CN220487970U - Hydraulic control floating load sensitive hydraulic system and electric arm vehicle - Google Patents
Hydraulic control floating load sensitive hydraulic system and electric arm vehicle Download PDFInfo
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- CN220487970U CN220487970U CN202322333317.4U CN202322333317U CN220487970U CN 220487970 U CN220487970 U CN 220487970U CN 202322333317 U CN202322333317 U CN 202322333317U CN 220487970 U CN220487970 U CN 220487970U
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Abstract
The utility model discloses a hydraulic control floating load sensitive hydraulic system and an electric arm vehicle, which relate to the technical field of hydraulic control, wherein the hydraulic control floating load sensitive hydraulic system comprises: a load-sensitive pump; a floating control valve connected with the load-sensitive pump through a first pipeline and a third pipeline; the load sensitive valve is connected with the floating control valve through a sixth pipeline and a seventh pipeline; the balance valve is connected with the floating control valve through a fourth pipeline and a fifth pipeline; a floating cylinder connected to the balance valve; the seventh pipeline is used for transmitting the load pressure of the load sensitive valve to the floating control valve, and the third pipeline is used for transmitting the highest load pressure of the system to the control oil port of the load sensitive pump; the fourth pipeline is connected with a pilot oil port of the balance valve, a main oil way of the balance valve is connected with the floating control valve through a fifth pipeline, and an unloading port of the floating control valve is connected with the hydraulic oil tank through a second pipeline. The system can improve the floating and locking reliability of the axle.
Description
Technical Field
The utility model relates to the technical field of hydraulic control, in particular to a hydraulic control floating load sensitive hydraulic system. In addition, the utility model also relates to an electric arm vehicle comprising the hydraulic control floating load sensitive hydraulic system.
Background
In the related art, the arm vehicles can be divided into electric arm vehicles and diesel arm vehicles according to different driving modes. The diesel-electric vehicle is generally driven by a hydraulic closed system, and therefore, a floating bridge is generally controlled by taking the pilot oil from the closed system. Unlike diesel-powered vehicles, electric-powered vehicles travel as motor driven, and therefore, it is impossible to take pilot oil from the traveling system to control the floating bridge.
At present, the control mode of the floating bridge of the electric arm vehicle mainly comprises a full-time floating control mode and an electric control floating control mode. The full-time floating control mode is to control the left and right floating cylinders to stretch and retract through a mechanical reversing valve arranged on the chassis, so that the axle is floated. The scheme has the advantages that the axle can be in a floating state at any moment, but the cost and the installation and debugging difficulty are high, and the further popularization of the scheme is limited.
The electric control floating control mode is to control the communication and locking of the rod cavity and the rodless cavity of the left and right floating oil cylinders through the electromagnetic ball valve, so as to realize the floating and locking of the axle. The scheme has the advantages of low cost, but the reliability of the system depends on the reliability of the electromagnetic ball valve to a great extent, and a certain failure risk exists.
In view of the foregoing, it is a problem to be solved by those skilled in the art to improve the floating and locking reliability of the axle.
Disclosure of Invention
Therefore, the utility model aims to provide a load-sensitive hydraulic system which can realize the hydraulic control floating control function of an electric locomotive and improve the floating and locking reliability of an axle.
Another object of the present utility model is to provide an electric arm vehicle comprising the above-described hydraulically floating load-sensitive hydraulic system.
In order to achieve the above object, the present utility model provides the following technical solutions:
a hydraulically floating load sensitive hydraulic system comprising:
a load-sensitive pump connected to the hydraulic tank;
a floating control valve connected with the load-sensitive pump through a first pipeline and a third pipeline;
the load sensitive valve is connected with the floating control valve through a sixth pipeline and a seventh pipeline;
the balance valve is connected with the floating control valve through a fourth pipeline and a fifth pipeline;
a floating cylinder connected to the balance valve;
the first pipeline and the sixth pipeline are system main oil ways, the seventh pipeline is used for transmitting the load pressure of the load sensitive valve to the floating control valve, and the third pipeline is used for transmitting the highest load pressure of the system to a control oil port of the load sensitive pump;
the fourth pipeline is connected with a pilot oil port of the balance valve, and an unloading port of the floating control valve is connected with the hydraulic oil tank through a second pipeline; when the fourth pipeline is communicated with high-pressure oil, the balance valve is opened, so that a rod cavity and a rodless cavity of the floating oil cylinder are communicated through the fifth pipeline, and the floating oil cylinder (5) is in a floating state; and when the fourth pipeline is communicated with oil return, the balance valve is locked, so that the floating oil cylinder is locked.
