CN202369305U - Crane and hoisting variable amplitude hydraulic system thereof - Google Patents
Crane and hoisting variable amplitude hydraulic system thereof Download PDFInfo
- Publication number
- CN202369305U CN202369305U CN2011205449377U CN201120544937U CN202369305U CN 202369305 U CN202369305 U CN 202369305U CN 2011205449377 U CN2011205449377 U CN 2011205449377U CN 201120544937 U CN201120544937 U CN 201120544937U CN 202369305 U CN202369305 U CN 202369305U
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- back pressure
- hydraulic efficiency
- elevator
- hydraulic system
- hoisting
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Abstract
The utility model discloses a hoisting variable amplitude hydraulic system, which comprises a self-weight descending boom hydraulic system, a hoisting hydraulic system and an oil return passage for connecting the self-weight descending boom hydraulic system and the hoisting hydraulic system; the self-weight descending boom hydraulic system is provided with a variable amplitude oil cylinder; two ends of the oil return passage are respectively communicated with an oil tank through a first backpressure valve and a second backpressure valve; a backpressure section is formed between the first backpressure valve and the second backpressure valve; a normal pressure section is formed between the first backpressure valve and the oil tank, and a normal pressure section is formed between the second backpressure valve and the oil tank; and the rod cavity of the variable amplitude oil cylinder of the self-weight descending boom hydraulic system is connected with a normal pressure section pipeline of the oil return passage and an oil tank pipeline. According to the hoisting variable amplitude hydraulic system, the rod cavity of the variable amplitude oil cylinder directly sucks oil from a position outside the backpressure section of the oil return passage of the hydraulic system or from the oil tank, so that any influence on the backpressure section of the oil return passage of the whole hoisting variable amplitude hydraulic system and a hoisting system is not produced when a boom descends, and hoisting hook slippage is not produced no matter whether the parameters of hoisting and variable amplitude are coordinated or not.
Description
Technical field
The utility model relates to and having arm that deadweight transfers arm fall the elevator luffing hydraulic efficiency pressure system of arm hydraulic efficiency pressure system and the hoisting crane with this elevator luffing hydraulic efficiency pressure system.
Background technology
Hoisting crane is in elevator luffing hydraulic efficiency pressure system, and the arm arm hydraulic efficiency pressure system that falls has two kinds of forms.A kind of is the power arm that falls, and another kind is the gravity arm that falls.
The power arm that falls, promptly depended on pressure oil realizes having the arm of falling rapid speed, the advantage of high efficiency, but have shortcomings such as luffing shake, luffing bounce-back, fine motion property difference.
In the luffing hydraulic efficiency pressure system of hoisting crane, the arm form that falls that the arm hydraulic efficiency pressure system that falls of arm often adopts deadweight to transfer.The deadweight arm system that falls of transferring has low energy consumption, advantage such as keep steady down.So deadweight place system down often is used in the changing-breadth system of hoisting crane.The oil return line oil suction of amplitude oil cylinder rod chamber from whole hydraulic efficiency pressure system all adopted in deadweight down let-down arm system at present, because of the oil return line oil suction of luffing rod chamber from system, has only very little back pressure, so energy-conservation and steady when transferring.
But; If in the fluid suction amplitude oil cylinder rod chamber of amplitude oil cylinder rod chamber with the oil return line of system, this moment, oil return line replenished fluid to the let-down arm system timely when falling arm under the deadweight, the oil return line of hoisting system will become negative pressure so; When the pressure on system oil return road becomes negative pressure; If do winch action this moment, can directly cause elevator slide hook, cause very serious safety misadventure.
As previously mentioned, might to make the oil return line back pressure be negative pressure to the let-down arm system under the deadweight of prior art, thereby directly cause slipping hook, causes great safety misadventure.But deadweight is transferred and is had energy-conservation and the pulsation-free advantage; So arm system that falls that present main frame producer still often adopts deadweight to transfer; But in the setting of parameter, just need especially to note, sets bad or adjusted the hidden danger that some parameters probably cause elevator slide hook.
Fig. 1 is the principle schematic of the car hosit elevator luffing hydraulic efficiency pressure system of prior art.As shown in Figure 1, luffing/elevator hydraulic efficiency pressure system comprises the elevator valve block (perhaps being called the elevator control cock) 40 ' of amplitude oil cylinder 10 ', the luffing valve block (perhaps being called the luffing control cock) 20 ' of controlling amplitude oil cylinder 10 ', hoist motor 30 ', control hoist motor 30 '.
