CN104533863B - Crane rotation system control valve - Google Patents
Crane rotation system control valve Download PDFInfo
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- CN104533863B CN104533863B CN201410838200.4A CN201410838200A CN104533863B CN 104533863 B CN104533863 B CN 104533863B CN 201410838200 A CN201410838200 A CN 201410838200A CN 104533863 B CN104533863 B CN 104533863B
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- directional control
- control valve
- damping
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- 239000012530 fluid Substances 0.000 claims abstract description 74
- 238000013016 damping Methods 0.000 claims abstract description 37
- 230000003139 buffering effect Effects 0.000 claims abstract description 29
- 239000002243 precursor Substances 0.000 claims abstract description 17
- 238000009434 installation Methods 0.000 claims description 2
- 238000006073 displacement reaction Methods 0.000 abstract description 4
- 230000008859 change Effects 0.000 abstract description 3
- 230000008447 perception Effects 0.000 abstract description 2
- 230000009467 reduction Effects 0.000 description 5
- 241000218158 Clematis Species 0.000 description 4
- 230000009471 action Effects 0.000 description 4
- 230000033001 locomotion Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Multiple-Way Valves (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a kind of crane rotation system control valve.Including slewing directional control valve, buffering reversal valve, relief valve, two 2/2-way pilot operated directional control valves, compensate and control damping, pressure-compensated valve, two repairing check valves, two trimmer valve guide dampings, precursor overflow valve, two rectification check valves, free skating rotary valve and rotary fluid motor.Present invention application bypass pressure compensator control, the flow-control making rotary system is uncorrelated with load pressure, the control pressure of pressure-compensated valve spring cavity, from motor oil-in, is obtained by 2/2-way pilot operated directional control valve so that recuperation valve can normal operation under negative load behavior；Application overflow valve perception load pressure signal, controlling buffer traffic with buffering reversal valve, the flow area of buffering valve port diminishes after being gradually increased along with the displacement of spool again, is finally zero, form the gradual change throttle circuit according to load pressure, can steadily start and stop when making system band carrying turn.
Description
Technical field
The present invention relates to control valve, especially relate to a kind of crane rotation system control valve.
Background technology
It is apply Hydraulic Elements very widely in hoisting machinery that rotary system controls valve, is used for controlling the rotary motion that crane part is got off relatively, coordinates the actions such as lifting amplitude-change, and weight is sent to another place specified from the radius of gyration.Rotary system all sets up reversal valve so that revolution can along negative actuation, it is ensured that job area is wide, and work is flexibly.During because of band load revolution, revolution inertia is big, therefore need to arrange rotary buffering valve so that when playing braking or acceleration and deceleration suddenly, load pressure impacts little, and stable working extends the working life of the parts such as rotary fluid motor, revolving support.
Existing rotary system controls valve can be divided into two classes, one class is integrated in banked direction control valves, and set up trimmer valve, Fill valve to control revolution action at rotary fluid motor working hole, but because not being used exclusively for revolution action, type selecting coordinates more difficult, the trimmer valve of configuration, Fill valve and free skating rotary valve etc. make structure complicated, take up room big.The main reversing valve of another kind of rotary control valve is three clematis stem throttle grvernings, and through by-pass port pressure release during middle position, along with the movement of commutation valve rod, oil inlet and oil return mouth is opened respectively, now oil-in 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 change, oil-in pressure reduction also can respective change, cause that the flow entering rotary fluid motor changes with load pressure, the speed of gyration of crane part is unstable so that operating difficulties, and speed regulation characteristic steepening during heavy duty, valve rod travel varies slightly, and flow will wide variation.The rotary system of three clematis stem shunt compensation speed governing classes controls valve can ensure that flow and load pressure are uncorrelated, but because of when buffer portion adopts overflow valve to make buffering, flow loss is serious and during middle position oil return opening be positive opening make braking time flow the various problems such as rise occur, it does not have be used widely.
