CN102951557B - Hydraulic system used for elevating mechanism - Google Patents
Hydraulic system used for elevating mechanism Download PDFInfo
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- CN102951557B CN102951557B CN201110240479.2A CN201110240479A CN102951557B CN 102951557 B CN102951557 B CN 102951557B CN 201110240479 A CN201110240479 A CN 201110240479A CN 102951557 B CN102951557 B CN 102951557B
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Abstract
The invention discloses a hydraulic system used for an elevating mechanism. The hydraulic system comprises an oil tank (1), a hydraulic pump (3), an elevating valve (5) and a hydraulic cylinder (6), the elevating valve has an elevating place and a falling place, the elevating valve enables oil in the oil tank to flow into the work chamber (13) of the hydraulic cylinder through the hydraulic pump when the elevating valve is in the elevating place, and the elevating valve enables the oil in the work chamber of the hydraulic cylinder to return to the oil tank when the elevating valve is in the falling place, wherein a safe valve (7) is connected between the elevating valve and the work chamber of the hydraulic cylinder, a backpressure valve (8) is connected between the oil tank and the safe valve, the safe valve prevents the flow-out of the oil in the work chamber or enables the oil in the work chamber to slowly flow out when the oil pressure at the inlet of the safe valve is zero, and the safe valve enables an oil way between the elevating valve and the work chamber to be smooth when the oil pressure at the inlet of the safe valve is not zero. The above technical scheme can avoid the damages of the hydraulic system, so the equipment damages and casualties are avoided, thereby the safe running of the elevating mechanism is guaranteed.
Description
Technical field
The present invention relates to a kind of hydraulic efficiency pressure system for lifting mechanism.
Background technology
As shown in Figure 1, hydraulic efficiency pressure system at present for the lifting mechanism of dumping truck generally includes fuel tank 1, oil filter 2, Hydraulic Pump 3, lift valve 5 and hydraulic actuating cylinder 6, in addition, by pass valve 4 is also connected with between the outlet of described Hydraulic Pump 3 and described fuel tank 1, described lift valve 5 has lifting position and decline position, in described lifting position, described lift valve 5 makes the fluid in described fuel tank 1 flow in the rodless cavity of described hydraulic actuating cylinder 6 by Hydraulic Pump 3, in described decline position, described lift valve 5 makes the fluid in the rodless cavity of described hydraulic actuating cylinder 6 flow back in described fuel tank 1.As shown in Figure 1, when lift valve 5 is in lifting position, the oil pump in fuel tank 1 enters in lift valve 5 by Hydraulic Pump 3, and fluid is flowed in the rodless cavity of hydraulic actuating cylinder 6 by lift valve 5, thus realizes the lifting of the piston rod of hydraulic actuating cylinder 6; When lift valve 5 is in decline position, the fluid in the rodless cavity of hydraulic actuating cylinder 6 flows back in fuel tank 1, thus realizes the decline of the piston rod of hydraulic actuating cylinder 6.Oil pipe between the rodless cavity and fuel tank 1 of hydraulic actuating cylinder 6 is unexpected when bursting due to the reason such as aging, fluid in the rodless cavity of hydraulic actuating cylinder 6 can flow out rapidly, piston rod in hydraulic actuating cylinder 6 can fall after rise rapidly owing to losing support, thus cause hydraulic efficiency pressure system to be damaged, even may cause overturning and personal casualty, thus bring very large loss to life and property.
Summary of the invention
The object of this invention is to provide a kind of hydraulic efficiency pressure system for lifting mechanism with higher safety performance.