Arm rod chamber 11 ' of amplitude oil cylinder 10 ' when flumping arm is that B ' from oil return line 50 ' sucks fluid in the amplitude oil cylinder 10 ' rod chamber 11 ' in the changing-breadth system.The two ends of this oil return line 50 ' are communicated with fuel tank 60 ' through back pressure valve T1 (for example back pressure is 0.3MPa) and back pressure valve T2 (for example back pressure is 0.7MPa) respectively; B ' locates to be positioned at the back pressure valve T1 of oil return line 50 ' and the part between the back pressure valve T2, and the return opening of luffing valve block and elevator valve block is the part between back pressure valve T1 and back pressure valve T2 also.
It is following that the B ' of oil return line 50 ' locates to produce the analysis of causes of negative pressure: oil return line is not coordinated, caused to the correlation parameter of car hosit changing-breadth system and hoisting system is negative pressure.For example, hoisting system existing problems sometimes after the problem adjustment elevator parameter that solves hoisting system, are done the luffing arm that falls and are just probably caused oil return line to produce negative pressure; Sometimes be changing-breadth system existing problems, adjust the luffing parameter this moment after, also can make the elevator place produce negative pressure when doing luffing.
Therefore, above-mentioned elevator luffing hydraulic efficiency pressure system has the hidden danger of elevator slide hook when changing the parameter of elevator or luffing.
The utility model content
The purpose of the utility model is to provide a kind of elevator luffing hydraulic efficiency pressure system of hoisting crane, to solve the problem that exists in the prior art, overcomes the hidden danger of elevator slide hook.A kind of hoisting crane with this elevator luffing hydraulic efficiency pressure system also is provided simultaneously.
For this reason; The utility model provides a kind of elevator luffing hydraulic efficiency pressure system on the one hand, comprises from the oil return line that flumps arm hydraulic efficiency pressure system, elevator hydraulic efficiency pressure system and connect the two, flumps the arm hydraulic efficiency pressure system certainly and has amplitude oil cylinder; The two ends of oil return line have first back pressure valve and second back pressure valve respectively; And be communicated with fuel tank through first back pressure valve and second back pressure valve respectively, form the back pressure section between first back pressure valve and second back pressure valve, be the normal pressure section between first back pressure valve and the fuel tank and between second back pressure valve and the fuel tank; Wherein, the rod chamber that flumps the amplitude oil cylinder of arm hydraulic efficiency pressure system certainly is connected with the normal pressure section pipeline of oil return line or is connected with the fuel tank pipeline.
It is further, above-mentioned that flumping the arm hydraulic efficiency pressure system also comprises the luffing control cock of controlling amplitude oil cylinder certainly.
Further, the back pressure set value of above-mentioned second back pressure valve is greater than the back pressure set value of first back pressure valve, and the rod chamber of amplitude oil cylinder is connected with the normal pressure section pipeline of first back pressure valve, one side.
Further, the back pressure set value of above-mentioned first back pressure valve is 0.3MPa, and the back pressure set value of second back pressure valve is 0.7MPa.
Further, above-mentioned elevator hydraulic efficiency pressure system comprises the elevator control cock of hoist motor and control hoist motor.
According to the utility model on the other hand, a kind of hoisting crane is provided, has comprised elevator luffing hydraulic efficiency pressure system, this elevator luffing hydraulic efficiency pressure system is the elevator luffing hydraulic efficiency pressure system according to top description structure.
According to the utility model; The rod chamber of amplitude oil cylinder through pipeline beyond the back pressure section of the oil return line of hydraulic efficiency pressure system or from the direct oil suction of fuel tank;, arm can not produce any influence when falling arm to the back pressure section and the hoisting system of the oil return line of whole elevator luffing hydraulic efficiency pressure system; No matter whether the parameter of elevator and luffing is coordinated, and can not produce elevator and slip hook.Wherein, the parameter of elevator can be according to the adjustment of elevator demand, and the parameter of luffing also can the adjustment of luffing demand.
Except top described purpose, characteristic and advantage, other purpose, characteristic and the advantage that the utlity model has are with combining accompanying drawing to do further detailed explanation.
Description of drawings
Constitute the preferred embodiment that the part of this specification sheets, the accompanying drawing that is used for further understanding the utility model show the utility model, and be used for explaining the principle of the utility model with specification sheets.Among the figure:
Fig. 1 is the principle schematic of the car hosit elevator luffing hydraulic efficiency pressure system of prior art;
Fig. 2 is the principle schematic according to the car hosit elevator luffing hydraulic efficiency pressure system of the utility model.
Description of reference numerals
1 arm is from flumping arm hydraulic efficiency pressure system 2 elevator hydraulic efficiency pressure systems
10 amplitude oil cylinder, 20 luffing control cock
30 hoist motors, 40 elevator control cock
50 oil return line T1, first back pressure valve
T2 second back pressure valve 60 fuel tanks
51 back pressure sections, 52 normal pressure sections
11 rod chambers, 12 pipelines.
The specific embodiment
Embodiment to the utility model is elaborated below in conjunction with accompanying drawing, but the multitude of different ways that the utility model can be defined by the claims and cover is implemented.
