiting the scope of the invention；The noun of locality " inside and outside " refers to relative to inside and outside each part profile in itself.
In the description of the invention, it is to be understood that limit parts using the word such as " first ", " second ", only It is for only for ease of and corresponding parts is distinguished, does not such as have Stated otherwise, above-mentioned word does not have particular meaning, therefore not It is understood that as limiting the scope of the invention.
Fig. 1-4 shows one embodiment of the present of invention.Reference picture 1-4, running motor shift valve provided by the present invention 100, including valve element 1, the first actuator port Y, the second actuator port L, the 3rd actuator port Z, external control hydraulic fluid port X and feedback hydraulic fluid port C, Valve element 1 has the first working position and the second working position, in the first working position, the first actuator port Y cut-offs and the second working oil Mouthful L is connected with the 3rd actuator port Z, and in the second working position, the first actuator port Y is connected and second with the 3rd actuator port Z Actuator port L ends；First actuator port Y is used to connect with oil sources, and the second actuator port L is used to connect with fuel tank, the 3rd work Make hydraulic fluid port Z to be used to connect with the swash plate controlling organization 500 of running motor；External control hydraulic fluid port X is used to guide control oil to act on valve element 1 Axial first end and valve element 1 is produced the trend moved from the first working position to the second working position, feedback hydraulic fluid port C is used for will row The actual working pressure for walking the motor 400 of motor feeds back to axially the second end of valve element 1 and valve element 1 is produced by the second working position The trend moved to the first working position, it is characterised in that running motor shift valve 100 is provided so that：
Feedback hydraulic fluid port C oil pressure is less than the first preset value PC1When, valve element 1 can be moved to the second work by the first working position Position, feedback hydraulic fluid port C oil pressure are more than the second preset value PC2When, valve element 1 can be moved to the first working position by the second working position, its In, the first preset value PC1With the second preset value PC2It is unequal；
Also, after valve element 1 is moved to the second working position by the first working position, feedback hydraulic fluid port C oil pressure is the first working value PC3, after valve element 1 switches to the first working position by the second working position, feedback hydraulic fluid port C oil pressure is the second working value PC4, wherein, the One working value PC3With the second preset value PC2Between meet PC3＜ K1PC2, K1≤ 1, and the second working value PC4With the first preset value PC1 Between meet PC4＞ K2PC1, K2≥1。
In the present invention, PC1And PC2Respectively motor 400 controls running motor by low speed in running motor shift valve 100 Switch to high speed and the critical pressure value by switching to low speed at a high speed, PC3And PC4Respectively motor 400 is in running motor shift valve 100 control running motors are switched at a high speed by low speed and actually enter pressure value, K after low speed by switching at a high speed1And K2Then divide Not Wei running motor the safety coefficient being stable under fast state and running motor are switched to after high speed by switching at a high speed by low speed The stable safety coefficient with lower-speed state after to low speed.
The present invention to running motor shift valve 100 by being improved so that the valve element 1 of running motor shift valve 100 divides Control running motor to carry out by low speed to the switching at a high speed and by high speed to low speed not under two different preset values, and cause The actual working pressure value of motor 400 is unsatisfactory for boundary condition of shifting gears after gearshift, can effectively prevent the high low speed of running motor Switch repeatedly, reduce the vibration under engineering machinery severe duty, this is advantageous to extend running motor shift valve 100, running motor And the service life of engineering machinery, walking security is improved, improves comfort.
In the present invention, it is preferred to K1＜ 1, and/or, K2＞ 1, such running motor by low speed after high speed is switched to And/or to be stable at safety coefficient after switching under speed state higher by switching at a high speed after low speed, can be more reliably prevented from The high low speed of running motor switches repeatedly, the vibration under engineering machinery severe duty is more effectively reduced, so as to be more beneficial for extending The service life of running motor shift valve 100, running motor and engineering machinery, walking security is improved, improves comfort.
As a kind of embodiment of running motor shift valve 100 of the present invention, running motor shift valve 100 can also include First chamber 1a, second chamber 1b and the 3rd chamber 1c, first chamber 1a connect with external control hydraulic fluid port X, the 3rd chamber 1c and feedback Hydraulic fluid port C is connected, and second chamber 1b is connected with the 3rd actuator port Z and moved in valve element 1 from the first working position to the second working position During switching ground connected with the second actuator port L and the first actuator port Y, and second chamber 1b effective pressure acting surface Effective pressure active area of the product less than the 3rd chamber 1c.Based on this, the present invention only need to first chamber 1a, second chamber 1b and 3rd chamber 1c effective pressure active area is configured, you can the valve element 1 of running motor shift valve 100 is distinguished Control running motor to carry out by low speed to the switching at a high speed and by high speed to low speed under two different preset values, and to change The actual working pressure value of motor 400 can be unsatisfactory for boundary condition of shifting gears after gear, and structure is simpler, and cost is relatively low, and can It is higher by property.Embodiment with reference to shown in Fig. 1-4 is further described by this point.
The present invention is further illustrated with reference to Fig. 1-4.
In order to make it easy to understand, the structure and working principle of running motor system is illustrated with reference to Fig. 1 first.
As shown in figure 1, running motor system includes running motor, running motor shift valve 100, the and of pressure selection valve 300 Balanced valve 200 etc., running motor include motor 400 and swash plate controlling organization 500 etc..
Wherein, the swash plate drive connection of swash plate controlling organization 500 and motor 400, for by driving swash plate to swing to change Become the pivot angle of swash plate.Controlled by Fig. 1, the swash plate controlling organization 500 of the embodiment is specially hydraulic cylinder, and its cylinder rod connects with swash plate Connect.Based on this, when the rodless cavity oil-feed of swash plate controlling organization 500, swash plate controlling organization 500 drives swash plate to be rocked to smaller angle Position is spent, running motor is switched to low-speed mode；And when the oil in the rodless cavity of swash plate controlling organization 500 flows back to fuel tank When, then swash plate controlling organization 500 can drive swash plate to be rocked to larger angle position, running motor is switched to fast mode.