Summary of the invention
For the shortcoming overcoming three clematis stem throttling speed control circuit flows relevant to load pressure and flow loss is serious during three clematis stem shunt compensation speed control loops bufferings, it is an object of the invention to provide a kind of crane rotation system control valve, making flow-control and load pressure uncorrelated, 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 reversal valve, relief valve, first 2/2-way pilot operated directional control valve, second 2/2-way pilot operated directional control valve, compensate and control damping, pressure-compensated valve, first repairing check valve, second repairing check valve, first trimmer valve elder generation guide cavity drainage screen, second trimmer valve elder generation guide cavity drainage screen, first trimmer valve guide damping, second trimmer valve guide damping, precursor overflow valve, first rectification check valve, second rectification check 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 oil-in n1 of pressure-compensated valve, the oil return opening n2 of pressure-compensated valve communicates with working connection oil return inlet T, the spring of pressure-compensated valve controls the compensated oil-out m3 controlling damping and the first 2/2-way pilot operated directional control valve and the second 2/2-way pilot operated directional control valve of chamber n3, m4 communicates, the oil-in 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 oil-in p3 of the first repairing check valve and the second repairing check valve all communicates with working connection oil return inlet T, the oil-out p1 of the first repairing check valve and the second repairing check valve, p2 respectively with the oil inlet and outlet A of rotary fluid motor, B communicates, the oil-in q3 of buffering reversal valve connects with the oil return opening y2 of precursor overflow valve, the oil-in y1 of precursor overflow valve and the oil-out k3 of the first rectification check valve and the second rectification check valve connects, the oil-in k1 of the first rectification check valve and the second rectification check 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 oil-in e1 of relief valve communicates with working connection high pressure hydraulic fluid port P, the oil-out 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 and is formed is slidably matched, valve pocket is arranged in the endoporus of valve body, and valve pocket is installed 8 groups of employing O RunddichtringOs sealing hydraulic fluid ports, the right-hand member of valve pocket abuts against on valve body inner face, the left end of valve pocket short end lid positions, outer spring and inner spring oppositely oriented, spring both sides are equipped with the first spring base and the second spring base, the right-hand member of the first spring base valve rod convex shoulder positions, the left end of the first spring base abuts against on valve body, the left end elastic spring of the second spring base is fixed on valve rod, the right-hand member of the second spring base abuts against on long end cap, short end lid and long end cap are fixed by bolts on valve body, and inside is respectively mounted an O RunddichtringO, 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 cap.
Described first trimmer valve guide damping, the second trimmer valve guide damping are screw thread damping or annular damper, install the first drainage screen before the first trimmer valve guide damping, install the second drainage screen before the second trimmer valve guide damping.
Two actuator ports A1, B1 of the load when middle position of described slewing directional control valve and working connection high pressure hydraulic fluid port P and working connection oil return inlet T are all not communicated with.
The invention have the advantages that:
It is negative opening with oil return that the present invention turns round oil-in during position in commutation part, and in rotary braking valve rod returns, position will not affect the normal stopping of motor because of the two valve port；Employing bypass pressure compensates, when oil-in is with by-pass port parallel fluid flow, make the pressure reduction approximately equal of the two valve port, load flow is only relevant to valve rod travel, the high pressure of two actuator ports of motor is obtained by two pilot operated directional control valves, the pilot control fluid of pilot operated directional control valve is from the first guide cavity fluid of slewing directional control valve so that recuperation valve spring cavity fluid always from the oil-in of motor, overcomes the shortcoming using shuttle valve to cause recuperation valve misoperation under negative load behavior.Revolution buffer portion adopts overflow valve and the combination of buffering reversal valve, and overflow valve perception load pressure signal determines the keying of buffer loop, and buffering reversal valve controls spillway discharge so that can slow down impact during system overpressure, and load flow will 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 installation diagram of the slewing directional control valve part of crane rotation system control valve of the present invention.
