CN203582302U - Control valve group, hydraulic control system and automobile crane - Google Patents
Control valve group, hydraulic control system and automobile crane Download PDFInfo
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- CN203582302U CN203582302U CN201320772919.3U CN201320772919U CN203582302U CN 203582302 U CN203582302 U CN 203582302U CN 201320772919 U CN201320772919 U CN 201320772919U CN 203582302 U CN203582302 U CN 203582302U
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- 239000003921 oil Substances 0.000 claims abstract description 196
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 21
- 239000012530 fluid Substances 0.000 claims description 20
- 239000002243 precursor Substances 0.000 claims description 14
- 238000005213 imbibition Methods 0.000 claims description 8
- 230000009471 action Effects 0.000 claims description 3
- 238000005086 pumping Methods 0.000 abstract description 5
- 230000007246 mechanism Effects 0.000 abstract description 3
- 238000004378 air conditioning Methods 0.000 description 9
- 239000000446 fuel Substances 0.000 description 8
- 238000010586 diagram Methods 0.000 description 4
- 230000006837 decompression Effects 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000011897 real-time detection Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
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Abstract
The utility model discloses a valve unit, hydraulic control system and mobile crane, this system includes hydraulic tank , hydraulic pump, actuating mechanism, pilot control system and valve unit (3), and the valve unit has oil inlet (P), first oil-out (A) and second oil-out (Y), is connected with first internal oil circuit (N1) between oil inlet and the first oil-out, and the oil inlet communicates the oil-out of hydraulic pump, and the actuating mechanism is connected to first oil-out; a second internal oil path (N2) is connected between the oil inlet and the second oil outlet, and the second oil outlet is connected to a pilot control system through a system pilot control oil path (V3); the control valve group comprises a switch valve (31) arranged in the first internal oil path and a reducing valve (32) installed in the second internal oil path and used for reducing the pressure of the hydraulic oil in the oil inlet and then flowing to the pilot control system. In which a hydraulic pump dedicated to pumping pilot control oil is eliminated, optimizing the overall system structure and performance.
Description
Technical field
The utility model relates to a kind of hydraulic efficiency pressure system, particularly a kind of small and medium-sized car hoisting crane and hydraulic control system thereof.
Background technology
In current medium and small tonnage car hosit, conventional a plurality of gear type pump series connection (being commonly called as multi-joint string pump) are as the propulsion source of hydraulic efficiency pressure system, state internal gear pump manufacturing firm can be by four gear type pump series connection, if by four above gear type pump series connection, manufacturing cost sharply rises, the cost performance of gear type pump reduces greatly, thereby current car hosit is used at most tetrad string pump as the propulsion source of hydraulic efficiency pressure system.
Car hosit generally has the compositions such as main actuating mechanism (elevator, luffing, flexible, revolution, air-conditioning) and auxiliary actuating unit (pilot control system).The control oil sources of its pilot control system is generally by an independent gear type pump fuel feeding, elevator, luffing, the actuating unit such as flexible are parallel system and by two common fuel feeding of gear type pump, after rotary power unit and air-conditioning actuating unit are connected in series by a gear type pump fuel feeding.Wherein, because actuating unit is more, and the number of gear type pump is limited, thereby has to a plurality of actuating units to be connected.The for example revolution of series connection, air-conditioning actuating unit are all high pressure oils when work, and this just causes two actuating units to influence each other when work, unstable properties.As first actuating unit 100 of connecting in Fig. 1 and the second actuating unit 200, unified by the first Hydraulic Pump 1 pump imbibition force feed be pumped to two actuating units by work change-over valve 4 selectivity from hydraulic reservoir T, and separately by the second Hydraulic Pump 2 to pilot control system pumping pilot control fluid.Wherein, utilize the first pressometer 6 and the second pressometer 7 to measure in real time respectively the hydraulic fluid pressure of the first Hydraulic Pump 1 and the second Hydraulic Pump 2 pumpings.Because each actuating unit of connecting influences each other in use, restriction mutually, the actuating unit of series connection causes the operation pressure of its fuel feeding oil pump (being the first Hydraulic Pump 1 in Fig. 1) too high simultaneously, has affected the in-use performance of car hosit.