Motor 400 is connected by balanced valve 200 with hydraulic fluid port A and hydraulic fluid port B.When one in hydraulic fluid port A and hydraulic fluid port B is to motor During 400 fuel feeding, the oil extraction of motor 400 is clockwise so as to drive motor 400 through another outflow in hydraulic fluid port A and hydraulic fluid port B Or rotate counterclockwise.
Running motor shift valve 100 be used for control swash plate controlling organization 500 rodless cavity switch with oil sources and fuel tank A connection, to control running motor at a high speed by controlling whether into the rodless cavity of swash plate controlling organization 500 fuel feeding Switch between pattern and low-speed mode.As shown in figure 1, in this embodiment, running motor shift valve 100 and swash plate controlling organization 500 rodless cavity is connected and connected by pressure selection valve 300 with balanced valve 200.Specifically, pressure selection valve 300 is shuttle valve； First actuator port Y of running motor shift valve 100 and the outlet of pressure selection valve 300, two of pressure selection valve 300 Import is connected by balanced valve 200 with hydraulic fluid port A and hydraulic fluid port B respectively；Second actuator port L of running motor shift valve 100 and oil Case connects；3rd actuator port Z of running motor shift valve 100 connects with the rodless cavity of swash plate controlling organization 500.
By setting pressure selection valve 300 so that the first actuator port Y all the time can be larger with pressure in hydraulic fluid port A and hydraulic fluid port B One connection.And because pressure value larger in hydraulic fluid port A pressure and hydraulic fluid port B pressure is oil supply pressure, while be also horse Up to 400 input pressure or actual working pressure, therefore, the first actuator port Y connects with oil sources all the time, and its pressure value PY Practically equal to the actual working pressure value of motor 400.
In order that running motor shift valve 100 can control the rodless cavity of swash plate controlling organization 500 switch with oil sources and A connection in fuel tank, as shown in figure 1, running motor shift valve 100 has the first working position (the left position in Fig. 1) and second Working position (the right position in Fig. 1).Wherein, as shown in Figure 1, when in the first working position, the first actuator port Y cut-offs and second Actuator port L connects with the 3rd actuator port Z, this cause running motor shift valve 100 connect swash plate controlling organization 500 without bar Chamber and oil sources, so as to which now hydraulic oil can be via the running motor shift valve 100 entrance swash plate controlling organization 500 without bar Chamber, promote the cylinder rod of swash plate controlling organization 500 overhanging, vertical direction of the driving swash plate into Fig. 1 is swung, and reduces the pivot angle of swash plate To minimum value, the output rotating speed of motor 400 is minimized, and then running motor is worked under low-speed mode；And when place When the second working position, the first actuator port Y connects with the 3rd actuator port Z and the second actuator port L ends, and this to walk Motor shift valve 100 connects the rodless cavity and fuel tank of swash plate controlling organization 500, so as to which now swash plate controlling organization 500 is without bar Chamber pressure release, the cylinder rod retraction of swash plate controlling organization 500, drives swash plate to be swung in the horizontal direction by the vertical direction in Fig. 1, increases The pivot angle of swash plate makes the output rotating speed of motor 400 be increased to maximum, and then running motor is worked in high speed mould to maximum Under formula.It can be seen that the first working position and the second working position of valve element 1 correspond to low-speed mode (the tick-over shape of running motor respectively State, or the first working condition) and fast mode (high speed operation state, or the second working condition).
In addition, as shown in Figure 1, running motor shift valve 100 also includes external control hydraulic fluid port X and feedback hydraulic fluid port C.Wherein, external control Hydraulic fluid port X is used as pilot control hydraulic fluid port, for introducing control oil, control running motor shift valve 100 to running motor shift valve 100 Switched from the first working position to the second working position.Feedback hydraulic fluid port C is then used to the actual working pressure of motor 400 feeding back to valve element On 1, in order to which running motor shift valve 100 works according to the actual walking load of motor 400 in the first working position and second Switch between position, so as to more accurately control running motor to complete to shift gears according to actual demand.As previously described, because the first work Hydraulic fluid port Y and feedback hydraulic fluid port C pressure are actually the actual working pressure of motor 400, therefore, the first actuator port Y pressure Power PYPressure P with feeding back hydraulic fluid port CCIt is equal.
In the prior art, the critical condition of running motor shift valve control running motor gearshift only has one, i.e. motor work Reach preset value as pressure, that is, feedback hydraulic fluid port C pressure PCEqual to preset value, it means that running motor in the prior art Shift valve according to same preset value come realize to from high speed to low speed and from low speed to the switching control of high speed.Its problem exists In because the maximal input of running motor is a steady state value, the output of running motor reaches moment of torsion and operating pressure and discharge capacity Directly proportional, therefore, after switching to low speed at a high speed, motor input port pressure will be less than preset value, now due to meeting by low Speed switches to the critical condition of high speed, and therefore, running motor shift valve can control running motor to automatically switch back into fast mode again, And after switching back into high speed, motor input port pressure rise to preset value, now due to meeting by switching to low speed at a high speed again Critical condition, therefore, running motor shift valve can control running motor to automatically switch back into low-speed mode again, so repeatedly, so that It can not be held under desired low-speed mode in running motor, but the phenomenon that high low speed switches repeatedly occurs, this can draw Rise engineering machinery tremble, not only influence shift valve in itself, running motor and engineering machinery entirety life-span and safety, simultaneously Also the comfortableness of product can be reduced.
In order to solve the problems, such as that the high low speed of running motor switches repeatedly in the prior art, the embodiment is shifted gears to running motor The structure of valve 100 is improved.It is described in detail with reference to Fig. 2-4.
