CN104533863A - Rotary system control valve of crane - Google Patents
Rotary system control valve of crane Download PDFInfo
- Publication number
- CN104533863A CN104533863A CN201410838200.4A CN201410838200A CN104533863A CN 104533863 A CN104533863 A CN 104533863A CN 201410838200 A CN201410838200 A CN 201410838200A CN 104533863 A CN104533863 A CN 104533863A
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- Prior art keywords
- valve
- way
- directional control
- control valve
- rotary
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
Abstract
The invention discloses a rotary system control valve of a crane. The rotary system control valve comprises a rotary reversing valve, a buffer reversing valve, a safety valve, two two-position two-way pilot operated directional control valves, a compensation control damper, a pressure compensation valve, two oil supplement one-way valves, two buffer valve pilot-operated dampers, a pilot-operated overflow valve, two rectification one-way valves, a free sliding rotary valve and a rotary hydraulic motor. Bypass pressure compensation speed regulation is applied to the rotary system control valve, so flow control of a rotary system is irrelevant to load pressure, control pressure of a pressure compensation valve spring cavity comes from a motor oil inlet and is obtained through the two two-position two-way pilot operated directional control valves, and the compensation valve can work normally under the negative load working condition; the overflow valve is applied to perceiving load pressure signals, the buffer reversing valve is used for controlling the buffer flow rate, the through-flow area of a buffer valve port gradually increases and then decreases along with displacement of a valve element and finally becomes zero, a throttle loop is formed according to gradual changes of load pressure, and the system can be stably started and stopped when operating with loads.
Description
Technical field
The present invention relates to control valve, especially relate to a kind of crane rotation system control valve.
Background technique
Rotary system control valve applies hydraulic element very widely in Hoisting Machinery, is used for controlling the rotary motion that crane part is got off relatively, coordinates the actions such as lifting amplitude-change, weight is sent to another place specified from one in the turning radius.Rotary system all sets up selector valve, and make revolution along negative actuation, can ensure that job area is wide, work flexibly.Because when band carries revolution, revolution inertia is large, therefore need arrange rotary buffering valve, when having made braking or acceleration and deceleration suddenly, induced pressure impacts little, stable working, the operating life of component such as prolongation rotary fluid motor, revolving support etc.
Existing rotary system control valve can be divided into two classes, one class is integrated in multi-way valve, and set up trimmer valve, Fill valve to control revolution action at rotary fluid motor working hole, but because not being be specifically designed to revolution action, type selecting coordinates more difficult, the trimmer valve configured, Fill valve and free skating rotary valve etc. make complex structure, take up room large.The main reversing valve of another kind of rotary control valve is three six logical throttle grvernings, and through by-pass port pressure release during meta, along with the movement of commutation valve rod, oil inlet and oil return mouth is opened respectively, now filler opening and by-pass port parallel fluid flow, and assignment of traffic is relevant to the pressure reduction of two valve ports.Valve port opening is certain, during load variations, filler opening pressure reduction also can respective change, the flow entering rotary fluid motor is caused to change with induced pressure, the rotating speed of crane part is unstable, makes operating difficulties, and speed regulation characteristic steepening during heavy duty, valve rod travel slightly changes, and flow will wide variation.The rotary system control valve of three six logical shunt compensation speed governing classes can guaranteed flow uncorrelated with induced pressure, but because of flow loss when buffer portion adopts relief valve to make buffering is serious and meta time return opening be positive opening make braking time the various problems such as flow appearance rise, be not used widely.
Summary of the invention
In order to overcome three six logical throttling speed control circuit flows relevant to induced pressure and three six lead to the shortcoming that when shunt compensation flow control circuits cushion, flow loss is serious, the object of the present invention is to provide a kind of crane rotation system control valve, make flow control uncorrelated with induced pressure, during overload, buffer traffic loss is less simultaneously.
