CN1172912A - Variable priority device - Google Patents
Variable priority device Download PDFInfo
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- CN1172912A CN1172912A CN97115006A CN97115006A CN1172912A CN 1172912 A CN1172912 A CN 1172912A CN 97115006 A CN97115006 A CN 97115006A CN 97115006 A CN97115006 A CN 97115006A CN 1172912 A CN1172912 A CN 1172912A
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- pump
- piston
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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
- F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
- F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
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- 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
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
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- 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
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
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- 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
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2271—Actuators and supports therefor and protection therefor
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
A changeable prior device of the invention is provided with a logic valve. The logic valve is arranged in a pump access of a lower voltage side in an oil pressure line which drives a plurality of operation devices by a pump and interdicts the pump access in positive ratio with a preset signal. The invention is characterized in that the invention is provided with a sequence moving valve and the sequence moving valve identifies a control pressure that can lead a high load operation device in the oil pressure line to move, feeds back a moving oil pressure from the pump and supplies an output signal controlling the area of a throttle hole of the logic valve.
Description
The present invention relates to variable priority device, this variable priority device is used for being driven by a pump pressurized oil system of the heavy machineries such as excavator of a plurality of apparatus for work.Be particularly related to the variable priority device that has the sequentially-operating valve, this sequentially-operating valve identification can make the control of high load apparatus for work action press, feedback accepts the action oil of self-pumping, the throttle hole area of control logic valve, make time lag minimum, make low voltage side apparatus for work and high pressure side apparatus for work supply with prearranged signals simultaneously with moving in the high load apparatus for work action of low-load apparatus for work action back.
Usually, be applicable to the what is called " preferentially " of heavy machinery, be meant when discharge oil by a pump makes actuator composite move more than at least two, the actuator that requires high load is relatively supplied with the more control mode of heavy wool flow.Excavator for example for the arm speech but cycle is preferential, is the suspension rod priority scheduling for scraper bowl.Why to adopt this preferential, be because during cycle during required flow-rate ratio arm action required flow many, during the suspension rod action during required flow-rate ratio scraper bowl action required flow many.Equal difference ground supply flow makes the high load apparatus for work move with the travelling speed of low-load apparatus for work with being directly proportional like this, makes the flexible movements of whole machinery.
In the pressurized oil system of suspension rod that drives excavator and scraper bowl, adopt the method for this priority device, can require to use the fixing throttle orifice of using on the scraper bowl oil pressure supply line of low-load, but, use and fix when using throttle orifice, when the scraper bowl single movement, produce the pressure loss, as a result, the action of pump discharge is pressed and can not be made full use of by the low-load apparatus for work.
In order to improve this situation, develop a kind of order changeable controller in the prior art, this device is by the load pressure that acts on respectively on high load apparatus for work and the low-load apparatus for work, automatically determines the supply flow of low-load side.
That is, the variable priority device of this excavator as shown in Figure 1.In order to drive a plurality of actuator from a pump 1 by oil circuit 1A is suspension rod cylinder 3 and scraper bowl cylinder 6, the suspension rod driving is being set respectively on oil circuit 2A arranged side by side, the 5A that branches out from oil circuit 1A is driving with control valve (being designated hereinafter simply as " BKT ") 5 with control valve (being designated hereinafter simply as suspension rod) 2 and scraper bowl.Have piston 7 moving up and down, load one-way valve (load check) 9 and logical valve in the action oil supply passage 9A of BKT5, this logical valve has the piston pressure chamber 8 that is formed on piston 7 tops.Being formed on the bottom of load one-way valve 9 and the opening area of the throttle orifice 10 between the supply passage 9A becomes along with the variation in pressure of piston pressure chamber.Sequentially-operating valve 4 is connected with piston pressure chamber 8, so that pass through outlet side oil circuit 12 to piston pressure chamber 8 supply pressure oil.