Fig. 2 is the principle schematic according to the car hosit elevator luffing hydraulic efficiency pressure system of the utility model.As shown in Figure 2, elevator luffing hydraulic efficiency pressure system comprises from flumping arm hydraulic efficiency pressure system 1 and elevator hydraulic efficiency pressure system 2.Particularly, flump certainly arm hydraulic efficiency pressure system 1 comprise amplitude oil cylinder 10, control amplitude oil cylinder 10 luffing control cock (being also referred to as the luffing valve block usually) 20, elevator hydraulic efficiency pressure system 2 comprise hoist motor 30 and control hoist motor 30 elevator control cock (being also referred to as the elevator valve block usually) 40.
The two ends of oil return line 50 are communicated with fuel tank 60 through first back pressure valve T1 (for example back pressure is 0.3MPa) and the second back pressure valve T2 (for example back pressure is 0.7MPa) respectively; First back pressure valve T1 of oil return line 50 and the part between the second back pressure valve T2 form back pressure section 51, and the return opening of luffing valve block 20 and elevator valve block 40 all is connected with back pressure section 51.
But in the utility model, the rod chamber 11 of amplitude oil cylinder 10 links to each other perhaps directly from fuel tank 60 oil suctions with the back pressure section 51 normal pressure section 52 in addition of oil return line 50 through pipeline 12.Except that above-described pipeline annexation; All the other pipeline annexations between amplitude oil cylinder 10 and the luffing control cock 20 and the pipeline annexation between hoist motor 30 and the elevator control cock 40 are well known to those skilled in the art, and do not give unnecessary details at this.
Preferably, the back pressure set value of the above-mentioned second back pressure valve T2 is greater than the back pressure set value of the first back pressure valve T1, and the rod chamber of amplitude oil cylinder is connected with the normal pressure section pipeline of the first back pressure valve T1, one side.More preferably, the back pressure set value of the above-mentioned first back pressure valve T1 is 0.3MPa, and the back pressure set value of the second back pressure valve T2 is 0.7MPa.
According to the utility model; The rod chamber 11 of amplitude oil cylinder 10 through pipeline on the first back pressure valve T1 of the oil return line of hydraulic efficiency pressure system and the pipeline between the fuel tank 60 perhaps from fuel tank 60 direct oil suctions; When arm falls arm, can not produce any influence, therefore just can not cause oil return line and elevator oil circuit to become negative pressure and then produce the problem of hook of slipping from flumping arm because of arm to back pressure section, the C place of hoisting system, the D place of the oil return line of whole elevator luffing hydraulic efficiency pressure system.The concrete structure of the utility model and luffing valve block 20 and elevator valve block 40 is irrelevant, is not limited to the concrete structure shown in Fig. 2.
More than be merely the preferred embodiment of the utility model, be not limited to the utility model, for a person skilled in the art, the utility model can have various changes and variation.All within the spirit and principle of the utility model, any modification of being done, be equal to replacement, improvement etc., all should be included within the protection domain of the utility model.
Claims (6)
1. elevator luffing hydraulic efficiency pressure system; Comprise from the oil return line (50) that flumps arm hydraulic efficiency pressure system (1), elevator hydraulic efficiency pressure system (2) and connect the two; Said have amplitude oil cylinder (10) from flumping arm hydraulic efficiency pressure system (1); The two ends of said oil return line (50) have first back pressure valve (T1) and second back pressure valve (T2) respectively; And be communicated with fuel tank (60) through said first back pressure valve (T1) and second back pressure valve (T2) respectively; Form back pressure section (51) between said first back pressure valve (T1) and second back pressure valve (T2); Between said first back pressure valve (T1) and the said fuel tank (60) and be normal pressure section (52) between second back pressure valve (T2) and the said fuel tank (60), it is characterized in that said the connection with normal pressure section (52) pipeline of said oil return line (50) perhaps from the rod chamber (11) that flumps the amplitude oil cylinder (10) of arm hydraulic efficiency pressure system (1) is connected with said fuel tank (60) pipeline.
2. elevator luffing hydraulic efficiency pressure system according to claim 1 is characterized in that, and is said from flumping the luffing control cock (20) that the arm hydraulic efficiency pressure system also comprises the said amplitude oil cylinder of control (10).
3. elevator luffing hydraulic efficiency pressure system according to claim 1; It is characterized in that; The back pressure set value of said second back pressure valve (T2) is greater than the back pressure set value of said first back pressure valve (T1), and the rod chamber (11) of said amplitude oil cylinder (10) is connected with normal pressure section (52) pipeline of said first back pressure valve (T1) side.
4. elevator luffing hydraulic efficiency pressure system according to claim 1 is characterized in that the back pressure set value of said first back pressure valve (T1) is 0.3MPa, and the back pressure set value of said second back pressure valve (T2) is 0.7MPa.