In order to achieve the above object, the technical solution used in the present invention is:
The present invention includes slewing directional control valve, buffering selector valve, safety valve, first 2/2-way pilot operated directional control valve, second 2/2-way pilot operated directional control valve, compensatory control damping, pressure-compensated valve, first repairing one-way valve, second repairing one-way valve, the first guide cavity filter screen of first trimmer valve, the first guide cavity filter screen of second trimmer valve, first trimmer valve guide damping, second trimmer valve guide damping, precursor overflow valve, first rectification one-way valve, second rectification one-way valve, free skating rotary valve and rotary fluid motor,
Two actuator port A1 of slewing directional control valve, the oil inlet and outlet A of B1 and rotary fluid motor, B mouth connects, the bypass hydraulic fluid port C of slewing directional control valve communicates with the filler opening n1 of pressure-compensated valve, the return opening n2 of pressure-compensated valve communicates with working connection oil return inlet T, the spring control chamber n3 of pressure-compensated valve is through the oil outlet m3 of compensatory control damping and the first 2/2-way pilot operated directional control valve and the second 2/2-way pilot operated directional control valve, m4 communicates, the filler opening m1 of the first 2/2-way pilot operated directional control valve and the second 2/2-way pilot operated directional control valve, m2 respectively with the oil inlet and outlet A of rotary fluid motor, B communicates, the pilot control fluid of the first 2/2-way pilot operated directional control valve and the second 2/2-way pilot operated directional control valve is from the first guide cavity fluid a of slewing directional control valve, b, the filler opening p3 of the first repairing one-way valve and the second repairing one-way valve all communicates with working connection oil return inlet T, the oil outlet p1 of the first repairing one-way valve and the second repairing one-way valve, p2 respectively with the oil inlet and outlet A of rotary fluid motor, B communicates, the buffering filler opening q3 of selector valve connects with the return opening y2 of precursor overflow valve, the filler opening y1 of precursor overflow valve connects with the oil outlet k3 of the first rectification one-way valve and the second rectification one-way valve, the filler opening k1 of the first rectification one-way valve and the second rectification one-way valve, k2 respectively with the A of rotary fluid motor, B mouth connects, the oil inlet and outlet z1 of free skating rotary valve, z2 respectively with the A of rotary fluid motor, B mouth connects, first trimmer valve guide damping, second trimmer valve guide damping respectively with the A of rotary fluid motor, B mouth communicates, the filler opening e1 of safety valve communicates with working connection high pressure hydraulic fluid port P, the oil outlet e2 of safety communicates with working connection oil return inlet T.
Described slewing directional control valve adopts housing configuration, valve rod is arranged in the endoporus of valve pocket to be formed and is slidably matched, valve pocket is arranged in the endoporus of valve body, and valve pocket is installed 8 groups of employing O RunddichtringO sealing hydraulic fluid ports, the right-hand member of valve pocket abuts against on valve body interior edge face, the left end of valve pocket is located with short end lid, the rotation direction of outer spring and inner spring is contrary, the first spring seat and the second spring seat are equipped with in spring both sides, the right-hand member of the first spring seat is located with valve rod convex shoulder, the left end of the first spring seat abuts against on valve body, the left end Steel Cable Baffle Ring of the second spring seat is fixed on valve rod, the right-hand member of the second spring seat abuts against long end and covers, short end lid and long end cover bolt are fixed on valve body, and inside installs an O RunddichtringO respectively, 2nd O RunddichtringO, the pilot control fluid of slewing directional control valve enters valve rod pilot control chamber in the end face of short end lid and long end lid.
Described first trimmer valve guide damping, the second trimmer valve guide damping are screw thread damping or annular damper, install the first filter screen before the first trimmer valve guide damping damping, install the second filter screen before the second trimmer valve guide damping damping.
Described slewing directional control valve two actuator ports A1, B1 of load when meta all do not communicate with working connection high pressure hydraulic fluid port P and working connection oil return inlet T.
The beneficial effect that the present invention has is:
When the present invention turns round commutation part meta, filler opening and oil return are for bearing opening, and returning meta at rotary braking valve rod can not affect the normal stopping of motor because of these two valve ports; Employing bypass pressure compensates, when filler opening and by-pass port parallel fluid flow, make the pressure reduction approximately equal of these two valve ports, load flow is only relevant to valve rod travel, the high pressure of motor two actuator ports is obtained by two pilot operated directional control valves, the pilot control fluid of pilot operated directional control valve, from the first guide cavity fluid of slewing directional control valve, makes recuperation valve spring chamber fluid always from the filler opening of motor, overcomes and use shuttle valve to cause the shortcoming of recuperation valve misoperation under negative load behavior.Revolution buffer portion adopts the combination of relief valve and buffering selector valve, and relief valve perception load pressure signal determines the keying of buffer loop, and buffering selector valve controlling water kick amount, make can slow down impact during system overpressure, and load flow can not lose seriously.