Preferably, the floating control valve comprises a three-way pressure reducing valve, a switching valve and a switching valve;
the inlet of the three-way pressure reducing valve is connected with the system main oil way, the outlet of the three-way pressure reducing valve is connected with an oil port a of the switch valve, the leakage port of the three-way pressure reducing valve is connected with an oil port b of the switch valve and then is connected with the second pipeline, and the second pipeline is used for communicating the oil port b of the switch valve with the hydraulic oil tank;
the d input port of the switching valve is connected with the c oil port of the switching valve, the e input port of the switching valve is connected with the load sensitive signal port of the load sensitive valve, and the f output port of the switching valve is connected with the control oil port;
when the switch valve is not powered, the oil port a is not communicated with other oil ports of the switch valve, and when the switch valve is powered, the oil port a is communicated with the oil port c.
Preferably, the floating control valve comprises a two-way pressure reducing valve, a switching valve and a switching valve, wherein an inlet of the two-way pressure reducing valve is connected with the system main oil way, an outlet of the two-way pressure reducing valve is connected with an oil port a of the switching valve, and an oil port b of the switching valve is connected with the second pipeline;
the d input port of the switching valve is connected with the c oil port of the switching valve, the e input port of the switching valve is connected with the load sensitive signal port of the load sensitive valve, and the f output port of the switching valve is connected with the control oil port;
when the switch valve is not powered, the oil port a is not communicated with other oil ports of the switch valve, and when the switch valve is powered, the oil port a is communicated with the oil port c.
Preferably, the switching valve comprises a shuttle valve or a one-way valve group.
Preferably, the load sensing valve comprises a pre-valve compensating load sensing valve or a post-valve compensating load sensing valve.
Preferably, the balancing valve comprises a hydraulically controlled check valve group or a hydraulic balancing valve.
An electric arm vehicle comprising a hydraulically floating load sensitive hydraulic system as claimed in any preceding claim.
When the hydraulic control floating load sensitive hydraulic system provided by the utility model is used, when the whole vehicle is only in a floating single action, the floating control valve is switched to a lower working state, on one hand, the pressure behind the valve is introduced into the control oil port of the load sensitive pump through the third pipeline so as to push the swash plate of the load sensitive pump, the outlet of the load sensitive pump keeps lower pressure Pa in a steady state, the pressure Pa is equal to the sum of the set pressure P1 of the floating control valve and the set pressure delta P of the pressure compensator of the load sensitive pump, namely Pa=P1+delta P, and the system is in a low energy consumption state; and on the other hand, the pressure oil output by the load sensitive pump is communicated to a pilot oil port of the balance valve through a fourth pipeline so as to open the balance valve, and a rod cavity and a rodless cavity of the floating oil cylinder are communicated through a fifth pipeline, so that axle floating is realized.
When the whole vehicle is in combined actions such as floating and steering and the floating load pressure is the highest, the floating control valve can still introduce the valve back pressure into the control oil port of the load sensitive pump through the third pipeline, so that the outlet of the load sensitive pump keeps lower pressure Pa in a steady state. When the whole vehicle is in combined actions such as floating and steering and the floating load pressure is not the highest, the floating control valve introduces the load pressure P2 of the load sensitive valve into a control oil port of the load sensitive pump through a third pipeline, and the control oil port of the load sensitive pump keeps pressure Pb according to an actual load steady state, wherein Pb=P2+DeltaP.