As Figure 2-3, in this embodiment, running motor shift valve 100 is arranged at the inside of the housing 5 of motor 400, It includes valve element 1, the first plunger 21, the second plunger 22, the first closeouts 31, the second closeouts 32, spring 4, the first working oil Mouth Y, the second actuator port L, the 3rd actuator port Z, external control hydraulic fluid port X, first chamber 1a, second chamber 1b and the 3rd chamber 1c； Also, the running motor shift valve 100 no longer includes valve body, but using housing 5 as valve body, running motor shift valve 100 Valve element 1 is directly arranged in housing 5, and the first actuator port Y of running motor shift valve 100, the second actuator port L, the 3rd Actuator port Z, external control hydraulic fluid port X and feedback hydraulic fluid port C then may be contained within the inwall of housing 5.
, can be by running motor shift valve 100 and horse by the way that running motor shift valve 100 to be arranged to the inside of housing 5 Become one structure up to 400, make structure compacter, reduce space hold.And it is used as valve body by the use of housing 5 so that without Each hydraulic fluid port for being separately provided special valve body again to accommodate valve element 1 and set running motor shift valve 100, can also further letter Change structure, it is cost-effective, maintain easily.
Specifically, from the figure 3, it may be seen that setting of the valve element 1 in housing 5 for convenience, in this embodiment, sets on housing 5 There is the second through hole 51, valve element 1 is placed in second through hole 51.Valve element 1 is housed using the second through hole 51, it is not only easy to process, The dismounting of valve element 1 is also allowed for simultaneously.Wherein, the second through hole 51 covers (i.e. on back cover of motor) after being arranged at housing 5.
Valve element 1 realizes running motor shift valve 100 in the first working position (the right position in Fig. 2-3) and second by mobile Switching between working position (the left position in Fig. 2-3), to control the first actuator port Y of running motor shift valve 100, the second work Make hydraulic fluid port L and the 3rd actuator port Z etc. on off operating mode.As shown in figure 3, in this embodiment, valve element 1 has axial first end (in figure be right-hand member) and axially the second end (being left end in figure), and as shown in figure 3, the axial first end of valve element 1 with Second the second end of axial direction is respectively equipped with the first plunger cavity 1f and the second plunger cavity 1g.First plunger cavity 1f effective pressure acting surface Effective pressure active area of the product less than the second plunger cavity 1g.It can be appreciated that axial first end herein and axially the second end are not It is limited to two end faces of the axial direction of valve element 1, and a section can be included respectively.
As shown in Figures 2 and 3, in this embodiment, the first plunger 21 and the second plunger 22 are respectively arranged at the first plunger In chamber 1f and the second plunger cavity 1g.Between first plunger 21 and the first plunger cavity 1f inwall and the second plunger 22 and the second post Freely slidable band is formed between plug chamber 1g inwall.Second working position is switched to by the first working position in valve element 1 During, the first plunger 21 is stretched out relative to the first plunger cavity 1f and the second plunger 22 is retracted relative to the second plunger cavity 1g；And During valve element 1 switches to the first working position by the second working position, the first plunger 21 is retracted relative to the first plunger cavity 1f And second plunger 22 stretched out relative to the second plunger cavity 1g.
Based on above-mentioned setting, from Fig. 2 and Fig. 3, between the first plunger 21 and the first plunger cavity 1f inwall and Annular seal space, respectively second chamber 1b and the 3rd chamber 1c are formed respectively between two plungers 22 and the second plunger cavity 1g inwall. I.e., in this embodiment, second chamber 1b and the 3rd chamber 1c is arranged on valve element 1 and respectively positioned at the axial direction first of valve element 1 End and axially the second end.Because second chamber 1b effective pressure active area is the first plunger cavity 1f effective pressure effect Area, the 3rd chamber 1c effective pressure active area are the second plunger cavity 1g effective pressure active area, and the first post The effective pressure active area for filling in chamber 1f is less than the second plunger cavity 1g effective pressure active area, therefore, second chamber 1b's Effective pressure active area is less than the 3rd chamber 1c effective pressure active area.
Moreover, as shown in Figures 2 and 3, in this embodiment, second chamber 1b and the 3rd chamber 1c and each hydraulic fluid port connection Relation is：3rd chamber 1c connects with feedback hydraulic fluid port C；Second chamber 1b connects with the 3rd actuator port Z and in valve element 1 first Working position successively connects during being moved to the second working position with the second actuator port L and the first actuator port Y, i.e. second Chamber 1b connects (as shown in Figure 2) simultaneously when valve element 1 is in the first working position with the 3rd actuator port Z and the second actuator port L Connected (as shown in Figure 3) with the 3rd hydraulic fluid port Z and the first working hole Y when valve element 1 is in the second working position.
And second chamber 1b connects with the second actuator port L or the first actuator port Y for convenience, as shown in figure 4, at this In embodiment, first passage 1d is additionally provided with valve element 1, second chamber 1b passes through first passage 1d and the first actuator port Y and A connection in two actuator port L.Wherein, as shown in Fig. 2 in the first working position, second chamber 1b passes through first passage 1d connects with the second actuator port L；As shown in figure 3, in the second working position, second chamber 1b passes through first passage 1d and first Actuator port Y is connected.Similarly, the 3rd chamber 1c and feedback hydraulic fluid port C connection for convenience, in this embodiment, such as Fig. 4 institutes Show, second channel 1e, the 3rd chamber 1c are additionally provided with valve element 1 and is connected by second channel 1e with feedback hydraulic fluid port C.Specifically, by Fig. 4 understands that second chamber 1b and the 3rd chamber 1c are along the axially extending of valve element 1, and first passage 1d and second channel 1e are then Radially extending along valve element 1, the arrangement of two such chamber and two passages on valve element 1 is more rationally compact, processing It is more convenient.