Utility model content
The purpose of this utility model is to provide a kind of control cock group, the hydraulic control system with this control cock group and car hosit, in this hydraulic control system, remove the Hydraulic Pump that is specifically designed to pumping pilot control fluid, thereby optimized integral structure and the serviceability of hydraulic control system.
For achieving the above object, according to an aspect of the present utility model, a kind of control cock group is provided, this control cock group has oil inlet, the first oil outlet and the second oil outlet, between described oil inlet and the first oil outlet, be connected with the first internal oil passages and and described the second oil outlet between be connected with the second internal oil passages; Described control cock group comprises switch valve and reducing valve, described switch valve is arranged in described the first internal oil passages the break-make with the first internal oil passages described in switching controls, described reducing valve is arranged in described the second internal oil passages, operating fluid force feed that described oil inlet enters can be depressurized and as pilot control oil, from described the second oil outlet, flow out afterwards.
Preferably, this control cock group also comprises check valve, and this check valve is arranged in described the second internal oil passages, so that hydraulic oil can flow to described the second oil outlet and oppositely cut-off from described oil inlet.
Preferably, this control cock group also has return opening and inner oil return circuit, and one end of this inside oil return circuit connects described return opening, and other end hydraulic connecting is on the described reducing valve and the oil circuit part between check valve of described the second internal oil passages; Described control cock group also comprises precursor overflow valve, and this precursor overflow valve is arranged in described inner oil return circuit, and the oil pressure relief setting value of described precursor overflow valve is greater than the setting outlet oil pressure of the exit end of described reducing valve.
Preferably, this control cock group also comprises safety overflow valve is set, and this safety overflow valve is arranged on being connected on oil circuit between described return opening and described the first internal oil passages.
Preferably, described switch valve is 2/2-way internal control type pilot operated directional control valve, solenoid directional control valve or sequence valve.
According to another aspect of the present utility model, a kind of hydraulic control system is also provided, the pilot control system that comprises hydraulic reservoir, Hydraulic Pump, actuating unit and this actuating unit, described Hydraulic Pump can be from described hydraulic reservoir pump imbibition force feed be pumped to described actuating unit by main working oil path, it is characterized in that, described hydraulic control system also comprises the control cock group above-mentioned according to the utility model, and this control cock group is arranged in described main working oil path;
Wherein, described oil inlet is communicated with the oil outlet of described Hydraulic Pump, and described the first oil outlet connects described actuating unit; Described the second oil outlet is connected to described pilot control system by system pilot control oil circuit.
Preferably, when described switch valve is internal control type pilot operated directional control valve, guide's fluid control pressure when this switch valve carries out switching over is identical with the setting operation pressure of described pilot control system.
Preferably, this system also comprises the work change-over valve for the direction of action of actuating unit described in switching controls, the oil inlet of this work change-over valve is connected with described first oil outlet of described control cock group, and the actuator port of described work change-over valve connects described actuating unit.
Preferably, this system also comprises accumulator, and this accumulator hydraulic connecting is in described system pilot control oil circuit.
Preferably, described actuating unit at least comprises the first actuating unit and the second actuating unit, corresponding the first main working oil path and the second main working oil path of comprising of described main working oil path, corresponding the first Hydraulic Pump and the second Hydraulic Pump of comprising of described Hydraulic Pump, this first Hydraulic Pump and the second Hydraulic Pump can be respectively pump imbibition force feed deliver to described the first actuating unit and the second actuating unit by described the first main working oil path and the second main working oil path respective pump respectively from described hydraulic reservoir independently, and described control cock group is arranged in described the first main working oil path or the second main working oil path.
According to an also aspect of the present utility model, a kind of car hosit is provided, this car hosit comprises the hydraulic control system above-mentioned according to the utility model.
According to technique scheme, in hydraulic control system of the present utility model, before work change-over valve, set up control cock group, make it possible to extension hydraulic oil from main working oil path and flow to pilot control system, thereby needn't provide independent Hydraulic Pump with to the special pumps hydraulic oil of pilot control system.In the situation that require only to have the Hydraulic Pump of limited number in whole hydraulic control system, can make the actuating unit of script series system in hydraulic control system can change into parallel way, make to avoid influencing each other and unstable properties between each actuating unit of series system, optimized integral structure and the serviceability of hydraulic control system.
Other feature and advantage of the present utility model partly in detail are described the specific embodiment subsequently.