To achieve these goals, the invention provides a kind of hydraulic efficiency pressure system for lifting mechanism, this hydraulic efficiency pressure system comprises fuel tank, Hydraulic Pump, lift valve and hydraulic actuating cylinder, described lift valve has lifting position and decline position, in described lifting position, described lift valve makes the fluid in described fuel tank flow in the epitrochoidal chamber of described hydraulic actuating cylinder by described Hydraulic Pump, in described decline position, described lift valve makes the fluid in the epitrochoidal chamber of described hydraulic actuating cylinder flow back in described fuel tank, wherein, also safety valve is connected with between the epitrochoidal chamber of described lift valve and described hydraulic actuating cylinder, back pressure valve is connected with between described fuel tank and described safety valve, when the oil pressure of the entrance of described safety valve is 0, described safety valve stops the fluid in described epitrochoidal chamber flow out or the fluid in described epitrochoidal chamber is slowly flowed out, when the oil pressure of the entrance of described safety valve is not 0, described safety valve is by the oil circuit conducting between described lift valve and described epitrochoidal chamber.
Preferably, described safety valve is arranged near described hydraulic actuating cylinder.
Preferably, described safety valve comprises bi-bit bi-pass spring hydraulicchange-over valve, when the inlet pressure sum of spring pressure and described bi-bit bi-pass spring hydraulicchange-over valve is greater than the delivery pressure of described bi-bit bi-pass spring hydraulicchange-over valve, described bi-bit bi-pass spring hydraulicchange-over valve is by the oil circuit conducting between described lift valve and described epitrochoidal chamber, and when the inlet pressure sum of spring pressure and described bi-bit bi-pass spring hydraulicchange-over valve is less than the delivery pressure of described bi-bit bi-pass spring hydraulicchange-over valve, described safety valve stops the fluid in described epitrochoidal chamber flow out or the fluid in described epitrochoidal chamber is slowly flowed out.
Preferably, be integrated with check valve in described bi-bit bi-pass spring hydraulicchange-over valve, when the oil pressure of the entrance of described bi-bit bi-pass spring hydraulicchange-over valve is 0, described check valve stops the fluid in the epitrochoidal chamber of described hydraulic actuating cylinder to flow out.
Preferably, be integrated with first throttle valve in described bi-bit bi-pass spring hydraulicchange-over valve, when the oil pressure of the entrance of described bi-bit bi-pass spring hydraulicchange-over valve is 0, described first throttle valve makes the fluid in the epitrochoidal chamber of described hydraulic actuating cylinder slowly flow out.
Preferably, described safety valve also comprises second throttle, and this second throttle is connected between described bi-bit bi-pass spring change-over valve and the epitrochoidal chamber of described hydraulic actuating cylinder.
Preferably, described back pressure valve is flow regulating valve.
Preferably, described back pressure valve is arranged between the return opening of described fuel tank and described lift valve.
Preferably, described lift valve has middle stop bit, stop bit in this, described fuel tank and described hydraulic actuating cylinder not connected.
Preferably, by pass valve is connected with between described hydraulic pressure delivery side of pump and described fuel tank.
The working process of the above-mentioned hydraulic efficiency pressure system for lifting mechanism is as follows: when explosion does not occur the oil pipe between fuel tank and safety valve, that is when the oil pressure of the entrance of described safety valve is not 0, safety valve by the oil circuit conducting between described lift valve and described epitrochoidal chamber, thus ensure that the normal operation of hydraulic efficiency pressure system; Oil pipe between fuel tank and safety valve is unexpected when bursting due to the reason such as aging, the oil pressure of the entrance of safety valve is 0, thus stop the fluid in epitrochoidal chamber flow out or the fluid in epitrochoidal chamber is slowly flowed out by safety valve, thus the working portion of hydraulic actuating cylinder can be made to keep motionless or slowly fall after rise, hydraulic efficiency pressure system is avoided to damage, and then avoid device damage and personal casualty, ensure that the safe operation of lifting mechanism.
Other features and advantages of the present invention are described in detail in detailed description of the invention part subsequently.