Also, as shown in figure 4, in this embodiment, the axial first end of valve element 1 also has necking section.So, needing When being dismantled to valve element 1, it is easy to staff or extracting tool to stretch into the second through hole 51 and exerted a force to valve element 1, makes Obtain valve element 1 to be easier to take out from the second through hole 51, so as to the dismounting for valve element 1 of being more convenient for.Moreover, as shown in Figure 4, necking section Groove 15 is also further provided with peripheral surface.Because the groove 15 is more convenient for exerting a force to necking section, therefore, groove 15 is set, The dismounting difficulty of valve element 1 can further be reduced.
In addition, as shown in Figures 2 and 3, in this embodiment, the axial first end of valve element 1 and the second end of axial direction are also distinguished Provided with the second closeouts 32 and the second closeouts 31, wherein, the first closeouts 31 and the second closeouts 32 are connected on housing 5 simultaneously Respectively positioned at valve element 1 axially the second end side and valve element 1 axial first end side, be respectively used to axially the to valve element 1 Two ends side and the axial first end side of valve element 1 are blocked.
Wherein, from Fig. 2 and Fig. 3, the first closeouts 31 are threadedly connected in the second through hole 51 and positioned at the axle of valve element 1 To the second end side, for being blocked to axially the second end side of valve element 1.Specifically, the outer weekly form of the first closeouts 31 Screw thread is equipped with face, screw thread also is provided with the inwall of the corresponding position of the second through hole 51, so that under the mating reaction of screw thread, First closeouts 31 can be threadedly connected in the second through hole 51.
Also, from Fig. 2 and Fig. 3, the first closeouts 31 of the embodiment, it is additionally provided with surface away from valve element 1 Binding groove 31b.Binding groove 31b is set, is easy to the dismounting of the first closeouts 31.The especially screw thread of the first closeouts 31 of the embodiment It is connected in housing 5, binding groove 31b effect is more prominent.Because based on set binding groove 31b, the first envelope is being dismounted During blocking piece 31, it can insert a tool into binding groove 31b, then to the inner side of the second through hole 51 of housing 5 or towards the second through hole 51 Outside screws the first closeouts 31, realizes the dismounting of the first closeouts 31, more convenient operation, and disassembly efficiency is higher.
In addition, the first closeouts 31 of the embodiment are additionally operable to support spring 4.Spring 4 support located at the first closeouts 31 with Between axially the second end of valve element 1, moved for making valve element 1 produce from the second working position to the first working position the application of valve element 1 The active force of trend.Specifically, in order to facilitate the setting of spring 4, as shown in Figures 2 and 3, in this embodiment, first blocks The surface of the close valve element 1 of part 31 is provided with spring accommodating chamber 31c, and spring 4 is contained in spring accommodating chamber 31c, and supports and set Between spring accommodating chamber 31c bottom wall and axially the second end of valve element 1, such spring 4 can apply to valve element 1 makes valve element 1 The active force resetted from the second working position to the first working position.Also, understood with reference to Fig. 2-4, axially the second end of valve element 1 also has There is spring base 16, spring 4 is connected by being sheathed on spring base 16 with valve element 1, and the adjacent sections of spring base 16 and valve element 1 Between form the shaft shoulder, spring 4 is supported on the shaft shoulder, so as to what is moved when valve element 1 between the first working position and the second working position During, spring 4 can compress or extend therewith, change the elastic force size applied to valve element 1.Also, it will be readily appreciated that bullet Limited between the inwall of the closeouts 31 of spring abutment 16 and first and the second through hole 51 and form spring cavity.
Moreover, as shown in Figures 2 and 3, the first closeouts 31 of the embodiment, being additionally provided with first through hole 31a thereon, this One through hole 31a connects with spring accommodating chamber 31c.Based on this, not only it is more convenient for dismantling, while oil return of being also more convenient for.Specifically, One through hole 31a is along the axially extending of valve element 1, the first through hole 31a so based on smaller length, you can realize spring accommodating chamber 31c and outside connection, structure is simpler, and oil return is more convenient.
As shown in Figures 2 and 3, in this embodiment, the second closeouts 32 are threadedly connected in the second through hole 51 and are located at The axial first end side of valve element 1, for being blocked to the axial first end side of valve element 1.Specifically, the second closeouts 32 Outer surface be provided with screw thread, screw thread is also equipped with the inwall of the corresponding position of the second through hole 51, so as to matching somebody with somebody in screw thread Under cooperation is used, the second closeouts 32 can be threadedly connected in the second through hole 51.
It can be seen that in this embodiment, the first closeouts 31 and the second closeouts 32 are threadedly connected to the second through hole 51 axially Opposite sides.Using thread connecting mode, the plugging effect of the first closeouts 31 and the second closeouts 32 is more preferable.
In addition, as shown in Figures 2 and 3, in this embodiment, first chamber 1a is located at the axial first end of valve element 1 and the Between two closeouts 32.Specifically, first chamber 1a is located at the axial first end of valve element 1, the second closeouts 32, the first plunger 21 And second through hole 51 inwall between.First chamber 1a connects with external control hydraulic fluid port X, the control oil energy that such external control hydraulic fluid port X is introduced Enough enter in first chamber 1a, and act on the axial first end of valve element 1, valve element 1 is produced from the first working position to the second work Make the dynamic trend of displacement, be easy to valve element 1 to switch to the second working position by the first working position under outer oil-control mouth X control action. Wherein, in order to further improve sealing effectiveness, as shown in Fig. 2 sealing ring 6 is additionally provided between the second closeouts 32 and housing 5, should Sealing ring 6 can be realized body more closely to be sealed to first chamber 1a.