Accompanying drawing explanation
Accompanying drawing is to be used to provide further understanding of the present utility model, and forms a part for specification sheets, is used from explanation the utility model, but does not form restriction of the present utility model with the specific embodiment one below.In the accompanying drawings:
Fig. 1 is the hydraulic schematic diagram of part of the hydraulic control system of small and medium-sized car hoisting crane of the prior art;
Fig. 2 is according to the hydraulic schematic diagram of the part of the hydraulic control system of preferred implementation of the present utility model;
Fig. 3 is according to the structure principle chart of the control cock group of a kind of preferred implementation of the present utility model, and switch valve wherein adopts pilot operated directional control valve;
Fig. 4 is according to the hydraulic structure schematic diagram of the control cock group of another kind of preferred implementation of the present utility model, and switch valve wherein adopts solenoid directional control valve; And
Fig. 5 is according to the hydraulic structure schematic diagram of the control cock group of also a kind of preferred implementation of the present utility model, and switch valve wherein adopts sequence valve.
description of reference numerals
The specific embodiment
Below in conjunction with accompanying drawing, the specific embodiment of the present utility model is elaborated.Should be understood that, the specific embodiment described herein only, for description and interpretation the utility model, is not limited to the utility model.
As shown in Figures 2 and 3, the hydraulic control system that the utility model provides a kind of control cock group and adopted this control cock group, this system comprises the pilot control system of hydraulic reservoir T, Hydraulic Pump, actuating unit and this actuating unit, Hydraulic Pump can be from hydraulic reservoir T pump imbibition force feed be pumped to actuating unit by main working oil path.Wherein, hydraulic control system also comprises the control cock group 3 being arranged in main working oil path.Shown in Fig. 3, this control cock group 3 has oil inlet P, the first oil outlet A and the second oil outlet Y, between oil inlet P and the first oil outlet A, is connected with the first internal oil passages N1, and this oil inlet P is communicated with the oil outlet of Hydraulic Pump, and the first oil outlet A connects actuating unit; Between oil inlet P and the second oil outlet Y, be connected with the second internal oil passages N2, this second oil outlet Y is connected to pilot control system by system pilot control oil circuit V3.Control cock group 3 in Fig. 3 comprises switch valve 31 and reducing valve 32, switch valve 31 is arranged in the first internal oil passages N1 the break-make with switching controls the first internal oil passages N1, reducing valve 32 is arranged in the second internal oil passages N2, flowing to pilot control system after the hydraulic oil decompression in oil inlet P.In the utility model, be intended to that control cock group 3 by setting up is drawn hydraulic oil from main working oil path and by flowing into system pilot control oil circuit V3 after reducing valve 32 decompressions, thereby make pilot control system needn't use separately a special Hydraulic Pump.Can save the Hydraulic Pump of Limited Number like this, thereby for the detachable one-tenth parallel form of actuating unit of connecting, by the independent pumps hydraulic oil of the Hydraulic Pump saving.
Wherein, control module 3 can provide for the pilot control system in hydraulic control system stable control oil sources, and pilot control system when work, can not impact the work of actuating unit.Will be in Fig. 1 originally for changing into other actuating unit fuel feeding to the gear type pump of pilot control system fuel feeding, thereby eliminate the problem of influencing each other of causing after actuating unit series connection, unstable properties, below will specifically address.Reducing valve 32 is wherein for reducing pressure and then offer pilot control system operating fluid force feed, switch valve 31 blocks main working oil path during for the setting operation pressure of the hydraulic oil out of reach pilot control system in main working oil path, has opened the problem of actuating unit to avoid pilot control system not start.