Accompanying drawing explanation
Accompanying drawing is used to provide a further understanding of the present invention, and forms a part for specification sheets, is used from explanation the present invention, but is not construed as limiting the invention with detailed description of the invention one below.In the accompanying drawings:
Fig. 1 is the structural representation of the hydraulic efficiency pressure system of the existing lifting mechanism for dumping truck;
Fig. 2 is the structural representation of a kind of embodiment of the hydraulic efficiency pressure system for lifting mechanism provided by the invention;
Fig. 3 is the structural representation of the another kind of embodiment of the hydraulic efficiency pressure system for lifting mechanism provided by the invention;
Fig. 4 is the structural representation of the first embodiment of the safety valve of the hydraulic efficiency pressure system for lifting mechanism provided by the invention;
Fig. 5 is the structural representation of the second embodiment of the safety valve of the hydraulic efficiency pressure system for lifting mechanism provided by the invention;
Fig. 6 is the structural representation of the third embodiment of the safety valve of the hydraulic efficiency pressure system for lifting mechanism provided by the invention;
Fig. 7 is the structural representation of the 4th kind of embodiment of the safety valve of the hydraulic efficiency pressure system for lifting mechanism provided by the invention.
Description of reference numerals
1: fuel tank; 2: oil filter; 3: Hydraulic Pump; 4: by pass valve; 5: lift valve; 6: hydraulic actuating cylinder; 7: safety valve; 8: back pressure valve; 9: second throttle; 10: first throttle valve; 11: check valve; 12: bi-bit bi-pass spring hydraulicchange-over valve; 13: epitrochoidal chamber; 14: working portion.
Detailed description of the invention
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.Should be understood that, detailed description of the invention described herein, only for instruction and explanation of the present invention, is not limited to the present invention.
Before the present invention is described in detail, it is to be noted, the term " entrance of safety valve " used in the present invention refers in particular to the hydraulic fluid port be connected with lift valve of safety valve, " entrance of bi-bit bi-pass spring hydraulicchange-over valve " refers in particular to the hydraulic fluid port be connected with lift valve of bi-bit bi-pass spring hydraulicchange-over valve, and " outlet of bi-bit bi-pass spring hydraulicchange-over valve " refers in particular to the hydraulic fluid port be connected with hydraulic actuating cylinder of bi-bit bi-pass spring hydraulicchange-over valve.
Below for dumping truck, the hydraulic efficiency pressure system for lifting mechanism is described.
As shown in Figures 2 and 3, the hydraulic efficiency pressure system for lifting mechanism that the specific embodiment of the invention provides comprises fuel tank 1, Hydraulic Pump 3, lift valve 5 and hydraulic actuating cylinder 6, described lift valve 5 has lifting position and decline position, in described lifting position, described lift valve 5 makes the fluid in described fuel tank 1 flow in the epitrochoidal chamber 13 of described hydraulic actuating cylinder 6 by described Hydraulic Pump 3, in described decline position, described lift valve 5 makes the fluid in the epitrochoidal chamber 13 of described hydraulic actuating cylinder 6 flow back in described fuel tank 1, wherein, safety valve 7 is also connected with between described lift valve 5 and the epitrochoidal chamber 13 of described hydraulic actuating cylinder 6, back pressure valve 8 is connected with between described fuel tank 1 and described safety valve 7, when the oil pressure of the entrance of described safety valve 7 is 0, described safety valve 7 stops the fluid in described epitrochoidal chamber 13 flow out or the fluid in described epitrochoidal chamber 13 is slowly flowed out, when the oil pressure of the entrance of described safety valve 7 is not 0, described safety valve 7 is by the oil circuit conducting between described lift valve 5 and described epitrochoidal chamber 13.
The working process of the above-mentioned hydraulic efficiency pressure system for lifting mechanism is as follows: when the oil pipe between fuel tank 1 and safety valve 7 does not occur to burst, that is when the oil pressure of the entrance of described safety valve 7 is not 0, safety valve 7 by the oil circuit conducting between described lift valve 5 and described epitrochoidal chamber 13, thus ensure that the normal operation of hydraulic efficiency pressure system; Oil pipe between fuel tank 1 and safety valve 7 is unexpected when bursting due to the reason such as aging, the oil pressure of the entrance of safety valve 7 is 0, thus stop the fluid in epitrochoidal chamber 13 flow out or the fluid in epitrochoidal chamber 13 is slowly flowed out by safety valve 7, thus the working portion 14 of hydraulic actuating cylinder 6 can be made to keep motionless or slowly fall after rise, hydraulic efficiency pressure system is avoided to damage, and then avoid device damage and personal casualty, ensure that the safe operation of lifting mechanism.