As shown in Figure 2, the delivery outlet 12A of this sequentially-operating valve 4 is connected with outlet side oil circuit 12, and this outlet side oil circuit 12 is communicated with piston pressure chamber 8, exhaust port 18A with return oil circuit 18 and be connected.Similarly, pump aperture 11A is connected with the input side oil circuit 11 that branches out from oil circuit 1A.Sleeve is being inserted in inside at valve casing 40, but first guide piston 17 insert by the control pressure move left and right of control oil channel 23 ground, this control oil channel 23 is to press the oil circuit of Pi branch to come out from supply with control to suspension rod control valve 2.Spring 15 supportings that are reset of the other end of the valve plug 13 that joins with an end of first guide piston 17 land and insert sleeve 14, form internal path 30 on valve plug 13.By moving of valve plug 13, pump aperture 11A is communicated with delivery outlet 12A, at the cylindrical shape inner room 32 that central authorities' formation of this valve plug 13 is communicated with internal path 30, and the end of this cylindrical shape inner room 32 and at protuberance 16 interlocks of the other end projection of valve casing 40.
Under the state of this structure, during excavation, when carrying out the composite move of suspension rod UP and scraper bowl IN, the control that drives suspension rod 2 usefulness presses Pi to act on the first guide piston 17 of sequentially-operating valve 4 by oil circuit 23, and first guide piston 17 is moved on the drawing of Fig. 2 to the right.Like this, the elastic force that overcomes Returnning spring 15 with the valve plug 13 of first guide piston 17 interlocks pushes to the right, by internal path 30 pump aperture 11A is communicated with delivery outlet 12A.Therefore, action oil is fed into delivery outlet 12A, and the pressure of piston pressure chamber 8 rises, and piston 7 and load one-way valve 9 move towards the below.Thereby the opening area of throttle orifice 10 diminishes, and the action oil flow that flows into scraper bowl 5 by oil pressure pump 1 reduces.As a result, be used to drive the action oil flow increase of suspension rod.The X-axis of Fig. 6 represents to supply with the pilot pressure Pi of sequentially-operating valve 4, Y-axis represent to act on the outlet side aperture 12A of sequentially-operating valve 4 pressure, be the oil pressure of piston pressure chamber 8.As shown in the figure, when initial pilot pressure Pi rose, because valve plug 13 moves to right-hand, the internal path 30 that is communicated with delivery outlet 12A became the state that is communicated with pump aperture 11A, and the pressure of outlet side oil circuit 12 is linear to be increased.In addition, owing to internal path 30 is being communicated with cylindrical shape inner room 32, so the action that forms pump aperture 11A in cylindrical shape inner room 32 is pressed.Under this state, the basal area of establishing first guide piston 17 is A
1, the basal area of cylindrical shape inner room 32 is A
2, control is pressed and is Pi, and the pressure of cylindrical shape inner room 32 is P
1, the elastic force of Returnning spring 15 is F
S1, then the equilibrium of forces state in the sequentially-operating valve 4 is a following formula.
PiA
1＝P
1A
2+F
s1……(1)
In the formula, equal sign left side formula is the power of expression with valve plug 13 thruster to the right, and equal sign right side formula is the power of expression with valve plug 13 thruster left.Because F
S1Be constant, so establish P
1For certain, when Pi is increased, the ground valve plug 13 that is directly proportional moves to the right side, the open area of pump aperture 11A is linear to be increased.As a result, the action of delivery outlet 12A is pressed and is the A line states among Fig. 6, at this moment, and the Pi of A line
1The pilot pressure of expression scraper bowl initial actuating, Pi
2The pilot pressure of expression suspension rod initial actuating.
But, when suspension rod and scraper bowl composite move, (make the operating pressure Pi of suspension rod action because of operating pressure is poor
2Than the operating pressure Pi that makes the scraper bowl action
1Big relatively) UP of suspension rod action do not carry out, and only carries out (Pi between the control nip of IN action at scraper bowl
1～Pi
2) take place.As a result, apparatus for work is pressed by the control in this interval and is driven in turn.Therefore, can not be by operator's intention performance operation function, and also running feels bad, operating efficiency is low.