As shown in Figure 3, control cock group 3 also preferably includes check valve 33, and this check valve 33 is arranged in the second internal oil passages N2, so that hydraulic oil can flow to the second oil outlet Y and oppositely cut-off from oil inlet P.This check valve 33 is back to control cock group 3 for preventing the pilot control hydraulic oil of pilot control system.In addition, control cock group 3 also preferably has return opening L and inner oil return circuit N3, and one end of this inside oil return circuit N3 connects return opening L, and other end hydraulic connecting is on the reducing valve 32 and the oil circuit part between check valve 33 of the second internal oil passages N2; Wherein, control cock group 3 also comprises precursor overflow valve 34, and this precursor overflow valve 34 is arranged in inner oil return circuit N3, and the oil pressure relief setting value of precursor overflow valve 34 is greater than the setting outlet oil pressure of the exit end of reducing valve 32.Precursor overflow valve 34 wherein, for limiting the maximum oil hydraulic coupling of the second internal oil passages N2, prevents that the hydraulic oil in main working oil path directly flowed to pilot control system when reducing valve 32 loses efficacy, and is back in hydraulic reservoir T.In addition, control cock group 3 also comprises safety overflow valve 35 is set, and this safety overflow valve 35 is arranged on being connected on oil circuit between return opening L and the first internal oil passages N1.This safety overflow valve 35 is for limiting the maximum working pressure and the maximum working pressure that is pumped to oil inlet P in main working oil path.
In addition, switch valve 31 is preferably the internal control type pilot operated directional control valve of the 2/2-way shown in Fig. 3.According to the hydraulic fluid pressure in the first internal oil passages N1 and conducting or end this first internal oil passages N1.Preferably, guide's fluid control pressure when switch valve 31 carries out switching over is identical with the setting operation pressure of pilot control system, and namely the spring force setting value in switch valve 31 and the setting operation pressure of pilot control system match.When the hydraulic fluid pressure in the first internal oil passages N1 is less than the setting operation pressure of pilot control system, this pilot operated directional control valve is in the next, the first internal oil passages N1 cut-off, the first Hydraulic Pump 1 is separately toward pilot control system pumps hydraulic oil, the first oil outlet A exports without fluid, the first actuating unit 100 attonitys, the reducing valve 32 that the hydraulic oil in the first internal oil passages N1 is all opened via valve port flows to the second oil outlet Y.When the pressure of oil inlet P reaches or exceeds the setting operation pressure of pilot control system, pilot operated directional control valve is in upper, the first internal oil passages N1 conducting, and then from the first oil outlet A output fluid, drive the first actuating unit 100 work.
Wherein, the pressure oil of the first Hydraulic Pump 1 output in Fig. 2 is delivered to the oil inlet P of control cock group 3 through the first main working oil path V1.As shown in Figure 3, because the hydraulic fluid flow rate in the first main working oil path V1 is fast, oil pressure is large, at precursor overflow valve 34, do not open and switch valve 31 during in the next off condition, fast by the pressure time of building of the pilot control system of the first main working oil path V1 fuel feeding by control cock group 3, system can respond fast.After pilot control system response, the main working oil path of switch valve 31 conducting, thus start the first actuating unit 100.
As shown in Figure 4, the switch valve 31 in the control cock group 3 of its demonstration can also be solenoid directional control valve, so that logic control or automatically control.Or as shown in Figure 5, the switch valve 31 of control cock group 3 wherein can also be logical switch valve or the valve group of other forms such as sequence valve.Also it should be noted that, in the car hosit of medium and small tonnage, the setting operation pressure of the pilot control system of its hydraulic control system is generally not more than 5MPa, so the setting outlet oil pressure of the exit end of reducing valve 32 also control to require to determine according to system, and this setting value is not more than 5MPa equally.
In addition, in hydraulic control system, generally also comprise the work change-over valve 4 for the direction of action of switching controls actuating unit, this work change-over valve 4 is three-position four-way valve, the work oil inlet of change-over valve 4 and the first oil outlet A of control cock group 3 are connected, and the actuator port of work change-over valve 4 connects actuating unit.And this hydraulic control system also comprises for detection of the first pressometer 6 of the hydraulic fluid pressure in main working oil path with for detection of the second pressometer 7 of the hydraulic fluid pressure in system pilot control oil circuit V3.By real-time detection, can be used for adjusting in real time each valve member and prevent the system failure.In addition as shown in Figure 2, the hydraulic control system in present embodiment also preferably includes accumulator 5, and these accumulator 5 hydraulic connectings are in system pilot control oil circuit V3.This accumulator 5 leaks for charging system, and the fluid traffic demand of formerly leading control system as emergent oil sources carries out fuel feeding compensation when larger, makes pilot control pressure oil-source more stable.