Preferably, described safety valve 7 is arranged near described hydraulic actuating cylinder 6, thus better protects hydraulic efficiency pressure system.Preferably, the oil pipe between safety valve 7 and hydraulic actuating cylinder 6 adopts the oil pipe of comparatively robust, such as steel pipe, thus makes the oil pipe between safety valve 7 and hydraulic actuating cylinder 6 be not easy to damage.
Safety valve 7 can adopt various suitable form, a preferred embodiment of the invention, described safety valve 7 comprises bi-bit bi-pass spring hydraulicchange-over valve 12, when the inlet pressure sum of spring pressure and bi-bit bi-pass spring hydraulicchange-over valve 12 is greater than the delivery pressure of bi-bit bi-pass spring hydraulicchange-over valve 12, bi-bit bi-pass spring hydraulicchange-over valve 12 is by the oil circuit conducting between described lift valve 5 and described epitrochoidal chamber 13, and when the inlet pressure sum of spring pressure and bi-bit bi-pass spring hydraulicchange-over valve 12 is less than the delivery pressure of bi-bit bi-pass spring hydraulicchange-over valve 12, described safety valve 7 stops the fluid in described epitrochoidal chamber 13 flow out or the fluid in described epitrochoidal chamber 13 is slowly flowed out, thus can protect hydraulic efficiency pressure system easily, ensure the safe operation of lifting mechanism.Particularly, can set the pressure of the pressure of spring and back pressure valve 8, make when lift valve 5 is in lifting position, the oil pressure of the entrance of bi-bit bi-pass spring hydraulicchange-over valve 12 and the pressure sum of spring are greater than the delivery pressure of bi-bit bi-pass spring hydraulicchange-over valve 12, thus make bi-bit bi-pass spring hydraulicchange-over valve 12 by the oil circuit conducting between described lift valve 5 and described epitrochoidal chamber 13; And when lift valve 5 is in decline position, the back pressure of back pressure valve 8 and the pressure sum of spring are greater than the delivery pressure of bi-bit bi-pass spring hydraulicchange-over valve 12, thus make bi-bit bi-pass spring hydraulicchange-over valve 12 by the oil circuit conducting between described lift valve 5 and described epitrochoidal chamber 13; No matter lift valve 5 is in lifting position and still declines position, when oil pipe between fuel tank 1 and bi-bit bi-pass spring hydraulicchange-over valve 12 occurs to burst, the pressure of the entrance of bi-bit bi-pass spring hydraulicchange-over valve 12 is 0, and the pressure in bi-bit bi-pass spring hydraulicchange-over valve 12 exit is larger, the pressure of spring is made to be less than the delivery pressure of bi-bit bi-pass spring hydraulicchange-over valve 12, thus bi-bit bi-pass spring hydraulicchange-over valve 12 is replaced, stop the fluid in described epitrochoidal chamber 13 flow out or the fluid in described epitrochoidal chamber 13 is slowly flowed out.
The fluid in described epitrochoidal chamber 13 can be stoped to flow out or the fluid in described epitrochoidal chamber 13 is slowly flowed out by various suitable mode.
As shown in Figure 2, according to one embodiment of the present invention, check valve 11 is integrated with in described bi-bit bi-pass spring hydraulicchange-over valve 12, when the oil pressure of the entrance of described bi-bit bi-pass spring hydraulicchange-over valve 12 is 0, described check valve 11 stops the fluid in the epitrochoidal chamber 13 of described hydraulic actuating cylinder 6 to flow out, thus the working portion 14 of hydraulic actuating cylinder 6 can be made to keep motionless.