The object of the present invention is to provide a kind of preferential variset from the control pressure to logical valve that supply with, this device can make the setting of high load apparatus for work action press i.e. control to press to the high pressure side control valve identification that requires the high load apparatus for work to supply with action oil, before arriving this setting pressure, the low-load apparatus for work is driven.
Another object of the present invention provides a kind of preferential variset, this device feedback accepts the action oil pressure of self-pumping, the area of control throttle orifice, make the delay minimum of the time of high load apparatus for work action after the action of low-load apparatus for work, low voltage side apparatus for work and high pressure side apparatus for work are moved simultaneously, improve the operating efficiency of machinery.
To achieve these goals, variable priority device of the present invention has logical valve, this logical valve is located in the pump path of low voltage side control valve, and this low voltage side control valve is positioned at by a pump and drives on the oil pressure line of a plurality of apparatus for work, and this logical valve is blocked the said pump path with prearranged signals with being directly proportional; It is characterized in that, have the sequentially-operating valve, this sequentially-operating valve identification can make the control of the high load apparatus for work action that is positioned on the oil pressure line press, and feedback accepts the action oil pressure of self-pumping, supplies with the output signal of control logic valve throttle hole area.
One of better feature of the present invention is that the said sequence operating valve has valve casing, first guide piston, piston, limit position part, identification mechanism, sleeve, valve plug, internal path, plunger, feedback mechanism.Be formed with pump path, the outlet side path that is connected with logical valve, a plurality of drain passageway of the action oil of supply pump discharge on the valve casing, be formed with through hole in central authorities.Elder generation's guide piston inserts a side of above-mentioned through hole slidably, and a side is communicated with the control oil channel of high pressure side control valve, so that the inner hollow portion that forms of first guide piston itself is pressed in the control that effect drives the high pressure side control valve.Piston inserts an end of above-mentioned hollow portion slidably, has the bar that is fixed on end itself.Limit position part inserts the other end of above-mentioned hollow portion slidably, and the other end is in the outside of piston projection.Identification mechanism is positioned at the inside of above-mentioned hollow portion, is used to discern the control that the high load apparatus for work is driven and presses.Sleeve is inserted in the opposite side of above-mentioned through hole regularly, is formed with the pump aperture, delivery outlet and the exhaust port that are communicated with respectively with said pump path, outlet side path and drain passageway.Valve plug inserts above-mentioned sleeve inner slidably, and an end is connected with the limit position part of first guide piston, and the other end is flexibly being supported by Returnning spring.Internal path is formed on an end of above-mentioned valve plug, the original state that is communicated with exhaust port with the pump aperture from above-mentioned sleeve of valve plug be moved into direct ratio ground, blocking-up said pump aperture is communicated with exhaust port, makes the area increase that is communicated with delivery outlet.Plunger is fixed on the other end of above-mentioned valve casing through hole, supports the other end of above-mentioned Returnning spring.Feedback mechanism is resisted above-mentioned control and is pressed, and makes valve plug be converted to original state.
Two of better feature of the present invention is, above-mentioned identification mechanism has elastic member, this elastic member is located at piston between piston and the limit position part with remaining on a skidding journey end state, limit position part is remained on opposite side end of travel state ground elastic biasing, and make between the end of the other end of above-mentioned load and limit position part and keep certain intervals.
Three of better feature of the present invention is that above-mentioned feedback mechanism has cylindrical shape inner room that is communicated with above-mentioned internal path, be formed on above-mentioned valve plug inside and the protuberance that inserts the cylindrical shape inner room from above-mentioned plunger protrusion, an end.