Accompanying drawing explanation
Fig. 1 is the hydraulic schematic diagram of crane rotation system control valve of the present invention.
Fig. 2 is the erection drawing of the slewing directional control valve part of crane rotation system control valve of the present invention.
In figure: 1, safety valve, 2, slewing directional control valve, 3a, first 2/2-way pilot operated directional control valve, 3b, second 2/2-way pilot operated directional control valve, 4, compensatory control damping, 5, pressure-compensated valve, 6a, first repairing one-way valve, 6b, second repairing one-way valve, 7, buffering selector valve, 8a, the first guide cavity filter screen of first trimmer valve, 8b, the first guide cavity filter screen of second trimmer valve, 9a, first trimmer valve guide damping, 9b, second trimmer valve guide damping, 10, precursor overflow valve, 11a, first rectification one-way valve, 11b, second rectification one-way valve, 12, free skating rotary valve, 13, rotary fluid motor, 14, short end lid, 15a, one O RunddichtringO, 15b, 2nd O RunddichtringO, 16, valve rod, 17, valve pocket, 18, valve body, 19, O RunddichtringO, 20a, first spring seat, 20b, second spring seat, 21, outer spring, 22, inner spring, 23, Steel Cable Baffle Ring, 24, long end lid.
Embodiment
Below in conjunction with drawings and Examples, the invention will be further described.
As shown in Figure 1, the present invention includes slewing directional control valve 2, buffering selector valve 7, safety valve 1, first 2/2-way pilot operated directional control valve 3a, second 2/2-way pilot operated directional control valve 3b, compensatory control damping 4, pressure-compensated valve 5, first repairing one-way valve 6a, second repairing one-way valve 6b, first trimmer valve first guide cavity filter screen 8a, second trimmer valve first guide cavity filter screen 8b, first trimmer valve guide damping 9a, second trimmer valve guide damping 9b, precursor overflow valve 10, first rectification one-way valve 11a, second rectification one-way valve 11b, free skating rotary valve 12 and rotary fluid motor 13.
Two actuator port A1 of slewing directional control valve 2, the oil inlet and outlet A of B1 and rotary fluid motor 13, B mouth connects, the bypass hydraulic fluid port C of slewing directional control valve 2 communicates with the filler opening n1 of pressure-compensated valve 5, the return opening n2 of pressure-compensated valve 5 communicates with working connection oil return inlet T, the spring control chamber n3 of pressure-compensated valve 5 is through the oil outlet m3 of compensatory control damping 4 and the first 2/2-way pilot operated directional control valve 3a and the second 2/2-way pilot operated directional control valve 3b, m4 communicates, the filler opening m1 of the first 2/2-way pilot operated directional control valve 3a and the second 2/2-way pilot operated directional control valve 3b, m2 respectively with the oil inlet and outlet A of rotary fluid motor 13, B communicates, the pilot control fluid of the first 2/2-way pilot operated directional control valve 3a and the second 2/2-way pilot operated directional control valve 3b is from the first guide cavity fluid a of slewing directional control valve 2, b, the filler opening p3 of the first repairing one-way valve 6a and the second repairing one-way valve 6b all communicates with working connection oil return inlet T, the oil outlet p1 of the first repairing one-way valve 6a and the second repairing one-way valve 6b, p2 respectively with the oil inlet and outlet A of rotary fluid motor 13, B communicates, the buffering filler opening q3 of selector valve 7 connects with the return opening y2 of precursor overflow valve 10, the filler opening y1 of precursor overflow valve (10) connects with the oil outlet k3 of the first rectification one-way valve 11a and the second rectification one-way valve 11b, the filler opening k1 of the first rectification one-way valve 11a and the second rectification one-way valve 11b, k2 respectively with the A of rotary fluid motor 13, B mouth connects, the oil inlet and outlet z1 of free skating rotary valve 12, z2 respectively with the A of rotary fluid motor 13, B mouth connects, first trimmer valve guide damping 9a, second trimmer valve guide damping 9b respectively with the A of rotary fluid motor 13, B mouth communicates, the filler opening e1 of safety valve 1 communicates with working connection high pressure hydraulic fluid port P, the oil outlet e2 of safety valve 1 communicates with working connection oil return inlet T.