5. elevator luffing hydraulic efficiency pressure system according to claim 1 is characterized in that, said elevator hydraulic efficiency pressure system comprises the elevator control cock (40) of hoist motor (30) and the said hoist motor of control (30).
6. a hoisting crane comprises elevator luffing hydraulic efficiency pressure system, it is characterized in that, said elevator luffing hydraulic efficiency pressure system is according to each described elevator luffing hydraulic efficiency pressure system in the claim 1 to 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011205449377U CN202369305U (en) | 2011-12-22 | 2011-12-22 | Crane and hoisting variable amplitude hydraulic system thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011205449377U CN202369305U (en) | 2011-12-22 | 2011-12-22 | Crane and hoisting variable amplitude hydraulic system thereof |
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| Publication Number | Publication Date |
|---|---|
| CN202369305U true CN202369305U (en) | 2012-08-08 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2011205449377U Expired - Fee Related CN202369305U (en) | 2011-12-22 | 2011-12-22 | Crane and hoisting variable amplitude hydraulic system thereof |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102874697A (en) * | 2012-10-18 | 2013-01-16 | 中联重科股份有限公司 | Hydraulic system for controlling amplitude variation of arm support and crane |
| CN102887447A (en) * | 2012-10-17 | 2013-01-23 | 中联重科股份有限公司 | Hydraulic control loop for amplitude-variable hydraulic cylinder, crane and amplitude-variable control method |
| CN103287999A (en) * | 2013-06-18 | 2013-09-11 | 中联重科股份有限公司 | Engineering machinery, winch amplitude variation hydraulic system of engineering machinery and working method of amplitude variation hydraulic system |
| CN103879891A (en) * | 2012-12-24 | 2014-06-25 | 三一重工股份有限公司 | Hydraulic system, lifting equipment and lifting equipment state transition method |
| CN102887435B (en) * | 2012-10-19 | 2014-11-05 | 中联重科股份有限公司 | Hydraulic system for controlling amplitude variation of crane boom, control method and crane |
| CN104528555A (en) * | 2014-12-19 | 2015-04-22 | 中联重科股份有限公司 | Main arm variable amplitude controlling system for crane and crane |
| CN104609321A (en) * | 2015-02-16 | 2015-05-13 | 徐州重型机械有限公司 | Crane boom luffing hydraulic control system, luffing device and crane |
-
2011
- 2011-12-22 CN CN2011205449377U patent/CN202369305U/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102887447A (en) * | 2012-10-17 | 2013-01-23 | 中联重科股份有限公司 | Hydraulic control loop for amplitude-variable hydraulic cylinder, crane and amplitude-variable control method |
| CN102887447B (en) * | 2012-10-17 | 2014-09-17 | 中联重科股份有限公司 | Hydraulic control loop for amplitude-variable hydraulic cylinder, crane and amplitude-variable control method |
| CN102874697A (en) * | 2012-10-18 | 2013-01-16 | 中联重科股份有限公司 | Hydraulic system for controlling amplitude variation of arm support and crane |
| CN102874697B (en) * | 2012-10-18 | 2015-07-01 | 中联重科股份有限公司 | Hydraulic system for controlling amplitude variation of arm support and crane |
| CN102887435B (en) * | 2012-10-19 | 2014-11-05 | 中联重科股份有限公司 | Hydraulic system for controlling amplitude variation of crane boom, control method and crane |
| CN103879891A (en) * | 2012-12-24 | 2014-06-25 | 三一重工股份有限公司 | Hydraulic system, lifting equipment and lifting equipment state transition method |
| CN103879891B (en) * | 2012-12-24 | 2016-02-10 | 三一重工股份有限公司 | The state transition method of a kind of hydraulic system, crane gear and crane gear |
| CN103287999A (en) * | 2013-06-18 | 2013-09-11 | 中联重科股份有限公司 | Engineering machinery, winch amplitude variation hydraulic system of engineering machinery and working method of amplitude variation hydraulic system |
| CN103287999B (en) * | 2013-06-18 | 2015-08-05 | 中联重科股份有限公司 | Construction machinery and equipment and elevator variable amplitude hydraulic system, operational method |
| CN104528555A (en) * | 2014-12-19 | 2015-04-22 | 中联重科股份有限公司 | Main arm variable amplitude controlling system for crane and crane |
| CN104528555B (en) * | 2014-12-19 | 2017-03-22 | 中联重科股份有限公司 | Main arm variable amplitude controlling system for crane and crane |
| CN104609321A (en) * | 2015-02-16 | 2015-05-13 | 徐州重型机械有限公司 | Crane boom luffing hydraulic control system, luffing device and crane |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20120808 Termination date: 20151222 |
|
| EXPY | Termination of patent right or utility model |