Four of better feature of the present invention is, in order to limit the opening area of above-mentioned low voltage side pump path, low-load apparatus for work and high load apparatus for work are moved simultaneously, the elastic force of above-mentioned elastic member is set for sequence control and is pressed the power that acts on the first guide piston basal area identical, and this sequence control pressure is that the control when the said sequence valve equipped at outlet port that drives logical valve forms pressure is pressed.
As mentioned above, according to variable priority device of the present invention, can make the setting of high load apparatus for work action press i.e. control to press in the identification of high pressure side control valve, before not reaching this setting pressure, not making the low voltage side apparatus for work supply with control to logical valve drivingly presses, feedback accepts the action oil pressure of self-pumping, the throttle hole area of control logic valve, the time lag of high pressure side, low voltage side apparatus for work action back apparatus for work action is minimized, low voltage side apparatus for work and high pressure side apparatus for work are side by side moved, can improve the operating efficiency of machinery.
Fig. 1 is the tectonic maps of existing variable priority device.
Fig. 2 is the enlarged view of the sequentially-operating valve among Fig. 1.
Fig. 3 is the variable priority device general structural map of one embodiment of the invention.
Fig. 4 is the enlarged view of the sequentially-operating valve among Fig. 3.
Fig. 5 (a) (b) (c) is the sequence valve movement state diagram of Fig. 4 (d).
Fig. 6 is that control that expression acts on the sequentially-operating valve presses the plotted curve that the sequentially-operating valve outlet side oil pressure that rises and cause changes.
The following describes embodiments of the invention.
Fig. 3 is the variable priority device general structural map of one embodiment of the invention.Fig. 4 is the enlarged view of the sequentially-operating valve among Fig. 3.Fig. 5 (a) (b) (c) is the sequence valve movement state diagram of Fig. 4 (d).Fig. 6 is that control that expression acts on the sequentially-operating valve presses the plotted curve that the sequentially-operating valve outlet side oil pressure that rises and cause changes.
The variable priority device of present embodiment being driven in the oil pressure line of a plurality of apparatus for work 3,6 by an oil pressure pump 1, is distinguished into low-load apparatus for work 6 and high load apparatus for work 3 as shown in Figure 3.The preferential variset of present embodiment is applicable to the heavy machineries such as excavator that have logical valve LV, and above-mentioned logical valve is arranged among the pump path 9A of low voltage side control valve 6, so that block pump path 9A with prearranged signals with being directly proportional.
Low-load actuator 6 that is driven by oil pressure pump 1 and high load actuator 3, according to control signal Pi switch the action oil of supplying with these actuator low voltage side and high pressure side control valve 5,2, be arranged among the low voltage side pump path 9A logical valve LV and with Fig. 1, the essentially identical parts of prior art illustrated in fig. 2, annotate in the present embodiment with Fig. 1, Fig. 2 in identical label, its detailed description is omitted.
The variable priority device of present embodiment contains sequentially-operating valve 25, and this sequentially-operating valve 25 is identified in high pressure side control valve 2 can make the control of high pressure side apparatus for work 3 actions press the (Pi of B line among Fig. 6
1), feedback accepts the action oil pressure P1 of self-pumping, supplies with the output signal of throttle orifice 10 areas of control logic valve.