Described slewing directional control valve 2 adopts housing configuration, valve rod 16 is arranged in the endoporus of valve pocket 17 to be formed and is slidably matched, valve pocket 17 is arranged in the endoporus of valve body 18, and valve pocket 17 is installed 8 groups and adopt O RunddichtringOs 19 to seal hydraulic fluid port, the right-hand member of valve pocket 17 abuts against on valve body 18 interior edge face, the left end short end lid 14 of valve pocket 17 is located, the rotation direction of outer spring 21 and inner spring 22 is contrary, outer spring 21 is dextrorotation, inner spring 22 is that left-handed (or outer spring 21 is for left-handed, inner spring 22 is dextrorotation), the spring rate of inner spring 22 is greater than the spring rate of outer spring 21, and outer spring 21 is in compressive state time initial, inner spring 22 in the raw and and have certain interval between spring seat, the first spring seat 20a and the second spring seat 20b is equipped with in spring both sides, the right-hand member of the first spring seat 20a is located with valve rod 16 convex shoulder, the left end of the first spring seat 20a abuts against on valve body 18, the left end Steel Cable Baffle Ring 23 of the second spring seat 20b is fixed on valve rod 15, the right-hand member of the second spring seat 20b abuts against on long end lid 24, short end lid 14 and long end lid 24 are fixed by bolts on valve body, and inside installs an O RunddichtringO 15a respectively, 2nd O RunddichtringO 15b, the pilot control fluid of slewing directional control valve 2 enters valve rod 16 pilot control chamber in the end face of short end lid 14 and long end lid 24.
Described slewing directional control valve 2 is hexagon guiding valves, the all-round opening of the equal right and wrong of restriction, valve rod 16 has four convex shoulders.
Described first trimmer valve guide damping 9a, the second trimmer valve guide damping 9b are screw thread damping or annular damper, install the first filter screen 8a before the first trimmer valve guide damping 9a damping, install the second filter screen 8b before the second trimmer valve guide damping 9b damping.
Described slewing directional control valve 2 two actuator ports A1, B1 of load when meta all do not communicate with working connection high pressure hydraulic fluid port P and working connection oil return inlet T.
As shown in Figure 1 and Figure 2, the control procedure under the various running statees of rotary system control valve of the present invention is as follows:
Band carries and starts fast: slewing directional control valve 2 first guide cavity a passes into fluid and rises to maximum pilot pressure fast, then the rapid therefrom displacement of valve rod 16 is moved to upper, because when crane part band carries, rotary inertia is larger, during quick startup, rotary fluid motor 13 inlet pressure peak value exceedes the setting value of precursor overflow valve 10, precursor overflow valve 10 is opened, the first guide cavity of buffering selector valve 7 there is the first buffering guide damping 9a and second buffering guide damping 9b, the peak clipping of damping and delay action make to cushion selector valve 7 and start a certain transition position remaining on meta and upper interdigit instantaneously at rotary fluid motor 13, then superpressure fluid is through the second rectification one-way valve 11b, precursor overflow valve 10, buffering selector valve 7 flow to working connection oil return inlet T, pressure and the peak flow of rotary fluid motor 13 weaken, the smooth starting of crane part energy.Band carries speed difference that the is different or rising of guide's fluid, the pressure peak of rotary fluid motor 13 filler opening is also different, the flow area of buffering valve port along with the displacement of spool increase gradually after diminish again, be finally zero, revolution is cushioned and is divided into normal load to cushion and heavy duty buffering, during normal load, the higher buffer capacity of induced pressure peak value is stronger; During heavy duty, for making rotary fluid motor 13 flow few because cushioning loss, therefore buffering valve port flow area is less, makes buffer function slightly weak.It is identical that slewing directional control valve 2 first guide cavity b passes into working principle when fluid rises to maximum pilot pressure fast.