In figure: 1, relief 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, compensate and control damping, 5, pressure-compensated valve, 6a, first repairing check valve, 6b, second repairing check valve, 7, buffering reversal valve, 8a, first trimmer valve elder generation guide cavity drainage screen, 8b, second trimmer valve elder generation guide cavity drainage screen, 9a, first trimmer valve guide damping, 9b, second trimmer valve guide damping, 10, precursor overflow valve, 11a, first rectification check valve, 11b, second rectification check valve, 12, free skating rotary valve, 13, rotary fluid motor, 14, short end lid, 15a, oneth O RunddichtringO, 15b, 2nd O RunddichtringO, 16, valve rod, 17, valve pocket, 18, valve body, 19, O RunddichtringO, 20a, first spring base, 20b, second spring base, 21, outer spring, 22, inner spring, 23, elastic spring, 24, long end cap.
Detailed description of the invention
Below in conjunction with drawings and Examples, the invention will be further described.
As it is shown in figure 1, the present invention include slewing directional control valve 2, buffering reversal valve 7, relief valve the 1, first 2/2-way pilot operated directional control valve 3a, the second 2/2-way pilot operated directional control valve 3b, compensate control damping 4, pressure-compensated valve the 5, first repairing check valve 6a, the second repairing check valve 6b, the first trimmer valve elder generation guide cavity drainage screen 8a, the second trimmer valve elder generation guide cavity drainage screen 8b, the first trimmer valve guide damps 9a, the second trimmer valve guide damps 9b, precursor overflow valve the 10, first rectification check valve 11a, the second rectification check 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 oil-in n1 of pressure-compensated valve 5, the oil return opening n2 of pressure-compensated valve 5 communicates with working connection oil return inlet T, the spring of pressure-compensated valve 5 controls the compensated oil-out m3 controlling 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 of chamber n3, m4 communicates, the oil-in 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 oil-in p3 of the first repairing check valve 6a and the second repairing check valve 6b all communicates with working connection oil return inlet T, the oil-out p1 of the first repairing check valve 6a and the second repairing check valve 6b, p2 respectively with the oil inlet and outlet A of rotary fluid motor 13, B communicates, the oil-in q3 of buffering reversal valve 7 connects with the oil return opening y2 of precursor overflow valve 10, the oil-in y1 of precursor overflow valve (10) and the oil-out k3 of the first rectification check valve 11a and the second rectification check valve 11b connects, the oil-in k1 of the first rectification check valve 11a and the second rectification check 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 damps 9a, second trimmer valve guide damp 9b respectively with the A of rotary fluid motor 13, B mouth communicates, the oil-in e1 of relief valve 1 communicates with working connection high pressure hydraulic fluid port P, the oil-out e2 of relief 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 and is formed is slidably matched, valve pocket 17 is arranged in the endoporus of valve body 18, and valve pocket 17 is installed 8 groups adopt O RunddichtringOs 19 seal hydraulic fluid port, the right-hand member of valve pocket 17 abuts against on valve body 18 inner face, the left end short end lid 14 of valve pocket 17 positions, outer spring 21 and inner spring 22 oppositely oriented, 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 more 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 spring base between have certain interval, spring both sides are equipped with the first spring base 20a and the second spring base 20b, the right-hand member of the first spring base 20a valve rod 16 convex shoulder positions, the left end of the first spring base 20a abuts against on valve body 18, the left end elastic spring 23 of the second spring base 20b is fixed on valve rod 15, the right-hand member of the second spring base 20b abuts against on long end cap 24, short end lid 14 and long end cap 24 are fixed by bolts on valve body, and inside is respectively mounted an O RunddichtringO 15a, 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 cap 24.
Described slewing directional control valve 2 is six limit guiding valves, and the equal right and wrong of restriction all-round opening has four convex shoulders on valve rod 16.
Described first trimmer valve guide damps 9a, the second trimmer valve guide damp 9b be screw thread damping or annular damper, the first trimmer valve guide damp 9a damping before install the first drainage screen 8a, the second trimmer valve guide damp 9b damping before install the second drainage screen 8b.