Sequentially-operating valve 25 has valve casing 40, first guide piston 19, piston 22, guide member 20, identification mechanism, sleeve 14, valve plug 13, internal path 30, plunger 28, feedback mechanism as shown in Figure 4.Be formed with the pump path 11 of the action oil of supply pump 1 discharge, outlet side path 12, a plurality of drain passageway 18 that is connected with the piston pressure chamber 8 of logical valve LV on the valve casing 40, be formed with through hole 24 in central authorities.Elder generation's guide piston 19 inserts a side of above-mentioned through hole 24 slidably, one side is communicated with the control oil channel 23 that control oil channel from the high pressure side control valve branches out, so that press Pi in the control that effect drives high pressure side control valve 2, the first guide piston 19 inner hollow portions 26 that form own.Piston 22 inserts the end of the other end 26 of above-mentioned hollow portion slidably, has the bar 27 that is fixed on end itself.Limit position part 20 inserts the other end of above-mentioned hollow portion slidably, and the other end is in the outside of piston projection.Identification mechanism is positioned at the inside of above-mentioned hollow portion 26, is used to discern the control that the high load apparatus for work is driven and presses.Sleeve 14 is inserted in the opposite side of through hole 24 regularly, is formed with pump aperture 11A, the delivery outlet 12A and the exhaust port 18A that are communicated with respectively with pump path 11, outlet side path 12 and drain passageway 18.Valve plug 13 inserts above-mentioned sleeve 14 inside slidably, and an end is connected with the limit position part 20 of first guide piston 19, and the other end is flexibly being supported by Returnning spring 15.Internal path 30 is formed on an end of valve plug 13, the original state that is communicated with delivery port 18A with the pump aperture 11A from sleeve 14 of valve plug 13 be moved into being communicated with of direct ratio ground blocking-up pump aperture 11A and exhaust port 18A, make the area increase that is communicated with delivery outlet 12A.Plunger 28 is fixed on the other end of the through hole 24 of valve casing 40, the other end of supporting Returnning spring 15.Feedback mechanism is resisted above-mentioned control and is pressed Pi, makes valve plug 13 be converted to original state.
Above-mentioned piston 22 can be through hole 24 inner moving in the scope of maximum shift motion S1, and limit position part 20 can move in hollow portion 26 in the scope of maximum shift motion S2.
Above-mentioned identification mechanism has the elastic member 21 that keeps certain intervals between the end of the other end that makes bar 27 and limit position part 20, this elastic member 21 is located between piston 22 and the limit position part 20, so that in a side piston 22 is remained on the state of stroke end, makes limit position part 20 remain on the state of stroke end at opposite side.
Opening area for the supply passage 9A that limits the low voltage side control valve 5 that action oil that oil pressure pump 1 discharges supplied to, low-load apparatus for work 6 and high pressure side apparatus for work 5 are moved simultaneously, it is identical with driving force F1 that the elastic force of above-mentioned elastic member 21 is set for, this driving force F1 is when the pressure of the delivery outlet 12A of the sequentially-operating valve 25 that drives logical valve LV forms, and presses Pi to produce by the control that acts on first guide piston section.
If the elastic force of above-mentioned elastic member 21 is set the elastic force greater than Returnning spring 15 for, control presses Pi to do the time spent by control oil channel 23, Returnning spring 15 compression earlier, and valve plug 13 is moved.
In order to be communicated with internal path 30, above-mentioned feedback mechanism have the cylindrical shape inner room 32 that is formed on valve plug 13 inside and from plunger 28 projections, an end inserts the protuberance 16 of cylindrical shape inner room 32.
The following describes the action of the present embodiment of above-mentioned structure.
For the action of clearer and more definite present embodiment, along with the Pi rising is pressed in the control that acts on sequentially-operating valve 25, the variation in pressure state of delivery outlet 12A is divided into following three phases.The 1st stage was that make a concerted effort (being designated hereinafter simply as repulsion force Fr) of the elastic force FS1 of the pressure P 1 of elastic force FS2 and the cylindrical shape inner room 32 that acts on valve plug 13 of elastic member 21 of first guide piston 19 and Returnning spring 15 becomes state of equilibrium.The 2nd stage was to act on the driving force F2 that the control on the piston 22 of first guide piston 19 presses Pi to produce to become state of equilibrium with repulsion force Fr.The 3rd stage was if driving force F2 greater than repulsion force Fr, asks state of equilibrium again.This each stage carries out in turn.
Illustrate from the 1st stage that original state is carried out earlier.Shown in Fig. 5 (a), original state is valve plug 13 is in the left side end of travel under the effect of Returnning spring 15 a state, and an end of valve plug 13 pushes limit position part 20 to the left, and first guide piston 19 is in the state of left side end of travel.At this moment, valve plug 13 switches to the state that the pump aperture 11A that makes sleeve 14 is communicated with exhaust port 18A.