Band carries medium and small opening smooth running: the first guide cavity a of slewing directional control valve 2 leads to oil makes valve rod 16 be between meta and maximum displacement place, 2/2-way pilot operated directional control valve 3b commutates to upper, set the first 2/2-way selector valve 3a, the cracking pressure of the second 2/2-way selector valve 3b is greater than the cracking pressure of slewing directional control valve 2, the A mouth fluid of rotary fluid motor 13 enters the spring control chamber of pressure-compensated valve 5 through compensatory control damping 4, the effect of compensatory control damping 4 reduces the compression shock and the pulsation that enter recuperation valve spring chamber fluid.Now, fluid flowing point two-way in slewing directional control valve 2, one tunnel is that high pressure hydraulic fluid port P flows into working connection oil return inlet T after by-pass port C and pressure-compensated valve 5, and another road is that high pressure hydraulic fluid port P flow to working connection oil return inlet T through the return opening B1 of slewing directional control valve 2 after filler opening A1 inflow rotary fluid motor 13.Must when recuperation valve spring force be less by the pressure balance of by-pass port, filler opening and pressure-compensated valve 5, filler opening pressure reduction and by-pass port pressure reduction approximately equal, the flow of inflow two valve ports is only relevant to valve rod present position and have nothing to do with induced pressure, make the load capacity of rotary control system strong, governor control characteristics is good, handiness.Heavy duty smooth running and induced pressure are when exceeding the setting pressure of precursor overflow valve 10, and buffering selector valve 7 commutates to upper, and buffering valve port is imported and exported obstructed, and flow all flow to rotary fluid motor 13.When the first guide cavity b of slewing directional control valve 2 leads to oily, working principle is identical.
Band carries fast braking: the oil liquid pressure of the first guide cavity a of slewing directional control valve 2 drops quickly to zero, then valve rod 16 moves to meta from upper rapidly.Valve rod 16 gets back to meta, because the rotary inertia of crane part is larger, because effect of inertia crane part can continue motion, now the A mouth of rotary fluid motor 13 there will be negative pressure, through the second repairing one-way valve 6b repairing, the B mouth of rotary fluid motor 13 there will be high pressure, when exceeding the set pressure of precursor overflow valve 10, relief valve is opened, and fluid flow to working connection oil return inlet T through precursor overflow valve 10, buffering selector valve 7.When the oil liquid pressure of the first guide cavity b of slewing directional control valve 2 drops quickly to zero, working principle is identical.
Free rotary: the electromagnet energising of free skating rotary valve 12, selector valve commutation is to the logical pressure of A, B mouth of right position rotary fluid motor 13, rotary fluid motor 13 is in quick condition, the steel wire end of arm can be flapped toward above the center of gravity of weight automatically, and when avoiding lifting by crane, weight deflection produces additional force to arm.
Claims (4)
1. a crane rotation system control valve, it is characterized in that: comprise slewing directional control valve (2), buffering selector valve (7), safety valve (1), first 2/2-way pilot operated directional control valve (3a), second 2/2-way pilot operated directional control valve (3b), compensatory control damping (4), pressure-compensated valve (5), first repairing one-way valve (6a), second repairing one-way valve (6b), first guide cavity filter screen (8a) of first trimmer valve, first guide cavity filter screen (8b) of second trimmer valve, first trimmer valve guide damping (9a), second trimmer valve guide damping (9b), precursor overflow valve (10), first rectification one-way valve (11a), second rectification one-way valve (11b), free skating rotary valve (12) and rotary fluid motor (13),
Two actuator port A1 of slewing directional control valve (2), the oil inlet and outlet A of B1 and rotary fluid motor (13), B mouth connects, the bypass hydraulic fluid port C of slewing directional control valve (2) communicates with the filler opening n1 of pressure-compensated valve (5), the return opening n2 of pressure-compensated valve (5) communicates with working connection oil return inlet T, the spring control chamber n3 of pressure-compensated valve (5) is through the oil outlet m3 of compensatory control damping (4) and the first 2/2-way pilot operated directional control valve (3a) and the second 2/2-way pilot operated directional control valve (3b), m4 communicates, the filler opening m1 of the first 2/2-way pilot operated directional control valve (3a) and the second 2/2-way pilot operated directional control valve (3b), m2 respectively with the oil inlet and outlet A of rotary fluid motor (13), B communicates, the pilot control fluid of the first 2/2-way pilot operated directional control valve (3a) and the second 2/2-way pilot operated directional control valve (3b) is from the first guide cavity fluid a of slewing directional control valve (2), b, the filler opening p3 of the first repairing one-way valve (6a) and the second repairing one-way valve (6b) all communicates with working connection oil return inlet T, the oil outlet p1 of the first repairing one-way valve (6a) and the second repairing one-way valve (6b), p2 respectively with the oil inlet and outlet A of rotary fluid motor (13), B communicates, the filler opening q3 of buffering selector valve 7 connects with the return opening y2 of precursor overflow valve (10), the filler opening y1 of precursor overflow valve (10) connects with the oil outlet k3 of the first rectification one-way valve (11a) and the second rectification one-way valve (11b), the filler opening k1 of the first rectification one-way valve (11a) and the second rectification one-way valve (11b), k2 respectively with the A of rotary fluid motor (13), B mouth connects, the oil inlet and outlet z1 of free skating rotary valve (12), z2 respectively with the A of rotary fluid motor (13), B mouth connects, first trimmer valve guide damping (9a), second trimmer valve guide damping (9b) respectively with the A of rotary fluid motor (13), B mouth communicates, the filler opening e1 of safety valve (1) communicates with working connection high pressure hydraulic fluid port P, the oil outlet e2 of safety valve (1) communicates with working connection oil return inlet T.
