CN202785413U - Anti-tilting hydraulic system for arm support of crane - Google Patents
Anti-tilting hydraulic system for arm support of crane Download PDFInfo
- Publication number
- CN202785413U CN202785413U CN201220423360.9U CN201220423360U CN202785413U CN 202785413 U CN202785413 U CN 202785413U CN 201220423360 U CN201220423360 U CN 201220423360U CN 202785413 U CN202785413 U CN 202785413U
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Abstract
The utility model discloses an anti-tilting hydraulic system for an arm support of a crane. When the output of a hydraulic pump is switched from high pressure to low pressure, an overflow valve (2), a no-leakage electromagnetic directional valve (3), a speed control valve (7) and a no-leakage electromagnetic directional valve (8) form a first transitional oil return circuit, and hydraulic oil flows to an oil sump tank through the first transitional oil return circuit; when a pressure sensor (1) measures that the oil pressure of a hydrocylinder (14) reaches the threshold at low pressure, the hydraulic oil flows to the oil sump tank through a first low-pressure loop. The anti-tilting hydraulic system for the arm support of the crane can relieve high pressure to a pressure close to the pressure of low-pressure and high-pressure oil circuits in a detectable and controllable manner by the aid of a pressure relief oil circuit when the arm support severely shakes due to switching of high pressure and low pressure, and then switches to the low-pressure and high-pressure oil circuits to prevent the arm support from shaking, thereby achieving the purposes of steadiness in operation, safety and reliability of the arm support, and energy conservation.
Description
Technical field
The utility model relates to the hydraulic technique field, relates in particular to the anti-hypsokinesis hydraulic efficiency pressure system of a kind of crane arm support.
Background technology
At present, in the process of hoisting heavy, safe reliability and good operation fine motion more and more become the hoisting crane user to be paid close attention to, more steady because good operation fine motion makes in the operation process, thereby safer.Development along with the epoch, people no longer only have been satisfied with this hoisting crane can hoisting heavy, but more and more pay attention to other such as the function of safety, the hommization aspect such as comfortable, convenient, the operation fine motion namely is that people are for control hoisting crane work speed and the steadily requirement of degree aspect.In the crawler crane normal operation process; jib steadily is most critical; but for the better protection to jib; the preventing backward tilting of arm support oil cylinder need provide high pressure or low pressure as required; but in the high-low pressure switching process; cause the jib shake, the technical program is to address the jib jitter problem from control oil cylinder high-low pressure switching process.
Summary of the invention
In view of this, a technical matters to be solved in the utility model provides the anti-hypsokinesis hydraulic efficiency pressure system of a kind of crane arm support, can avoid the jib shake when carrying out high and low voltage exchange.
A kind of crane arm support is prevented the hypsokinesis hydraulic efficiency pressure system, comprising: Hydraulic Pump 12, hydraulic ram 14, high-low pressure control setup and pressure relief device; Described high-low pressure control setup is arranged on described on hydraulic ram 14; Described high-low pressure control setup comprises: hydraulic control one-way valve 15, pressure sensor 1, by pass valve 2, nothing are leaked solenoid directional control valve 3, by pass valve 4; Described pressure relief device comprises: governor valve 7 and leakage-free solenoid valve 8; Pressure oil enters described hydraulic ram 14 through described hydraulic control one-way valve 15; Under the state of described Hydraulic Pump output high pressure, described by pass valve 2 and form the first high tension loop without leaking solenoid directional control valve 3, hydraulic oil falls after rise through described the first high pressure and flows back to fuel tank; Under the state of described Hydraulic Pump output low pressure, described by pass valve 4 forms the first low tension loop, and hydraulic oil flows back to fuel tank through described the first low tension loop; When the output of described Hydraulic Pump switches to low pressure by high pressure, described by pass valve 2, without leaking solenoid directional control valve 3, governor valve 7 and forming the First Transition oil return circuits without leaking solenoid directional control valve 8, hydraulic oil flows back to fuel tank through described First Transition oil return circuit; When the oil pressure of pressure sensor 1 measurement hydraulic ram 14 reached the threshold value that switches to low pressure, hydraulic oil flowed back to fuel tank through described the first low tension loop; When the output of described Hydraulic Pump switches to high pressure by low pressure, described by pass valve 4, governor valve 7 and form the second transition oil return circuit without leaking solenoid directional control valve 8, hydraulic oil flows back to fuel tank by described the second transition oil return circuit; When the oil pressure of pressure sensor 1 measurement hydraulic ram 14 reached the threshold value that switches to high pressure, hydraulic oil flowed back to fuel tank through described the first high tension loop.