Under this state, oil pressure, the control that promptly drives high pressure side control valve 2 press Pi to supply to control oil channel 23, the driving force F1 that obtains is the elastic force FS1 of Returnning spring 15 greater than repulsion force Fr if the basal area A1 of first guide piston 19 and control pressure Pi multiply each other, and then first guide piston 19 and valve plug 13 move (seeing Fig. 5 (b)) to the right in the scope of stroke S1.At this moment, because the elastic force FS1 of elastic member 21 is greater than the elastic force FS2 of Returnning spring 15, so elastic member 21 does not shrink.Because moving of valve plug 13, the open state of pump aperture 11A locking exhaust port 18A, if be communicated with (this internal path 30 is communicated with the delivery outlet 12A of valve plug 13) with internal path 30, then the pump pressure P1 of pump aperture 11A affacts the cylindrical shape inner room 32 that is communicated with internal path 30.At this moment, acting on the repulsion force Fr of valve plug 13, is that the basal area A2 of cylindrical shape inner room 32 and pump pressure P1 multiply each other the making a concerted effort of elastic force FS2 of the power F2 that obtains and Returnning spring.If this repulsion force Fr is greater than the elastic force FS1 of elastic member 21, valve plug 13 pushing limit position parts 20 then, limit position part 20 with displacement distance S2 that bar 27 contacts in the side shifting (seeing Fig. 5 (c)) of turning left again.This state is to press Pi to rise with hypothesis control, driving force F1 greater than the elastic force FS1 of elastic member 21 as prerequisite, if driving force F1 less than elastic force FS1, then first guide piston 19 sidesway of turning left.
As a result, elastic member 21 shrinks, and valve plug 13 is left the time, and the equilibrium of forces state is a following formula
FS1=FS2+P1A2 ... (2) precondition is FS1＜PiA1.Therefore, parameter is P1 in the formula (2), the discharging operation of P1 and pump is pressed, the opening area of pump aperture 11A and internal path 30 is directly proportional, so to press be one regularly when pump is discharged, it is same value that the mobile position with valve plug 13 of internal path 30 opening areas is set the levoform and the right formula that make formula (2) for.
Under this state, it is big more that the discharge of pump 1 is pressed, FS2+P1A2) " FS1, in order to make the opening area minimum, the valve plug sidesway of turning left.In addition, limit position part 20 has omitted Fig. 5 (b) state at Fig. 5 (a) state and has switched to Fig. 5 (c) state, as a result, the time lag of moving at high pressure side, low voltage side apparatus for work action back apparatus for work minimizes, and low voltage side apparatus for work and high pressure side apparatus for work move simultaneously.At this moment, press identical if the elastic force FS1 of elastic member 21 is set at the control of initial driving high load apparatus for work, then shown in the B line of Fig. 6, at the Pi1 place, the pressure line of delivery outlet 12A rises to the setting elastic force FS1 of elastic member 21 in the drawings abreast with Y-axis.
The following describes the state that carried out for the 2nd stage from the 1st stage.Control press to continue is risen, and driving force F1 becomes under the state identical with the elastic force of elastic member 21, and the state that control presses Pi to act on driving force F2 on the area A 3 of piston 22 and the same value of repulsion force Fr is Pi on the B line of Fig. 6
1, have Pi
2Interval.
That is, have
PiA3=(P1A2+FS2) ... (3) pilot pressure is Pi
2At this state, valve plug 13 does not move, and is halted state.