As shown in Figure 3, according to another embodiment of the invention, first throttle valve 10 is integrated with in described bi-bit bi-pass spring hydraulicchange-over valve 12, when the oil pressure of the entrance of described bi-bit bi-pass spring hydraulicchange-over valve 12 is 0, described first throttle valve 10 makes the fluid in the epitrochoidal chamber 13 of described hydraulic actuating cylinder 6 slowly flow out, thus the working portion 14 of hydraulic actuating cylinder 6 can be made slowly to fall after rise.
Conveniently control the rising or falling speed of lifting mechanism, preferably, described safety valve 7 also comprises second throttle 9, and this second throttle 9 is connected between described bi-bit bi-pass spring change-over valve 12 and the epitrochoidal chamber 13 of described hydraulic actuating cylinder 6.
Fig. 4 to Fig. 7 shows four kinds of embodiments of the safety valve of the hydraulic efficiency pressure system for lifting mechanism.In the embodiment shown in Fig. 4, safety valve 7 comprises bi-bit bi-pass spring hydraulicchange-over valve 12 and second throttle 9, is integrated with check valve 11 in bi-bit bi-pass spring hydraulicchange-over valve 12; In the embodiment shown in Fig. 5, safety valve 7 comprises bi-bit bi-pass spring hydraulicchange-over valve 12 and second throttle 9, is integrated with first throttle valve 10 in bi-bit bi-pass spring hydraulicchange-over valve 12; In the embodiment shown in fig. 6, safety valve 7 only comprises bi-bit bi-pass spring hydraulicchange-over valve 12, is integrated with check valve 11 in bi-bit bi-pass spring hydraulicchange-over valve 12; In the embodiment shown in figure, safety valve 7 only comprises bi-bit bi-pass spring hydraulicchange-over valve 12, is integrated with first throttle valve 10 in bi-bit bi-pass spring hydraulicchange-over valve 12.
Back pressure valve 8 for when lift valve 5 is in decline position for safety valve 7 provides back pressure.Back pressure valve 8 can take various suitable form, and such as, described back pressure valve 8 can be flow regulating valve.As selection, back pressure valve 8 also can be check valve.
Back pressure valve 8 can be arranged in position, and such as, back pressure valve 8 can be arranged between lift valve 5 and safety valve 7, between the return opening that also can be arranged on fuel tank 1 and lift valve 5.In order to prevent the lifting speed affecting lifting mechanism, preferably, described back pressure valve 8 is arranged between described fuel tank 1 and the return opening of described lift valve 5.
Described lift valve 5 can take various suitable form.Such as, lift valve 5, except having lifting position and decline position, can also have middle stop bit, stop bit in this, and described fuel tank 1 is not connected with described hydraulic actuating cylinder 6, thus easily lifting mechanism can be locked in any position.
In order to filter the impurity of fluid in fuel tank 1 easily, preferably, oil filter 2 is connected with between described fuel tank 1 and described Hydraulic Pump 3.
In order to control the pressure of lift valve 5 entrance easily, so that lifting lifting mechanism reposefully, preferably, between the outlet of described Hydraulic Pump 3 and described fuel tank 1, be connected with by pass valve 4.
Described epitrochoidal chamber 13 can be the rod chamber of hydraulic actuating cylinder 6, also can be the rodless cavity of hydraulic actuating cylinder 6, select according to specific needs.When epitrochoidal chamber 13 is the rodless cavity of hydraulic actuating cylinder 6, piston rod is the working portion 14 of hydraulic actuating cylinder 6, is responsible for being risen by lifting mechanism or falling.
The working process of the hydraulic efficiency pressure system for lifting mechanism that the specific embodiment of the invention provides is described below in conjunction with accompanying drawing.