Two actuator ports A1, B1 of the load when middle position of described slewing directional control valve 2 and working connection high pressure hydraulic fluid port P and working connection oil return inlet T are all not communicated with.
As shown in Figure 1 and Figure 2, the control process that rotary system of the present invention controls under the various running statuses of valve is as follows:
Band load quickly starts: the first guide cavity a of slewing directional control valve 2 passes into fluid and is quickly ramped up to maximum control pressure, then the rapid therefrom displacement of valve rod 16 is moved to upper, because when crane part band carries, rotary inertia is bigger, when quickly starting, 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 reversal valve 7 there is the first buffering guide damp 9a and the second buffering guide and damp 9b, the peak clipping of damping and delay action make buffering reversal valve 7 a certain transition position of position and upper interdigit in rotary fluid motor 13 starts and is momentarily held at, then superpressure fluid is through the second rectification check valve 11b, precursor overflow valve 10, buffering reversal valve 7 flow to working connection oil return inlet T, pressure and the peak flow of rotary fluid motor 13 weaken, crane part energy smooth starting.The speed that or guide fluid different with load rises is different, the pressure peak of rotary fluid motor 13 oil-in is also different, the flow area of buffering valve port diminishes after being gradually increased along with the displacement of spool again, it is finally zero, revolution buffering is made to be divided into normal load buffering and heavy duty buffering, during normal load, the more high buffer capacity of load pressure peak value is more strong；During heavy duty, for making rotary fluid motor 13 flow few because of buffering loss, therefore buffering valve port flow area is less, makes cushioning effect slightly weak.The first guide cavity b of slewing directional control valve 2 passes into fluid, and to be quickly ramped up to operation principle during maximum control pressure identical.
With carrying medium and small opening even running: the logical oil of the first guide cavity a of slewing directional control valve 2 makes valve rod 16 be between middle position and maximum displacement place, 2/2-way pilot operated directional control valve 3b commutation is to upper, set the first 2/2-way reversal valve 3a, the second 2/2-way reversal valve 3b open pressure more than the unlatching pressure of slewing directional control valve 2, the compensated spring controlling damping 4 entrance pressure-compensated valve 5 of the A mouth fluid of rotary fluid motor 13 controls chamber, and compensating the effect controlling damping 4 is the compression shock and pulsation that reduce and enter recuperation valve spring cavity 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 oil return opening B1 of slewing directional control valve 2 after oil-in A1 inflow rotary fluid motor 13.Must when recuperation valve spring force be less by the pressure balance of by-pass port, oil-in and pressure-compensated valve 5, oil-in pressure reduction and by-pass port pressure reduction approximately equal, the flow flowing into two valve ports is only relevant to valve rod present position and unrelated with load pressure, the load capacity making rotary control system is strong, governor control characteristics is good, handiness.When heavy duty even running and load pressure exceed the setting pressure of precursor overflow valve 10, buffering reversal valve 7 commutation is to upper, and buffering valve port is imported and exported obstructed, and flow all flow to rotary fluid motor 13.During the first guide cavity b of slewing directional control valve 2 logical oil, operation principle is identical.
With load 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 is rapidly from upper movement to middle position.Valve rod 16 returns to middle position, because the rotary inertia of crane part is bigger, owing to effect of inertia crane part may proceed to motion, now the A mouth of rotary fluid motor 13 there will be negative pressure, through the second repairing check 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, overflow valve is opened, and fluid flow to working connection oil return inlet T through precursor overflow valve 10, buffering reversal valve 7.It is identical that the oil liquid pressure of the first guide cavity b of slewing directional control valve 2 drops quickly to operation principle when zero.
Free rotary: the electric magnet energising of free skating rotary valve 12, reversal valve commutation leads to pressure to A, B mouth of right position rotary fluid motor 13, rotary fluid motor 13 is in quick condition, the steel wire end making arm can be flapped toward above the center of gravity of weight automatically, it is to avoid during lifting, arm is produced additional force by weight deflection.