More than set forth and in main working oil path, set up control cock group 3, so that the hydraulic oil in main working oil path is flowed to actuating unit and pilot control system simultaneously, thereby needn't Hydraulic Pump be set separately for pilot control system.Wherein, described actuating unit in this hydraulic control system can be more than one, Fig. 2 for example, can at least comprise the first actuating unit 100 and the second actuating unit 200, corresponding the first main working oil path V1 and the second main working oil path V2 of comprising of main working oil path, corresponding the first Hydraulic Pump 1 and the second Hydraulic Pump 2 of comprising of Hydraulic Pump, this first Hydraulic Pump 1 and the second Hydraulic Pump 2 can be respectively pump imbibition force feed deliver to the first actuating unit 100 and the second actuating unit 200 by the first main working oil path V1 and the second main working oil path V2 respective pump respectively from hydraulic reservoir T independently, and control cock group 3 is arranged in the first main working oil path V1 or the second main working oil path V2.In other words, at least comprising the hydraulic control system of two actuating units, this two actuating units tandem working no longer as shown in Figure 1, but parallel way setting, work independently and be independent of each other.Thereby the first actuating unit 100 and the second actuating unit 200 interactional problem when tandem working have been solved, and the first actuating unit 100 of parallel way and the second actuating unit 200 provide hydraulic oil by the first Hydraulic Pump 1 and the second Hydraulic Pump 2 respectively, compared to two actuating units that are tandem working by single Hydraulic Pump in Fig. 1, provide hydraulic oil, greatly alleviate the load of Hydraulic Pump, improved its work life.
On the basis of the hydraulic control system of said structure, the working process of this system is below described.
As shown in Figure 2, the first Hydraulic Pump 1(gear type pump) from hydraulic reservoir T, oil suction enters system, and mechanical energy is converted to hydraulic energy, has the oil sources of certain flow and pressure by the first main working oil path V1 output, enter the oil inlet P of control cock group 3, drive the first actuating unit 100 motions.The second Hydraulic Pump 2(gear type pump) be independent of the oil suction from hydraulic reservoir T of the first Hydraulic Pump 1 and enter system, mechanical energy is converted to hydraulic energy, the oil sources by the second main working oil path V2 output with certain flow and pressure, to drive the second actuating unit 200 motions.The first actuating unit 100 and the second actuating unit 200 belong to the mode of being connected in parallel, and the first actuating unit 100 and the second actuating unit 200 can be distinguished independently moving, also can together move, and according to the mode of its corresponding work change-over valve 4, determine.When work change-over valve 4 is separately during all in meta, the first actuating unit 100 and the second actuating unit 200 are not worked; When work change-over valve 4 is separately all simultaneously in upper or simultaneously when the next, the two works and forward work simultaneously or reverse operation simultaneously simultaneously.When system overloads, the safety overflow valve in the first main working oil path V1 35 is opened, and plays safety guard-safeguard effect, and fluid enters hydraulic reservoir T through safety overflow valve 35 by oil return circuit.Hydraulic oil in the second main working oil path V1 is equally through by pass valve oil return wherein.
When hydraulic control system is worked, by the first pressometer 6 and the second pressometer 7, can detect respectively the hydraulic fluid pressure in the first main working oil path V1 and system pilot control oil circuit V3, thus the operation pressure of reflection and monitoring the first Hydraulic Pump 1.Wherein, precursor overflow valve 34 is according to system requirements setting pressure; control enters the hydraulic oil pressure in system pilot control oil circuit V3; as the detected value of the second pressometer 7 occurs abnormal; precursor overflow valve 34 is opened; play safety guard-safeguard effect, the overflowing liquid force feed of precursor overflow valve 34 by inner oil return circuit N3 and return opening L oil return to hydraulic reservoir T.