At last, illustrate from the 2nd stage and carried out for the 3rd stage.Control presses Pi to continue to increase, and having overcome the middle equal sign right side of formula (3) formula is repulsion force Fr.At this moment, piston 22 formerly hollow portion 26 inwalls of guide piston 19 inside slides, and moves to the right side, and like this, the limit position part 20 that joins with bar 27 moves in the scope of shift motion S2, and valve plug 13 is moved.As a result, pump aperture 11A increases with the area that is communicated with of delivery outlet 12A, and the pressure of delivery outlet 12A rises.In addition, if the pressure of delivery outlet 12A rises, then repulsion force Fr rises, and when this repulsion force Fr overcame driving force F2, valve plug 13 re-moved the left side.Therefore, valve plug 13 is being followed the tracks of driving force F2 and is being continued to move with the point that repulsion force Fr becomes identical value, the result, at Fig. 5 (c) state (promptly to Fig. 5 (d) state, limit position part 20 has the state of stroke S2), feedback is received in the variable value of this state and promptly controls pump discharge pressure P1, the automatically mobile position of transfer valve 13 of pressing Pi and delivery outlet 12A.
Claims (5)
1. a variable priority device has logical valve, and this logical valve is located at by a pump and drives in the pump path of the low voltage side control valve in the oil pressure line of a plurality of apparatus for work, blocks the said pump path with prearranged signals with being directly proportional; It is characterized in that, have the sequentially-operating valve, this sequentially-operating valve identification can make the control of the high load apparatus for work action that is arranged in above-mentioned oil pressure line press, and feedback accepts the action oil pressure of self-pumping, supplies with the output signal of the above-mentioned logical valve throttle hole area of control.
2. variable priority device as claimed in claim 1 is characterized in that, the said sequence operating valve has valve casing, first guide piston, piston, limit position part, identification mechanism, sleeve, valve plug, internal path, plunger and feedback mechanism;
Be formed with pump path, the outlet side path that is connected with logical valve, a plurality of drain passageway of the action oil of supply pump discharge on the valve casing, be formed with through hole in central authorities;
Elder generation's guide piston inserts a side of above-mentioned through hole slidably, and a side is communicated with control oil channel from the high pressure side control valve, so that first guide piston inside formation hollow portion itself is pressed in the control that effect drives the high pressure side control valve;
Piston inserts the other end of above-mentioned hollow portion slidably, has the bar that is fixed on end itself;
Limit position part inserts the other end of above-mentioned hollow portion slidably, and the other end is in the outside of piston projection;
Identification mechanism is positioned at above-mentioned hollow portion inside, is used to discern the control that the high load apparatus for work is driven and presses;
Sleeve is inserted in the opposite side of above-mentioned through hole regularly, is formed with the pump aperture, delivery outlet and the exhaust port that are communicated with respectively with pump path, outlet side path and drain passageway;
Valve plug inserts above-mentioned sleeve inner slidably, and an end is connected with the limit position part of first guide piston, and the other end is flexibly being supported by Returnning spring;
Internal path is formed on an end of above-mentioned valve plug, the original state that is communicated with exhaust port with the pump aperture from sleeve of valve plug be moved into being communicated with of blocking-up pump aperture, direct ratio ground and exhaust port, make the area increase that is communicated with delivery outlet;
Plunger is fixed on the other end of valve casing through hole, the other end of supporting Returnning spring;
Feedback mechanism is resisted above-mentioned control and is pressed, and makes valve plug be converted to original state.
3. variable priority device as claimed in claim 2, it is characterized in that, above-mentioned identification mechanism has elastic member, this elastic member is located at piston between piston and the limit position part with remaining on a skidding journey end state, limit position part is remained on opposite side end of travel state ground elastic biasing, and make between the end of the other end of above-mentioned bar and limit position part and keep certain intervals.
4. variable priority device as claimed in claim 2 is characterized in that, above-mentioned feedback mechanism has cylindrical shape inner room that is communicated with above-mentioned internal path, be formed on above-mentioned valve plug inside and the protuberance that inserts the cylindrical shape inner room from above-mentioned plunger protrusion, an end.