According to an embodiment of system of the present utility model, further, in the hydraulic oil inflow point of described governor valve 7 filter 6 is set.
According to an embodiment of system of the present utility model, further, between described high-low pressure control setup and described pressure relief device, explosion relief valve 5 is set.
According to an embodiment of system of the present utility model, further, described Hydraulic Pump is Variable plunger pump.
An embodiment according to system of the present utility model, further, when the output of described Hydraulic Pump is switched to low pressure or low pressure and is switched to high pressure by high pressure, in the time threshold of setting, the oil pressure that described pressure sensor 1 detects described hydraulic ram 14 is not less than the pressure threshold of setting, and then described pressure sensor 1 sends alerting signal to described warning device
Crane arm support of the present utility model is prevented the hypsokinesis hydraulic efficiency pressure system, may cause in the serious process of jib shake in high and low pressure conversion, utilize the pressure release oil circuit, can detect, controllably high pressure be let out near pressure low, high-pressure oil passage, then switch to low, high-pressure oil passage, avoiding the jib shake.
Description of drawings
In order to be illustrated more clearly in the utility model embodiment or technical scheme of the prior art, the below will do one to the accompanying drawing of required use in embodiment or the description of the Prior Art and introduce simply, apparently, accompanying drawing in the following describes only is embodiment more of the present utility model, for those of ordinary skills, under the prerequisite of not paying creative work, can also obtain according to these accompanying drawings other accompanying drawing.
Fig. 1 is the scheme drawing according to an embodiment of the anti-hypsokinesis hydraulic efficiency pressure system of crane arm support of the present utility model.
The specific embodiment
With reference to the accompanying drawings the utility model is described more fully, exemplary embodiment of the present utility model wherein is described.Below in conjunction with the accompanying drawing among the utility model embodiment, the technical scheme among the utility model embodiment is clearly and completely described, obviously, described embodiment only is the utility model part embodiment, rather than whole embodiment.Based on the embodiment in the utility model, those of ordinary skills are not making the every other embodiment that obtains under the creative work prerequisite, all belong to the scope of the utility model protection.Below in conjunction with figure and embodiment the technical solution of the utility model is carried out many-sided description.
Fig. 1 is the scheme drawing according to an embodiment of the anti-hypsokinesis hydraulic efficiency pressure system of crane arm support of the present utility model.As shown in Figure 1, the anti-hypsokinesis hydraulic efficiency pressure system of crane arm support comprises: Hydraulic Pump 12, hydraulic ram 14, high-low pressure control setup and pressure relief device.The high-low pressure control setup is arranged on hydraulic ram 14.High-low pressure control setup 22 comprises: hydraulic control one-way valve 15, pressure sensor 1, by pass valve 2, nothing are leaked solenoid directional control valve 3, by pass valve 4; Pressure relief device 23 comprises: governor valve 7 and leakage-free solenoid valve 8.System also comprises control setup and warning device, and fuel tank (not drawing in Fig. 1).According to an embodiment, system can arrange 2 hydraulic rams 14 and high-low pressure control setup 21 and 22, for being arranged in parallel, also a hydraulic ram 14 and high-low pressure control setup can only be set.Hydraulic ram 14 can change hydraulic energy into the energy conversion device that mechanical energy is carried out straight reciprocating motion.The jib shake refers to a kind of sense stricto shake, refer in hoisting crane work process, thereby because the interference of some factor brings jib to lose original balance and shaking phenomenon.
Pressure oil enters hydraulic ram 14 through hydraulic control one-way valve 15.Under the state of Hydraulic Pump 12 output high pressure, by pass valve 2 and form the first high tension loop without leaking solenoid directional control valve 3, hydraulic oil falls after rise through the first high pressure and flows back to fuel tank; Under the state of Hydraulic Pump 12 output low pressure, by pass valve 4 forms the first low tension loop, and hydraulic oil flows back to fuel tank through the first low tension loop.