In summary understand, in this embodiment, first chamber 1a is located at the axial first end and the second closeouts of valve element 1 Between 32, connected with external control hydraulic fluid port X；Second chamber 1b and the 3rd chamber 1c is located on valve element 1 and is located at the axial direction of valve element 1 respectively First end and axially the second end, wherein, the 3rd chamber 1c connects with feedback hydraulic fluid port C, and second chamber 1b and the 3rd actuator port Z Connection and priority and the second actuator port L and the first work during valve element 1 moves in the first working position to the second working position Make hydraulic fluid port Y connections.
Specifically, from Fig. 2-4, the valve element 1 of the embodiment, it has four sealing sections successively vertically, respectively It is close to seal section the 12, the 3rd along the first sealing section 11, second being sequentially distributed by axial first end to axially the second end Seal section 13 and the 4th and seal section 14, and the inwall of this four sealings sections and the second through hole 51 is slidingly sealed.Adjacent is close There is necking section between envelope section.So, can lead to during valve element 1 is mobile between the first working position and the second working position This four sealing sections are crossed to control first chamber 1a, second chamber 1b and the 3rd chamber 1c and each hydraulic fluid port connected relation.
Wherein, as shown in Fig. 2 when valve element 1 is in the first working position (rightmost in figure), the first sealing section 11 is to the The inner wall surface between first chamber 1a and the second actuator port L of two through holes 51 is sealed, so as to by first chamber 1a isolates with the second actuator port L, ensures that first chamber 1a only connects with external control hydraulic fluid port X；Meanwhile second sealing section 12 to the The inner wall surface between second chamber 1b and the first actuator port Y of two through holes 51 is sealed, and the first sealing section 11 and second sealing section 12 between necking section to the second through hole 51 between second chamber 1b and the second actuator port L Inner wall surface formed avoid so that second chamber 1b connected with the second actuator port L and with the first actuator port Y every From；3rd sealing section 13 enters to the inner wall surface between the first actuator port Y and the 3rd chamber 1c of the second through hole 51 Row sealing, meanwhile, the necking section that the 3rd sealing section 13 and the 4th is sealed between section 14 is located at the 3rd to the second through hole 51 Inner wall surface between chamber 1c and feedback hydraulic fluid port C, which is formed, to be avoided, and the 4th sealing section 14 is anti-to being located at for the second through hole 51 Inner wall surface between feedback hydraulic fluid port C and spring cavity is sealed so that the 3rd chamber 1c and the first actuator port Y and spring cavity are equal Isolation, and only connected with feedback hydraulic fluid port C.
And as shown in figure 3, when valve element 1 is in the second working position (leftmost in figure), the first sealing section 11 is still to the The inner wall surface between first chamber 1a and the second actuator port L of two through holes 51 is sealed, and realizes first chamber 1a With isolating for the second actuator port L, ensure that first chamber 1a only connects with external control hydraulic fluid port X；But differently, the second sealing section 12 The inner wall surface between second chamber 1b and the second actuator port L of second through hole 51 is sealed, and the first sealing The necking section that section 11 and second is sealed between section 12 is located at second chamber 1b and the first actuator port Y to the second through hole 51 Between inner wall surface formed avoid so that second chamber 1b change into connected with the first actuator port Y and with the second work Make hydraulic fluid port L isolation；Although the 3rd sealing section 13 and the 4th seals section 14 and is moved to the left, the 3rd sealing section 13 and the 4th The necking section between section 14 is sealed still to the inwall table between the 3rd chamber 1c and feedback hydraulic fluid port C of the second through hole 51 Face, which is formed, to be avoided, meanwhile, the 3rd sealing section 13 still to the second through hole 51 positioned at the first actuator port Y and the 3rd chamber 1c it Between inner wall surface sealed, and the 4th sealing section 14 still to second through hole 51 positioned at feedback hydraulic fluid port C and spring cavity it Between inner wall surface sealed so that the 3rd chamber 1c still isolates with the first actuator port Y and spring cavity, and still only Connected with feedback hydraulic fluid port C.
It can be seen that in this embodiment, when valve element 1 is in the first working position, first chamber 1a connects with external control hydraulic fluid port X, Second chamber 1b is connected and isolated with the first actuator port Y, the 3rd chamber 1c with the second actuator port L and the 3rd actuator port Z Connected with feedback hydraulic fluid port C；And when valve element 1 is in the second working position, first chamber 1a connects with external control hydraulic fluid port X, second chamber 1b is connected with the first actuator port Y and the 3rd actuator port Z and isolated with the second actuator port L, the 3rd chamber 1c and feedback oil Mouth C connections.
The principle of gearshift and boundary condition is controlled to enter the embodiment running motor shift valve 100 with reference to Fig. 2 and Fig. 3 Row explanation.
First, describe for convenience, by the first actuator port Y, the second actuator port L, the 3rd actuator port Z, outer oil-control Mouth X and feedback hydraulic fluid port C pressure are respectively defined as PY、PL、PZ、PXAnd PC, and by first chamber 1a, second chamber 1b and the 3rd chamber Room 1c effective pressure active area is respectively defined as A1、A2And A3, by spring 4 in the first working position and the second working position to valve The active force that core 1 applies is respectively defined as F1And F2, and discharge capacity of the motor 400 in the first working position and the second working position is divided V is not defined as it1And V2.Because the second actuator port L connects with fuel tank, it is therefore contemplated that PL=0.Further, since such as preceding institute To state, the first actuator port Y and feedback hydraulic fluid port C pressure are actually the actual working pressure of motor 400, therefore, PY=PC。
Based on above-mentioned, due to as shown in Figure 2 and as it was previously stated, when valve element 1 be in the first working position, first chamber 1a and outside Oil-control mouth X is connected, and second chamber 1b connects with the second actuator port L and the 3rd actuator port Z, the 3rd chamber 1c and feedback hydraulic fluid port C is connected, and the elastic force of spring 4 is F1, therefore, valve element 1 is slided in the second through hole 51 ignoring hydraulic power and frictional force Influence, can obtain the force balance state equation of valve element 1 now is：
PX×A1+PL×A2=PC×A3+F1 (1)。
Due to PL=0, therefore, it can derive in outer oil-control mouth X control pressures PXIn the presence of, can be by valve element 1 by One working position is pushed to the second working position, i.e. running motor can be switched to the feedback hydraulic fluid port C of fast mode by low-speed mode Pressure PC(i.e. the actual working pressure of motor 400) should meet：
PC＜ (PX×A1-F1)/A3 (2)。
And then understand, in outer oil-control mouth X control pressures PXIn the presence of, running motor is switched at a high speed by low-speed mode The boundary condition (referred to as boundary condition 1) of pattern is：
PC1=(PX×A1-F1)/A3 (3)。
The PC1It is referred to as the first preset value.It follows that when feedback hydraulic fluid port C oil pressure is less than the first preset value PC1When, valve Core 1 can be moved to the second working position by the first working position.