5. variable priority device as claimed in claim 3, it is characterized in that, in order to limit the opening area of above-mentioned low voltage side pump path, low-load apparatus for work and high load apparatus for work are moved simultaneously, the elastic force of above-mentioned elastic member is set for sequence control and is pressed the power that acts on the first guide piston basal area identical, and the control when this sequence control presses the said sequence valve equipped at outlet port that drives logical valve to form pressure is pressed.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR29389/96 | 1996-07-19 | ||
| KR1019960029389A KR100205567B1 (en) | 1996-07-19 | 1996-07-19 | Variable priority apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1172912A true CN1172912A (en) | 1998-02-11 |
Family
ID=19466882
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN97115006A Pending CN1172912A (en) | 1996-07-19 | 1997-07-15 | Variable priority device |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPH1089308A (en) |
| KR (1) | KR100205567B1 (en) |
| CN (1) | CN1172912A (en) |
| DE (1) | DE19729387A1 (en) |
| GB (1) | GB2315521A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103775409A (en) * | 2012-10-22 | 2014-05-07 | 林德液压两合公司 | Hydrostatic driving system |
| CN110318440A (en) * | 2018-03-29 | 2019-10-11 | 神钢建机株式会社 | Rotary engineering machinery |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100464761B1 (en) * | 1997-11-29 | 2005-04-06 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | Heavy Machinery Hydraulics |
| KR100559230B1 (en) * | 1998-09-30 | 2006-06-07 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | varible priority device for heavy equipment |
| KR20010009599A (en) * | 1999-07-12 | 2001-02-05 | 양재신 | Logic valve |
| US6745564B2 (en) * | 2001-12-21 | 2004-06-08 | Volvo Construction Equipment Holding Sweden Ab | Hydraulic variable control apparatus for heavy construction equipment |
| KR100518767B1 (en) * | 2003-05-28 | 2005-10-06 | 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 | flow control device of construction heavy equipment actuator |
| JP5485007B2 (en) | 2010-05-07 | 2014-05-07 | 日立建機株式会社 | Hydraulic control device for work vehicle |
| CN105705706B (en) * | 2013-10-31 | 2017-10-10 | 沃尔沃建造设备有限公司 | Flow control valve for the engineering equipment with float function |
-
1996
- 1996-07-19 KR KR1019960029389A patent/KR100205567B1/en not_active IP Right Cessation
-
1997
- 1997-07-09 DE DE19729387A patent/DE19729387A1/en not_active Withdrawn
- 1997-07-14 GB GB9714826A patent/GB2315521A/en not_active Withdrawn
- 1997-07-15 JP JP9205368A patent/JPH1089308A/en active Pending
- 1997-07-15 CN CN97115006A patent/CN1172912A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103775409A (en) * | 2012-10-22 | 2014-05-07 | 林德液压两合公司 | Hydrostatic driving system |
| CN103775409B (en) * | 2012-10-22 | 2017-05-03 | 林德液压两合公司 | Hydrostatic driving system |
| CN110318440A (en) * | 2018-03-29 | 2019-10-11 | 神钢建机株式会社 | Rotary engineering machinery |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH1089308A (en) | 1998-04-07 |
| KR100205567B1 (en) | 1999-07-01 |
| GB2315521A (en) | 1998-02-04 |
| KR980009963A (en) | 1998-04-30 |
| DE19729387A1 (en) | 1998-01-22 |
| GB9714826D0 (en) | 1997-09-17 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C53 | Correction of patent for invention or patent application | ||
| CB02 | Change of applicant information |
Applicant after: Volvo Construction Equipment (Korea) Co., Ltd. Applicant before: Samsung Heavy Industries Co., Ltd. |
|
| COR | Change of bibliographic data |
Free format text: CORRECT: APPLICANT; FROM: SAMSUNG HEAVY INDUSTRIES CO., LTD. TO: VOLVO CONSTRUCTION EQUIPMENT(COREA)LTD. |
|
| C01 | Deemed withdrawal of patent application (patent law 1993) | ||
| WD01 | Invention patent application deemed withdrawn after publication |