On the basis of the above, the utility model also provides a kind of car hosit, the car hosit of especially medium and small tonnage, and this car hosit comprises the hydraulic control system above-mentioned according to the utility model.Wherein, the car hosit of medium and small tonnage generally includes rotary power unit and air-conditioning actuating unit.As shown in Figure 2, when hydraulic control system also comprises the second Hydraulic Pump 2 and the second actuating unit 200, and the second Hydraulic Pump 2 can be independent of the first Hydraulic Pump 1 pump imbibition force feed while being pumped in the second actuating unit 200 by the second main working oil path V2 from hydraulic reservoir T, this first actuating unit 100 can be the wherein one in rotary power unit and air-conditioning actuating unit, and the second actuating unit 200 can be the another one in rotary power unit and air-conditioning actuating unit.Because rotary power unit and air-conditioning actuating unit are high pressure oil when the work, in the hydraulic control system in Fig. 1, when the two is worked, influence each other, cause serviceability unstable, operation pressure for the rotary power unit of series connection and the Hydraulic Pump of air-conditioning actuating unit pumps hydraulic oil is the operation pressure sum of two actuating units simultaneously, and system energy consumption is high.And in hydraulic control system of the present utility model, rotary power unit and air-conditioning actuating unit work alone, by the first Hydraulic Pump 1 and the second Hydraulic Pump 2, independently provide hydraulic oil respectively, remove the Hydraulic Pump that is specifically designed to pumping pilot control fluid, thereby optimized integral structure and the serviceability of hydraulic control system.
Below describe by reference to the accompanying drawings preferred implementation of the present utility model in detail; but; the utility model is not limited to the detail in above-mentioned embodiment; within the scope of technical conceive of the present utility model; can carry out multiple simple variant to the technical solution of the utility model, these simple variant all belong to protection domain of the present utility model.
It should be noted that in addition, each concrete technical characterictic described in the above-mentioned specific embodiment, in reconcilable situation, can combine by any suitable mode, for fear of unnecessary repetition, the utility model is to the explanation no longer separately of various possible array modes.
In addition, between various embodiment of the present utility model, also can carry out combination in any, as long as it is without prejudice to thought of the present utility model, it should be considered as content disclosed in the utility model equally.
Claims (11)
1. a control cock group, it is characterized in that, this control cock group (3) has oil inlet (P), the first oil outlet (A) and the second oil outlet (Y), between described oil inlet (P) and the first oil outlet (A), be connected with the first internal oil passages (N1) and and described the second oil outlet (Y) between be connected with the second internal oil passages (N2); Described control cock group (3) comprises switch valve (31) and reducing valve (32), described switch valve (31) is arranged in described the first internal oil passages (N1) break-make with the first internal oil passages (N1) described in switching controls, described reducing valve (32) is arranged in described the second internal oil passages (N2), and the operating fluid force feed that described oil inlet (P) is entered can be depressurized and as pilot control oil, from described the second oil outlet (Y), flow out afterwards.
2. control cock group according to claim 1, it is characterized in that, this control cock group (3) also comprises check valve (33), this check valve (33) is arranged in described the second internal oil passages (N2), so that hydraulic oil can flow to described the second oil outlet (Y) and oppositely cut-off from described oil inlet (P).
3. control cock group according to claim 2, it is characterized in that, this control cock group (3) also has return opening (L) and inner oil return circuit (N3), one end of this inside oil return circuit (N3) connects described return opening (L), and other end hydraulic connecting is on the described reducing valve (32) and the oil circuit part between check valve (33) of described the second internal oil passages (N2); Described control cock group (3) also comprises precursor overflow valve (34), this precursor overflow valve (34) is arranged in described inner oil return circuit (N3), and the oil pressure relief setting value of described precursor overflow valve (34) is greater than the setting outlet oil pressure of the exit end of described reducing valve (32).
4. control cock group according to claim 3, it is characterized in that, this control cock group (3) also comprises safety overflow valve (35) is set, and this safety overflow valve (35) is arranged on being connected on oil circuit between described return opening (L) and described the first internal oil passages (N1).
5. control cock group according to claim 1, is characterized in that, internal control type pilot operated directional control valve, solenoid directional control valve or sequence valve that described switch valve (31) is 2/2-way.
6. a hydraulic control system, the pilot control system that comprises hydraulic reservoir (T), Hydraulic Pump, actuating unit and this actuating unit, described Hydraulic Pump can be from described hydraulic reservoir (T) pump imbibition force feed be pumped to described actuating unit by main working oil path, it is characterized in that, described hydraulic control system also comprises that, according to the control cock group (3) described in any one in claim 1-5, this control cock group (3) is arranged in described main working oil path;
Wherein, described oil inlet (P) is communicated with the oil outlet of described Hydraulic Pump, and described the first oil outlet (A) connects described actuating unit; Described the second oil outlet (Y) is connected to described pilot control system by system pilot control oil circuit (V3).