When the output of Hydraulic Pump 12 switches to low pressure by high pressure, by pass valve 2, without leaking solenoid directional control valve 3, governor valve 7 and forming the First Transition oil return circuits without leaking solenoid directional control valve 8, hydraulic oil flows back to fuel tank through the First Transition oil return circuit. and when the oil pressure of pressure sensor 1 measurement hydraulic ram 14 reached the threshold value that switches to low pressure, hydraulic oil flowed back to fuel tank through the first low tension loop; When the output of Hydraulic Pump switches to high pressure by low pressure, by pass valve 4, governor valve 7 and form the second transition oil return circuit without leaking solenoid directional control valve 8, hydraulic oil flows back to fuel tank by the second transition oil return circuit; When the oil pressure of pressure sensor 1 measurement hydraulic ram 14 reached the threshold value that switches to high pressure, hydraulic oil flowed back to fuel tank through the first high tension loop.
The smooth transition when Variable plunger pump that the utility model adopts high-low pressure control setup, relief arrangement and remote pressure control to cut off with pressure, control setup are controlled as required the high-low pressure of oil cylinder and guaranteed the high-low pressure switching.
According to an embodiment of the present utility model, in the hydraulic oil inflow point of governor valve 7 filter 6 is set.Explosion relief valve 5 is set between high-low pressure control setup and pressure relief device, for example is a kind of explosion-proof pipe valve.The Variable plunger pump 12 of Hydraulic Pump 12 for cutting off with pressure, system comprises remote-control pressure control valve 24, is comprised of by pass valve 9, by pass valve 10, solenoid directional control valve 11.The oil cylinder boosting refers to principal arm or rises when having surpassed jib that oil cylinder participates in promoting principal arm or surpassed the jib motion.During hoisting crane work, hand change over valve 13 is operated in left position, and oil cylinder withstands all the time principal arm or surpassed the jib boosting.When jib is in the state that the low pressure boosting stretches out, solenoid directional control valve 11 electric, solenoid directional control valve 3 electric, the electromagnet of remaining solenoid directional control valve is defaulted as dead electricity entirely.Through the left position of hand change over valve, hydraulic control one-way valve 15, oil cylinder 14, because factors vary such as jib kinematic velocitys, unnecessary force feed is by by pass valve 2, electromagnetic valve 3 oil sump tanks by pump for pressure oil.When jib is in the state that high-pressure boost stretches out, solenoid directional control valve 11 dead electricity, solenoid directional control valve 3 dead electricity, the electromagnet of remaining solenoid directional control valve is defaulted as dead electricity entirely.Through the left position of hand change over valve, hydraulic control one-way valve 15, oil cylinder 14, because factors vary such as jib kinematic velocitys, unnecessary force feed is by by pass valve 4 oil sump tanks by pump for pressure oil.
Under the state that is in the static or passive compression of low pressure, solenoid directional control valve 11 electric, solenoid directional control valve 3 electric, the electromagnet of remaining solenoid directional control valve is defaulted as dead electricity entirely, at this moment pump is in the low pressure dissengaged positions, discharge capacity only is used for leaking, with energy-conservation.Under the state that is in passive compression, the large chamber of oil cylinder fluid is by the left position oil sump tank of by pass valve 2, solenoid directional control valve 3.Under the state that is in high voltage static or passive compression, solenoid directional control valve 11 dead electricity, solenoid directional control valve 3 dead electricity, the electromagnet of remaining solenoid directional control valve is defaulted as dead electricity entirely.At this moment pump is in the high pressure cut-off state, and discharge capacity only is used for leaking, with energy-conservation.During passive compression, the large chamber of oil cylinder fluid is by by pass valve 4 oil sump tanks.
According to an embodiment of the present utility model, the oil cylinder high pressure conditions has greater impact when switching to low-pressure state, causes the jib shake.The pressure release loop is set, and when satisfying high pressure and switch to low pressure condition (jib angle, load ratio), the pressure release oil circuit is made of blowdown valve, explosion relief valve and pipeline; The hydraulic ram high pressure conditions is set up by by pass valve 4.