And due to as shown in Figure 3 and as it was previously stated, when valve element 1 be in the second working position, first chamber 1a and outer oil-control Mouth X connections, second chamber 1b connect with the first actuator port Y and the 3rd actuator port Z, and the 3rd chamber 1c connects with feedback hydraulic fluid port C Logical, the elastic force of spring 4 is F2, therefore, in the shadow ignored hydraulic power and frictional force and slided to valve element 1 in the second through hole 51 Ring, can obtain the force balance state equation of valve element 1 now is：
PX×A1+PY×A2=PC×A3+F2 (4)。
Due to PY=PC, therefore, can derive that valve element 1 can be moved to the first working position by the second working position, i.e. OK The enough feedback hydraulic fluid port C that low-speed mode is switched to by fast mode of Danone of galloping along on horseback pressure PC(the i.e. real work pressure of motor 400 Power) it should meet：
PC＞ (PX×A1-F2)/(A3-A2) (5)。
And then understand, running motor is switched to boundary condition (the referred to as boundary condition of low-speed mode by fast mode 2) it is：
PC2=(PX×A1-F2)/(A3-A2) (6)。
The PC2It is referred to as the second preset value.It follows that when feedback hydraulic fluid port C oil pressure is more than the second preset value PC2When, valve Core 1 can be moved to the first working position by the second working position.
In order to prevent due to the switching repeatedly caused by being shifted gears based on same preset value the problem of, the embodiment is by One preset value PC1With the second preset value PC2It is arranged to unequal, so as to be based on formula (3) and formula (6), three can be obtained The area A of chamber1、A2And A3Between corresponding relation.
Moreover, further, the embodiment also on the basis of the discharge capacity situation under considering the high low-speed mode of running motor, Pass through the area A to three chambers1、A2And A3Be designed, come control gearshift after motor 400 actual working pressure value so that The actual working pressure value that motor 400 after high speed is switched to by low speed is unsatisfactory for boundary condition 2, so as to it is anticipated that stable It is held in fast mode, and to be unsatisfactory for boundary condition by the actual working pressure value for switching to motor 400 after low speed at a high speed 1, so as to it is anticipated that be stably held in low-speed mode, and then more efficiently prevent from high low speed and send out with switching phenomenon repeatedly It is raw.
In order to facilitate description, by the first working position valve element 1 is moved into the second working position, and (i.e. running motor is switched by low speed To at a high speed) oil pressure (i.e. the actual working pressure of motor 400) that feeds back hydraulic fluid port C afterwards is calculated as the first working value PC3, and by valve element 1 by Second working position is moved to oil pressure (the i.e. horse that the first working position (i.e. running motor is switched at a high speed by low speed) feeds back hydraulic fluid port C afterwards Actual working pressure up to 400) it is calculated as the second working value PC4。
Based on this, in order that the actual working pressure value that motor 400 after high speed is switched to by low speed is unsatisfactory for boundary condition 2, it is easy to control running motor to be stable under fast mode, in this embodiment, the first working value PC3Boundary condition (the letter of satisfaction Referred to as boundary condition 3) be：
PC3＜ K1PC2, K1＜ 1, (7).
Wherein, because the maximal input of motor 400 is a steady state value, output torque T and the motor 400 of motor 400 Discharge capacity V and input port pressure (i.e. actual working pressure) P meet：T=K × V × P, wherein K are proportionality coefficient, therefore, motor It is directly proportional between 400 output torque T and the discharge capacity V of motor 400 and input port pressure (i.e. actual working pressure) P, so as to, if Actual working pressure when motor is switched to high speed by low speed is PC1, then the actual working pressure P after switchingC3With PC1Between it is full Foot：PC3×V2=PC1×V1, so as to derive the first working value PC3For：
And then by formula (7), formula (8) and formula (3), it may be determined that the area A of three chambers1、A2And A3Between Corresponding relation.
In addition, similarly, in order that being unsatisfactory for border by the actual working pressure value for switching to motor 400 after low speed at a high speed Condition 1, it is easy to control running motor to be stable under low-speed mode, in this embodiment, the second working value PC4The perimeter strip of satisfaction Part (referred to as boundary condition 3) is：
PC4＞ K2PC1, K2＞ 1, (9).
Wherein, if actual working pressure when motor is by switching at a high speed low speed is PC2, then the real work pressure after switching Power PC4With PC2Between meet：PC4×V1=PC2×V2, so as to derive the first working value PC4For：
And then by formula (10), formula (9) and formula (6), it may be determined that the area A of three chambers1、A2And A3Between Corresponding relation.
From the foregoing, comprehensive boundary condition 1, boundary condition 2, boundary condition 3 and boundary condition 4, it may be determined that first Chamber 1a, second chamber 1b and the 3rd chamber 1c effective pressure active area A1、A2And A3Between relation.In other words, may be used With by effective pressure active area A1、A2And A3It is designed, to enable running motor shift valve 100 to be walked in control More stably it is held under desired velocity mode after motor gearshift, and is unlikely to switch repeatedly, causes complete machine to be trembleed.