As shown in Figures 2 and 3, when lift valve 5 is in lifting position, oil pump in fuel tank 1 enters in lift valve 5 by Hydraulic Pump 3, bi-bit bi-pass spring hydraulicchange-over valve 12 opens straight-through oil circuit under the double action of oil pressure and spring pressure, fluid flows in the epitrochoidal chamber 13 of hydraulic actuating cylinder 6, thus realizes the lifting of the working portion 14 of hydraulic actuating cylinder 6, when lift valve 5 is in decline position, back pressure valve 8 produces back pressure in the entrance of bi-bit bi-pass spring hydraulicchange-over valve 12, bi-bit bi-pass spring hydraulicchange-over valve 12 opens straight-through oil circuit under the back pressure of back pressure valve 8 and the double action of spring pressure, fluid in the epitrochoidal chamber 13 of hydraulic actuating cylinder 6 is flowed back in fuel tank 1 by safety valve 7 and lift valve 5, thus realizes the decline of the working portion 14 of hydraulic actuating cylinder 6, no matter lift valve 5 is in lifting position and still declines position, when oil pipe between fuel tank 1 and bi-bit bi-pass spring hydraulicchange-over valve 12 occurs to burst, the pressure of the entrance of bi-bit bi-pass spring hydraulicchange-over valve 12 is 0, and the pressure in bi-bit bi-pass spring hydraulicchange-over valve 12 exit is larger, this pressure overcomes the spring force of bi-bit bi-pass spring hydraulicchange-over valve 12, thus make bi-bit bi-pass spring hydraulicchange-over valve 12 be in check valve 11 state or first throttle valve 10 state, the fluid in described epitrochoidal chamber 13 is stoped to flow out or the fluid in described epitrochoidal chamber 13 is slowly flowed out, thus the working portion 14 of hydraulic actuating cylinder 6 can be made to keep motionless or slowly fall after rise, hydraulic efficiency pressure system is avoided to damage, and then avoid device damage and personal casualty, ensure that the safe operation of lifting mechanism.
Hydraulic efficiency pressure system for lifting mechanism provided by the invention can be widely used in the lifting mechanism of various engineering truck, the lifting mechanism of such as dumping truck.
Below the preferred embodiment of the present invention is described in detail by reference to the accompanying drawings; but; the present invention is not limited to the detail in above-mentioned embodiment; within the scope of technical conceive of the present invention; can carry out multiple simple variant to technical scheme of the present invention, these simple variant all belong to protection scope of the present invention.
It should be noted that in addition, each the concrete technical characteristic described in above-mentioned detailed description of the invention, in reconcilable situation, can be combined by any suitable mode.In order to avoid unnecessary repetition, the present invention illustrates no longer separately to various possible array mode.
In addition, also can carry out combination in any between various different embodiment of the present invention, as long as it is without prejudice to thought of the present invention, it should be considered as content disclosed in this invention equally.
Claims (9)
1. the hydraulic efficiency pressure system for lifting mechanism, this hydraulic efficiency pressure system comprises fuel tank (1), Hydraulic Pump (3), lift valve (5) and hydraulic actuating cylinder (6), described lift valve (5) has lifting position and decline position, in described lifting position, described lift valve (5) makes the fluid in described fuel tank (1) flow in the epitrochoidal chamber (13) of described hydraulic actuating cylinder (6) by described Hydraulic Pump (3), in described decline position, described lift valve (5) makes the fluid in the epitrochoidal chamber of described hydraulic actuating cylinder (6) (13) flow back in described fuel tank (1), it is characterized in that, safety valve (7) is also connected with between the epitrochoidal chamber (13) of described lift valve (5) and described hydraulic actuating cylinder (6), back pressure valve (8) is connected with between described fuel tank (1) and described safety valve (7), when the oil pressure of the entrance of described safety valve (7) is 0, described safety valve (7) stops the fluid in described epitrochoidal chamber (13) flow out or the fluid in described epitrochoidal chamber (13) is slowly flowed out, when the oil pressure of the entrance of described safety valve (7) is not 0, described safety valve (7) is by the oil circuit conducting between described lift valve (5) and described epitrochoidal chamber (13), the entrance of described safety valve (7) is the hydraulic fluid port be connected with described lift valve (5) of described safety valve (7), wherein, described safety valve (7) comprises bi-bit bi-pass spring hydraulicchange-over valve (12), when the inlet pressure sum of spring pressure and described bi-bit bi-pass spring hydraulicchange-over valve (12) is greater than the delivery pressure of described bi-bit bi-pass spring hydraulicchange-over valve (12), described bi-bit bi-pass spring hydraulicchange-over valve (12) is by the oil circuit conducting between described lift valve (5) and described epitrochoidal chamber (13), and when the inlet pressure sum of spring pressure and described bi-bit bi-pass spring hydraulicchange-over valve (12) is less than the delivery pressure of described bi-bit bi-pass spring hydraulicchange-over valve (12), described safety valve (7) stops the fluid in described epitrochoidal chamber (13) flow out or the fluid in described epitrochoidal chamber (13) is slowly flowed out.