Hydraulic ram by the process that high-pressure oil passage switches to low pressure oil way is: get electric without leaking solenoid directional control valve 8, pressure is by by pass valve 2 in the hydraulic ram, explosion relief valve 5, filter 6, without leaking solenoid directional control valve 8 to the oil return line pressure release, when pressure is let out certain value (than the setting P2 of by pass valve 2 more greatly, P2+0.5MPa for example) time, pressure is detected by pressure sensor 1, only detect pressure reach setting value above (or being lower than) just allow solenoid directional control valve 3 TURP is changed to low tension loop, reply power failure states without leaking solenoid directional control valve 8 after switching to low tension loop.Switch to the condition that low pressure is switched if satisfy high pressure, detect oil cylinder working-pressure behind certain hour, be not less than a certain setting value, then alarm (possible cause: electromagnetic valve 3 is stuck, or does not give electricity).The pressure release speed determines that high-low pressure switches steady degree, by the set flow decision of governor valve 7.After governor valve is once set up, fixing, do not need to transfer again.
When the oil cylinder low-pressure state switches to high pressure conditions, when the oil cylinder low-pressure state switches to high pressure conditions, if motion is too fast because jib rises and falls, also can produce impact and cause the jib shake, can be by following control process: when satisfying low pressure and switch to condition of high voltage (jib angle, load ratio), nothing leakage solenoid directional control valve 8 gets electric, and the millisecond value of delay adjustments is such as 500 milliseconds of grades (purpose is to allow nothing leakage solenoid directional control valve 8 prior to solenoid directional control valve 3 dead electricity); Solenoid directional control valve 3 dead electricity; (the millisecond value of delay adjustments such as 500 milliseconds etc., decide according to actual effect) without leakage solenoid directional control valve 8 dead electricity, turns high tension loop.
When the output of Hydraulic Pump was switched to low pressure or low pressure and switched to high pressure by high pressure, in the time threshold of setting, the oil pressure that pressure sensor 1 detects hydraulic ram 14 was not less than the pressure threshold of setting, and then pressure sensor 1 sends alerting signal to warning device.
The pressure cut off threshold value of the utility model design pump slightly is lower than the high-voltage value that the high-low pressure control setup is set up, the low voltage value of pump remote pressure control slightly is lower than the low voltage value that the high-low pressure control setup is set up, and pump guarantees all that at oil cylinder height state minimum injection rate only keeps leakage with energy-conservation like this.
Crane arm support of the present utility model is prevented the hypsokinesis hydraulic efficiency pressure system, by eliminating the jitter phenomenon of preventing backward tilting of arm support oil cylinder in the high-low pressure handoff procedure, reaches smooth operation, arm support safe and reliably reaches energy-conservation purpose.
Description of the present utility model provides for example with for the purpose of describing, and is not exhaustively or with the utility model to be limited to disclosed form.Many modifications and variations are obvious for the ordinary skill in the art.Selecting and describing embodiment is for better explanation principle of the present utility model and practical application, thereby and makes those of ordinary skill in the art can understand the various embodiment with various modifications that the utility model design is suitable for special-purpose.
Claims (5)
1. the anti-hypsokinesis hydraulic efficiency pressure system of crane arm support is characterized in that, comprising:
Hydraulic Pump (12), hydraulic ram (14), high-low pressure control setup and pressure relief device; Described high-low pressure control setup is arranged on the described hydraulic ram (14);
Described high-low pressure control setup comprises: hydraulic control one-way valve (15), pressure sensor (1), by pass valve (2), nothing are leaked solenoid directional control valve (3), by pass valve (4); Described pressure relief device comprises: governor valve (7) and leakage-free solenoid valve (8);
Pressure oil enters described hydraulic ram (14) through described hydraulic control one-way valve (15); Under the state of described Hydraulic Pump (12) output high pressure, described by pass valve (2) and form the first high tension loop without leaking solenoid directional control valve (3), hydraulic oil falls after rise through described the first high pressure and flows back to fuel tank; Under the state of described Hydraulic Pump (12) output low pressure, described by pass valve (4) forms the first low tension loop, and hydraulic oil flows back to fuel tank through described the first low tension loop;
When the output of described Hydraulic Pump (12) switches to low pressure by high pressure, described by pass valve (2), without leaking solenoid directional control valve (3), governor valve (7) and forming the First Transition oil return circuit without leaking solenoid directional control valve (8); Hydraulic oil flows back to fuel tank through described First Transition oil return circuit; When the oil pressure of measuring described hydraulic ram (14) when described pressure sensor (1) reaches the threshold value that switches to low pressure, switch to described the first low tension loop, hydraulic oil flows back to fuel tank through described the first low tension loop;
When the output of described Hydraulic Pump (12) switches to high pressure by low pressure, described by pass valve (4), governor valve (7) and form the second transition oil return circuit without leaking solenoid directional control valve (8), hydraulic oil flows back to fuel tank by described the second transition oil return circuit; When the oil pressure of measuring described hydraulic ram (14) when described pressure sensor (1) reaches the threshold value that switches to high pressure, switch to described the first high tension loop, hydraulic oil flows back to fuel tank through described the first high tension loop.