So according to boundary condition 1, boundary condition 2, boundary condition 3 and boundary condition 4, to the walking horse shown in Fig. 2-4 Up to the first chamber 1a of shift valve 100 effective pressure active area A1, second chamber 1b effective pressure active area A2And 3rd chamber 1c effective pressure active area A3It is designed and checks, can effectively prevents the high low speed of running motor from cutting repeatedly Change.After the completion of design, the workflow of running motor shift valve 100 can be as follows：
When the actual working pressure of running motor is more than PC1When, outer oil-control can not promote valve element 1 to move to left, and running motor is only capable of Run in the low-speed mode；When the actual working pressure of running motor is less than PC1When, outer oil-control promotes valve element 1 to move to left, and waits to move to left When switching to the second working position (running motor switches to fast mode) to leftmost, valve element 1, by the limitation of border member 3, walking Motor pressure will be less than K1PC2, due to being unsatisfactory for boundary condition 2, therefore, running motor can be stablized to work in high speed mode； And when the actual working pressure of running motor is more than PC2When, under the collective effect of spring force and each closed chamber, valve element 1 moves to right, By the limitation of boundary condition 4, after low-speed mode is switched to, running motor pressure will be above K2PC1, due to being unsatisfactory for perimeter strip Part 1, therefore, running motor will stabilise under low-speed mode and run.
It can be seen that by making running motor shift valve 100 that there is first chamber 1a, second chamber 1b and the 3rd in the embodiment Chamber 1c, and respectively to first chamber 1a, second chamber 1b and the 3rd chamber 1c effective pressure active area A1、A2And A3Enter Row design, running motor can be controlled stably to be held in after gearshift under corresponding mode of operation, without frequent Ground switches repeatedly, so as to efficiently solve complete machine wobble problem, is advantageous to extend running motor shift valve 100, walking horse Reach or even the life-span of construction machinery product, improve the security of engineering machinery traveling.The control being additionally, since outside without plus Element and detecting element etc., therefore, overall structure is relatively simple, and control is more convenient, and control accuracy and functional reliability are relative It is higher, meanwhile, cost is relatively low.
Although in other embodiment (not shown), second chamber 1b and the 3rd chamber 1c can also be not provided with valve element 1 On, such as it can be arranged between valve element 1 and housing 5 or special valve body, but the embodiment is by second chamber 1b and the 3rd chamber Room 1c is arranged on valve element 1, and it is advantageous in that, can make it that the structure of running motor shift valve 100 is relatively simple compact, oil circuit Design it is more convenient, and cause only need mainly the structure of valve element 1 is designed, you can reduce the wind that high low speed switches repeatedly Danger, simpler convenience.
In addition, though the valve element 1 shown in Fig. 4, the diameters of its four sealing sections are identical, it is to be understood that, this not structure Into limitation of the present invention, for example, the different sealing section of valve element 1 is arranged to have different diameters, or in housing 5 etc. On open up some auxiliary ducts, can also make feasible.
Based on the running motor shift valve 100 of the present invention, present invention also offers a kind of running motor and a kind of engineering machine Tool.Wherein, running motor includes motor 400 and the swash plate controlling organization 500 with the swash plate drive connection of motor 400, also, its Also include the running motor shift valve 100 of the present invention, running motor shift valve 100 is arranged inside the housing 5 of motor 400.And Engineering machinery then includes the running motor of the present invention.The engineering machinery of present invention crawler belt machinery such as can be excavator.
The exemplary embodiment of the present invention is the foregoing is only, is not intended to limit the invention, all spirit in the present invention Within principle, any modification, equivalent substitution and improvements made etc., it should be included in the scope of the protection.

Claims (15)

1. a kind of running motor shift valve (100), it is characterised in that including valve element (1), the first actuator port (Y), the second work Hydraulic fluid port (L), the 3rd actuator port (Z), external control hydraulic fluid port (X) and feedback hydraulic fluid port (C), the valve element (1) have the first working position and Second working position, in first working position, first actuator port (Y) cut-off and second actuator port (L) with 3rd actuator port (Z) connection, in second working position, first actuator port (Y) and the described 3rd work Hydraulic fluid port (Z) connects and second actuator port (L) ends；First actuator port (Y) is used to connect with oil sources, and described the Two actuator ports (L) are used to connect with fuel tank, and the 3rd actuator port (Z) is used for the swash plate controlling organization with running motor (500) connect；The external control hydraulic fluid port (X) is used to guide control oil to act on the axial first end of the valve element (1) and made described Valve element (1) produces the trend moved from first working position to second working position, and the feedback hydraulic fluid port (C) is used for institute The actual working pressure for stating the motor (400) of running motor feeds back to axially the second end of the valve element (1) and makes the valve element (1) trend moved from second working position to first working position, also, the running motor shift valve are produced (100) it is provided so that：
The oil pressure of the feedback hydraulic fluid port (C) is less than the first preset value PC1When, the valve element (1) can be by first work shift Move to second working position, the oil pressure of the feedback hydraulic fluid port (C) and be more than the second preset value PC2When, the valve element (1) can be by Second working position is moved to first working position, wherein, the first preset value PC1With the second preset value PC2No It is equal；
Also, after the valve element (1) is moved to second working position by first working position, the feedback hydraulic fluid port (C) Oil pressure is the first working value PC3, after the valve element (1) switches to first working position by second working position, the feedback The oil pressure of hydraulic fluid port (C) is the second working value PC4, wherein, the first working value PC3With the second preset value PC2Between meet PC3＜ K1PC2, K1≤ 1, and the second working value PC4With the first preset value PC1Between meet PC4＞ K2PC1, K2≥1。
2. running motor shift valve (100) according to claim 1, it is characterised in that the running motor shift valve (100) first chamber (1a), second chamber (1b) and the 3rd chamber (1c), the first chamber (1a) and the external control are also included Hydraulic fluid port (X) connects, and the 3rd chamber (1c) connects with the feedback hydraulic fluid port (C), the second chamber (1b) and the described 3rd Actuator port (Z) is connected and cut during the valve element (1) moves from first working position to second working position Connected with second actuator port (L) and first actuator port (Y) with changing, and effective pressure of the second chamber (1b) Power active area is less than the effective pressure active area of the 3rd chamber (1c).