2. the hydraulic efficiency pressure system for lifting mechanism according to claim 1, wherein, described safety valve (7) is arranged near described hydraulic actuating cylinder (6).
3. the hydraulic efficiency pressure system for lifting mechanism according to claim 1, wherein, check valve (11) is integrated with in described bi-bit bi-pass spring hydraulicchange-over valve (12), when the oil pressure of the entrance of described bi-bit bi-pass spring hydraulicchange-over valve (12) is 0, described check valve (11) stops the fluid in the epitrochoidal chamber (13) of described hydraulic actuating cylinder (6) to flow out.
4. the hydraulic efficiency pressure system for lifting mechanism according to claim 1, wherein, first throttle valve (10) is integrated with in described bi-bit bi-pass spring hydraulicchange-over valve (12), when the oil pressure of the entrance of described bi-bit bi-pass spring hydraulicchange-over valve (12) is 0, described first throttle valve (10) makes the fluid in the epitrochoidal chamber of described hydraulic actuating cylinder (6) (13) slowly flow out.
5. the hydraulic efficiency pressure system for lifting mechanism according to claim 1, wherein, described safety valve (7) also comprises second throttle (9), and this second throttle (9) is connected between the epitrochoidal chamber (13) of described bi-bit bi-pass spring change-over valve (12) and described hydraulic actuating cylinder (6).
6. the hydraulic efficiency pressure system for lifting mechanism according to claim 1, wherein, described back pressure valve (8) is flow regulating valve.
7. the hydraulic efficiency pressure system for lifting mechanism according to claim 1, wherein, described back pressure valve (8) is arranged between the return opening of described fuel tank (1) and described lift valve (5).
8. the hydraulic efficiency pressure system for lifting mechanism according to claim 1, wherein, described lift valve (5) has middle stop bit, stop bit in this, and described fuel tank (1) is not connected with described hydraulic actuating cylinder (6).
9. the hydraulic efficiency pressure system for lifting mechanism according to claim 1, wherein, is connected with by pass valve (4) between the outlet of described Hydraulic Pump (3) and described fuel tank (1).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110240479.2A CN102951557B (en) | 2011-08-19 | 2011-08-19 | Hydraulic system used for elevating mechanism |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110240479.2A CN102951557B (en) | 2011-08-19 | 2011-08-19 | Hydraulic system used for elevating mechanism |
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| CN102951557A CN102951557A (en) | 2013-03-06 |
| CN102951557B true CN102951557B (en) | 2015-02-18 |
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| CN201110240479.2A Active CN102951557B (en) | 2011-08-19 | 2011-08-19 | Hydraulic system used for elevating mechanism |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108916132A (en) * | 2018-07-31 | 2018-11-30 | 宁波市镇海海威液压科技有限公司 | A kind of device of accurate control hydraulic cylinder raising and lowering |
| CN112777523A (en) * | 2019-11-05 | 2021-05-11 | 中冶宝钢技术服务有限公司 | Auxiliary dismounting trolley for double-layer cinder valve |
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| CN101210581A (en) * | 2006-12-28 | 2008-07-02 | 中国国际海运集装箱(集团)股份有限公司 | Self-reducing resisting hydraulic cylinder |
| JP2010254380A (en) * | 2009-04-21 | 2010-11-11 | Kobelco Cranes Co Ltd | Hose reel winding device for mobile crane |
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