2. the system as claimed in claim 1 is characterized in that:
Hydraulic oil inflow point at described governor valve (7) arranges filter (6).
3. the system as claimed in claim 1 is characterized in that:
Explosion relief valve (5) is set between described high-low pressure control setup and described pressure relief device.
4. the system as claimed in claim 1 is characterized in that:
Described Hydraulic Pump (12) is Variable plunger pump.
5. the system shown in claim 1 is characterized in that, also comprises warning device;
When the output of described Hydraulic Pump (12) is switched to low pressure or low pressure and is switched to high pressure by high pressure, in the time threshold of setting, if described pressure sensor (1) detects the pressure threshold that the oil pressure of described hydraulic ram (14) is not less than setting, then described pressure sensor (1) sends alerting signal to described warning device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220423360.9U CN202785413U (en) | 2012-08-24 | 2012-08-24 | Anti-tilting hydraulic system for arm support of crane |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220423360.9U CN202785413U (en) | 2012-08-24 | 2012-08-24 | Anti-tilting hydraulic system for arm support of crane |
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| Publication Number | Publication Date |
|---|---|
| CN202785413U true CN202785413U (en) | 2013-03-13 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201220423360.9U Expired - Lifetime CN202785413U (en) | 2012-08-24 | 2012-08-24 | Anti-tilting hydraulic system for arm support of crane |
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| CN (1) | CN202785413U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103350964A (en) * | 2013-07-23 | 2013-10-16 | 中联重科股份有限公司 | Backwards-tilting prevention hydraulic control system of arm support and tower crane |
| CN103469785A (en) * | 2013-09-26 | 2013-12-25 | 徐工集团工程机械股份有限公司 | Anti-backward inclination control device of dynamic compactor |
| CN104481955A (en) * | 2014-12-17 | 2015-04-01 | 上海市机械施工集团有限公司 | Hydraulic device for automatically controlling supporting shaft force of foundation pit engineering |
| CN107655761A (en) * | 2017-10-30 | 2018-02-02 | 上海应用技术大学 | Rupture disk pressure release test system and method |
| CN108046137A (en) * | 2017-12-13 | 2018-05-18 | 三汽车起重机械有限公司 | High pressure protector, oil gas cylinder component, crane and high voltage protective method |
| CN110173483A (en) * | 2019-06-28 | 2019-08-27 | 北京三一智造科技有限公司 | Hydraulic system and rotary drilling rig |
-
2012
- 2012-08-24 CN CN201220423360.9U patent/CN202785413U/en not_active Expired - Lifetime
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103350964A (en) * | 2013-07-23 | 2013-10-16 | 中联重科股份有限公司 | Backwards-tilting prevention hydraulic control system of arm support and tower crane |
| CN103469785A (en) * | 2013-09-26 | 2013-12-25 | 徐工集团工程机械股份有限公司 | Anti-backward inclination control device of dynamic compactor |
| CN103469785B (en) * | 2013-09-26 | 2015-12-16 | 徐工集团工程机械股份有限公司 | Anti-backward inclination control device of dynamic compactor |
| CN104481955A (en) * | 2014-12-17 | 2015-04-01 | 上海市机械施工集团有限公司 | Hydraulic device for automatically controlling supporting shaft force of foundation pit engineering |
| CN107655761A (en) * | 2017-10-30 | 2018-02-02 | 上海应用技术大学 | Rupture disk pressure release test system and method |
| CN108046137A (en) * | 2017-12-13 | 2018-05-18 | 三汽车起重机械有限公司 | High pressure protector, oil gas cylinder component, crane and high voltage protective method |
| CN110173483A (en) * | 2019-06-28 | 2019-08-27 | 北京三一智造科技有限公司 | Hydraulic system and rotary drilling rig |
| CN110173483B (en) * | 2019-06-28 | 2024-01-23 | 北京三一智造科技有限公司 | Hydraulic system and rotary drilling rig |
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| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term |
Granted publication date: 20130313 |
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| CX01 | Expiry of patent term |