2. a kind of crane rotation system control valve according to claim 1, it is characterized in that: described slewing directional control valve (2) adopts housing configuration, valve rod (16) is arranged in the endoporus of valve pocket (17) to be formed and is slidably matched, valve pocket (17) is arranged in the endoporus of valve body (18), and the upper installation 8 groups of valve pocket (17) adopts O RunddichtringO (19) sealing hydraulic fluid port, the right-hand member of valve pocket (17) abuts against on valve body (18) interior edge face, the left end of valve pocket (17) is located with short end lid (14), the rotation direction of outer spring (21) and inner spring (22) is contrary, the first spring seat (20a) and the second spring seat (20b) are equipped with in spring both sides, the right-hand member of the first spring seat (20a) is located with valve rod (16) convex shoulder, the left end of the first spring seat (20a) abuts against on valve body (18), the left end Steel Cable Baffle Ring (23) of the second spring seat (20b) is fixed on valve rod (15), the right-hand member of the second spring seat (20b) abuts against on long end lid (24), short end lid (14) and long end lid (24) are fixed by bolts on valve body, and inside installs an O RunddichtringO (15a) respectively, 2nd O RunddichtringO (15b), the pilot control fluid of slewing directional control valve (2) enters valve rod (16) pilot control chamber in the end face of short end lid (14) and long end lid (24).
3. a kind of crane rotation system control valve according to claim 1, it is characterized in that: described first trimmer valve guide damping (9a), the second trimmer valve guide damping (9b) are screw thread damping or annular damper, before first trimmer valve guide damping (9a) damping, the first filter screen (8a) is installed, before the second trimmer valve guide damping (9b) damping, the second filter screen (8b) is installed.
4. a kind of truck crane rotary system control valve according to claim 1, is characterized in that: described slewing directional control valve (2) two actuator ports A1, B1 of load when meta all do not communicate with working connection high pressure hydraulic fluid port P and working connection oil return inlet T.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201410838200.4A CN104533863B (en) | 2014-12-30 | 2014-12-30 | Crane rotation system control valve |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410838200.4A CN104533863B (en) | 2014-12-30 | 2014-12-30 | Crane rotation system control valve |
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| CN104533863A true CN104533863A (en) | 2015-04-22 |
| CN104533863B CN104533863B (en) | 2016-06-29 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106837906A (en) * | 2016-12-14 | 2017-06-13 | 武汉船用机械有限责任公司 | A kind of anchor capstan hydraulic control system |
| CN107355438A (en) * | 2017-07-25 | 2017-11-17 | 江苏柳工机械有限公司 | A kind of accessory control system |
| CN109592585A (en) * | 2018-12-12 | 2019-04-09 | 三汽车起重机械有限公司 | Crane rotation braking system and crane |
| CN111448113A (en) * | 2017-12-15 | 2020-07-24 | 法维莱运输亚眠公司 | Brake system for railway vehicles |
| CN112173976A (en) * | 2020-09-28 | 2021-01-05 | 徐州阿马凯液压技术有限公司 | Integrated spacing anti-resonance valve rod assembly structure |
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| CN201317637Y (en) * | 2008-12-23 | 2009-09-30 | 常德信诚液压有限公司 | Turning control assembly of hydraulic truck crane |
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