3. running motor shift valve (100) according to claim 2, it is characterised in that the running motor shift valve (100) spring (4) is also included, the spring (4) is arranged at axially the second end of the valve element (1) and the valve element (1) is applied Adding makes the valve element (1) produce active force from from second working position to the first working position mobile trend, and described first Preset value PC1For PC1=(PX×A1-F1)/A3, the second preset value PC2For PC2=(PX×A1-F2)/(A3-A2), described first Working value PC3ForSecond working value isWherein, PXFor the oil of the external control hydraulic fluid port (X) Pressure, A1、A2And A3Effective pressure of respectively described first chamber (1a), the second chamber (1b) and the 3rd chamber (1c) Power active area, F1And F2Respectively described spring (4) is in first working position and second working position to the valve element (1) active force applied, V1And V2Respectively described motor (400) is in first working position and second working position Discharge capacity.
4. running motor shift valve (100) according to claim 2, it is characterised in that the second chamber (1b) and institute The 3rd chamber (1c) is stated to be arranged on the valve element (1) and respectively positioned at the axial first end and axially second of the valve element (1) End.
5. running motor shift valve (100) according to claim 4, it is characterised in that the axial direction first of the valve element (1) End and the second end of axial direction are respectively equipped with the first plunger cavity (1f) and the second plunger cavity (1g), are provided with first plunger cavity (1f) First plunger (21), is provided with the second plunger (22) in second plunger cavity (1g), and the second chamber (1b) is positioned at described the Between the inwall of one plunger (21) and first plunger cavity (1f), the 3rd chamber (1c) is located at the second plunger (22) and institute Between the inwall for stating the second plunger cavity (1g).
6. running motor shift valve (100) according to claim 4, it is characterised in that is additionally provided with the valve element (1) One passage (1d), the second chamber (1b) pass through the first passage (1d) and first actuator port (Y) and described the A connection in two actuator ports (L)；And/or second channel (1e), the 3rd chamber are additionally provided with the valve element (1) (1c) is connected by the second channel (1e) with the feedback hydraulic fluid port (C).
7. according to any described running motor shift valves (100) of claim 1-6, it is characterised in that the running motor changes Gear valve (100) also includes the first closeouts (31), and first closeouts (31) are arranged at the axial direction second of the valve element (1) End, the spring (4) of the running motor shift valve (100) support the axle located at first closeouts (31) with the valve element (1) To between the second end and the valve element (1), which is applied, makes the valve element (1) produce from second working position to first work Make the active force of position mobile trend.
8. running motor shift valve (100) according to claim 7, it is characterised in that first closeouts (31) Spring accommodating chamber (31c) is provided with close to the surface of the valve element (1), the spring (4) is arranged at the spring accommodating chamber In (31c).
9. running motor shift valve (100) according to claim 7, it is characterised in that on first closeouts (31) First through hole (31a) is additionally provided with, the first through hole (31a) connects with the spring accommodating chamber (31c).
10. running motor shift valve (100) according to claim 7, it is characterised in that first closeouts (31) Surface away from the valve element (1) is provided with binding groove (31b).
11. according to any described running motor shift valves (100) of claim 1-6, it is characterised in that the valve element (1) Axial first end has necking section.
12. running motor shift valve (100) according to claim 11, it is characterised in that the circumferential table of the necking section Face is provided with groove (15).
13. a kind of running motor, including motor (400) and the swash plate control machine with the swash plate drive connection of the motor (400) Structure (500), it is characterised in that also include the running motor shift valve (100) as described in claim 1-12 is any, the walking The housing (5) that motor shift valve (100) is arranged at the motor (400) is internal.
14. running motor according to claim 13, it is characterised in that the housing (5) is provided with the second through hole (51), The valve element (1) of the running motor shift valve (100) is placed in second through hole (51), and the running motor shift valve (100) the first actuator port (Y), the second actuator port (L), the 3rd actuator port (Z), external control hydraulic fluid port (X) and feedback hydraulic fluid port (C) on the inwall that may be contained within the housing (5).
15. a kind of engineering machinery, it is characterised in that including the running motor as described in claim 13 or 14.
CN201711246964.4A 2017-12-01 2017-12-01 Walking motor gear shifting valve, walking motor and engineering machinery Active CN107795538B (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201711246964.4A CN107795538B (en) 2017-12-01 2017-12-01 Walking motor gear shifting valve, walking motor and engineering machinery
KR1020207013037A KR102273877B1 (en) 2017-12-01 2018-03-15 Travel motor switching valve, travel motor and civil machinery
JP2020517249A JP7162659B2 (en) 2017-12-01 2018-03-15 Travel motor shift valves, travel motors and engineering machinery
DE112018002268.4T DE112018002268T5 (en) 2017-12-01 2018-03-15 Traction motor switching valve, traction motor and construction machine
PCT/CN2018/079068 WO2018188449A1 (en) 2017-12-01 2018-03-15 Travel motor shift valve, travel motor and construction machine

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KR (1) KR102273877B1 (en)
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WO2018188449A1 (en) 2018-10-18
CN107795538B (en) 2023-09-08
JP7162659B2 (en) 2022-10-28
JP2020523521A (en) 2020-08-06
DE112018002268T5 (en) 2020-02-20
KR20200060502A (en) 2020-05-29

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