Claims (4)
1. a crane rotation system control valve, it is characterized in that: include slewing directional control valve (2), buffering reversal valve (7), relief valve (1), first 2/2-way pilot operated directional control valve (3a), second 2/2-way pilot operated directional control valve (3b), compensate and control damping (4), pressure-compensated valve (5), first repairing check valve (6a), second repairing check valve (6b), first trimmer valve elder generation guide cavity drainage screen (8a), second trimmer valve elder generation guide cavity drainage screen (8b), first trimmer valve guide damping (9a), second trimmer valve guide damping (9b), precursor overflow valve (10), first rectification check valve (11a), second rectification check 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 oil-in n1 of pressure-compensated valve (5), the oil return opening n2 of pressure-compensated valve (5) communicates with working connection oil return inlet T, the spring of pressure-compensated valve (5) controls the compensated oil-out m3 controlling 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) of chamber n3, m4 communicates, the oil-in 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 oil-in p3 of the first repairing check valve (6a) and the second repairing check valve (6b) all communicates with working connection oil return inlet T, the oil-out p1 of the first repairing check valve (6a) and the second repairing check valve (6b), p2 respectively with the oil inlet and outlet A of rotary fluid motor (13), B communicates, the oil-in q3 of buffering reversal valve 7 connects with the oil return opening y2 of precursor overflow valve (10), the oil-in y1 of precursor overflow valve (10) and the oil-out k3 of the first rectification check valve (11a) and the second rectification check valve (11b) connects, the oil-in k1 of the first rectification check valve (11a) and the second rectification check 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 oil-in e1 of relief valve (1) communicates with working connection high pressure hydraulic fluid port P, the oil-out e2 of relief 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) and is formed is slidably matched, valve pocket (17) is arranged in the endoporus of valve body (18), and the upper installation of valve pocket (17) 8 groups adopts O RunddichtringO (19) to seal hydraulic fluid ports, the right-hand member of valve pocket (17) abuts against on valve body (18) inner face, the left end of valve pocket (17) short end lid (14) positions, outer spring (21) and inner spring (22) oppositely oriented, spring both sides are equipped with the first spring base (20a) and the second spring base (20b), the right-hand member of the first spring base (20a) valve rod (16) convex shoulder positions, the left end of the first spring base (20a) abuts against on valve body (18), the left end elastic spring (23) of the second spring base (20b) is fixed on valve rod (15), the right-hand member of the second spring base (20b) abuts against on long end cap (24), short end lid (14) and long end cap (24) are fixed by bolts on valve body, and inside is respectively mounted an O RunddichtringO (15a), 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 cap (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 drainage screen (8a) is installed, before the second trimmer valve guide damping (9b) damping, the second drainage screen (8b) is installed.
4. a kind of crane rotation system control valve according to claim 1, it is characterised in that: two actuator ports A1, B1 of described slewing directional control valve (2) load when middle position and working connection high pressure hydraulic fluid port P and working connection oil return inlet T are all not communicated with.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410838200.4A CN104533863B (en) | 2014-12-30 | 2014-12-30 | Crane rotation system control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410838200.4A CN104533863B (en) | 2014-12-30 | 2014-12-30 | Crane rotation system control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104533863A CN104533863A (en) | 2015-04-22 |
| CN104533863B true CN104533863B (en) | 2016-06-29 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410838200.4A Active CN104533863B (en) | 2014-12-30 | 2014-12-30 | Crane rotation system control valve |
Country Status (1)
| Country | Link |
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| CN (1) | CN104533863B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107355438A (en) * | 2017-07-25 | 2017-11-17 | 江苏柳工机械有限公司 | A kind of accessory control system |
| FR3075131B1 (en) * | 2017-12-15 | 2020-01-10 | Faiveley Transport Amiens | RAIL BRAKING SYSTEM FOR RAIL VEHICLE |
| CN109592585B (en) * | 2018-12-12 | 2020-04-28 | 三一汽车起重机械有限公司 | Crane rotation braking system and crane |
| 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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