7. hydraulic control system according to claim 6, it is characterized in that, when described switch valve (31) is internal control type pilot operated directional control valve, guide's fluid control pressure when this switch valve (31) carries out switching over is identical with the setting operation pressure of described pilot control system.
8. hydraulic control system according to claim 6, it is characterized in that, this system also comprises the work change-over valve (4) for the direction of action of actuating unit described in switching controls, the oil inlet of this work change-over valve (4) is connected with described first oil outlet (A) of described control cock group (3), and the actuator port of described work change-over valve (4) connects described actuating unit.
9. hydraulic control system according to claim 6, is characterized in that, this system also comprises accumulator (5), and this accumulator (5) hydraulic connecting is in described system pilot control oil circuit (V3).
10. hydraulic control system according to claim 6, it is characterized in that, described actuating unit at least comprises the first actuating unit (100) and the second actuating unit (200), corresponding the first main working oil path (V1) and the second main working oil path (V2) of comprising of described main working oil path, corresponding the first Hydraulic Pump (1) and the second Hydraulic Pump (2) of comprising of described Hydraulic Pump, this first Hydraulic Pump (1) and the second Hydraulic Pump (2) can be distinguished independently from described hydraulic reservoir (T) pump imbibition force feed and by described the first main working oil path (V1) and the second main working oil path (V2) respective pump, deliver to described the first actuating unit (100) and the second actuating unit (200) respectively, and described control cock group (3) is arranged in described the first main working oil path (V1) or the second main working oil path (V2).
11. 1 kinds of car hosits, is characterized in that, this car hosit comprises according to the hydraulic control system described in any one in claim 1-10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320772919.3U CN203582302U (en) | 2013-11-28 | 2013-11-28 | Control valve group, hydraulic control system and automobile crane |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201320772919.3U CN203582302U (en) | 2013-11-28 | 2013-11-28 | Control valve group, hydraulic control system and automobile crane |
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| CN203582302U true CN203582302U (en) | 2014-05-07 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104265706A (en) * | 2014-09-19 | 2015-01-07 | 潍柴动力（青州）传控技术有限公司 | Relieving device of pilot control hydraulic system |
| CN111059087A (en) * | 2019-12-23 | 2020-04-24 | 中联重科股份有限公司 | Power distribution hydraulic system and crane |
| CN112498047A (en) * | 2019-09-16 | 2021-03-16 | 河北雷萨重型工程机械有限责任公司 | Crane air conditioner control system and crane |
| CN113819095A (en) * | 2021-08-16 | 2021-12-21 | 中联重科土方机械有限公司 | Hydraulic system, control method of hydraulic system, and engineering machine |
| CN114412869A (en) * | 2022-01-27 | 2022-04-29 | 湖南三一中型起重机械有限公司 | Operating valve block, emergency hydraulic control system and operating machine |
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2013
- 2013-11-28 CN CN201320772919.3U patent/CN203582302U/en not_active Expired - Lifetime
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104265706A (en) * | 2014-09-19 | 2015-01-07 | 潍柴动力（青州）传控技术有限公司 | Relieving device of pilot control hydraulic system |
| CN112498047A (en) * | 2019-09-16 | 2021-03-16 | 河北雷萨重型工程机械有限责任公司 | Crane air conditioner control system and crane |
| CN111059087A (en) * | 2019-12-23 | 2020-04-24 | 中联重科股份有限公司 | Power distribution hydraulic system and crane |
| CN111059087B (en) * | 2019-12-23 | 2021-07-30 | 中联重科股份有限公司 | Power distribution hydraulic system and crane |
| CN113819095A (en) * | 2021-08-16 | 2021-12-21 | 中联重科土方机械有限公司 | Hydraulic system, control method of hydraulic system, and engineering machine |
| CN113819095B (en) * | 2021-08-16 | 2023-12-08 | 中联重科土方机械有限公司 | Hydraulic system, control method of hydraulic system and engineering machinery |
| CN114412869A (en) * | 2022-01-27 | 2022-04-29 | 湖南三一中型起重机械有限公司 | Operating valve block, emergency hydraulic control system and operating machine |
| CN114412869B (en) * | 2022-01-27 | 2023-06-02 | 湖南三一中型起重机械有限公司 | Operating valve block, emergency hydraulic control system and working machine |
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