When the axle is required to be locked, the floating control valve is switched to an upper working state, and a pilot oil port of the balance valve can be communicated with the hydraulic oil tank through a second pipeline, so that the balance valve is closed, and the floating oil cylinder is ensured to be in a locking state. At the same time, the floating load pressure is unloaded through the floating control valve, and the outlet pressure of the load-sensitive pump is only related to the load pressure of the load-sensitive valve and the set pressure of the load-sensitive pump.
In summary, the hydraulic control floating load sensitive hydraulic system provided by the utility model can realize the hydraulic control floating control function of the electric locomotive and improve the floating and locking reliability of the axle.
In addition, the utility model also provides an electric arm vehicle comprising the hydraulic control floating load sensitive hydraulic system.
Drawings
In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the drawings that are required to be used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are only embodiments of the present utility model, and that other drawings can be obtained according to the provided drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of a hydraulically controlled floating load-sensitive hydraulic system according to the present utility model;
fig. 2 is a schematic structural view of the floating control valve.
In fig. 1-2:
the hydraulic oil tank is characterized in that the hydraulic oil tank is composed of a load sensitive pump 1, a floating control valve 2, a three-way pressure reducing valve 2-1, a switching valve 2-2, a switching valve 2-3, a load sensitive valve 3, a balance valve 4, a floating oil cylinder 5, a hydraulic oil tank 6, a first pipeline 7, a second pipeline 8, a third pipeline 9, a fourth pipeline 10, a fifth pipeline 11, a sixth pipeline 12 and a seventh pipeline 13.
Detailed Description
The following description of the embodiments of the present utility model will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present utility model, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.
The utility model provides a hydraulic control floating load sensitive hydraulic system which can realize the hydraulic control floating control function of an electric locomotive and improve the floating and locking reliability of an axle. Another core of the utility model is to provide an electric arm vehicle comprising the above-mentioned hydraulically floating load-sensitive hydraulic system.
Referring to fig. 1 and 2, fig. 1 is a schematic structural diagram of a hydraulic control floating load-sensitive hydraulic system according to the present utility model; fig. 2 is a schematic structural view of the floating control valve.
The present embodiment provides a hydraulically floating load-sensitive hydraulic system, comprising:
a load-sensitive pump 1 connected to a hydraulic tank 6;
a floating control valve 2 connected to the load-sensitive pump 1 via a first line 7 and a third line 9;
a load-sensitive valve 3 connected to the float control valve 2 via a sixth line 12 and a seventh line 13;
a balance valve 4 connected to the float control valve 2 through a fourth pipe 10 and a fifth pipe 11;
a floating cylinder 5 connected to the balance valve 4;
the first pipeline 7 and the sixth pipeline 12 are main oil ways of the system, the seventh pipeline 13 is used for transmitting the load pressure of the load sensitive valve 3 to the floating control valve 2, and the third pipeline 9 is used for transmitting the highest load pressure of the system to a control oil port of the load sensitive pump 1;
the fourth pipeline 10 is connected with a pilot oil port of the balance valve 4, and an unloading port of the floating control valve 2 is connected with the hydraulic oil tank 6 through a second pipeline 8; when the fourth pipeline 10 is communicated with high-pressure oil, the balance valve 4 is opened, so that the rod cavity and the rodless cavity of the floating oil cylinder 5 are communicated through the fifth pipeline 11, and the floating oil cylinder 5 is in a floating state; when the fourth pipe 10 communicates with the return oil, the balance valve 4 is closed to close the floating cylinder 5.
It should be noted that the floating control valve 2 may provide a pilot signal for the balance valve 4 to control the opening and locking of the balance valve 4, so as to realize the communication or locking between the rod cavity and the rodless cavity of the floating cylinder 5.
The shapes, structures, types and the like of the load-sensitive pump 1, the floating control valve 2, the load-sensitive valve 3, the balance valve 4, the floating cylinder 5, the first pipeline 7, the second pipeline 8, the third pipeline 9, the fourth pipeline 10, the fifth pipeline 11, the sixth pipeline 12 and the seventh pipeline 13 can be determined according to actual situations and actual demands in an actual application process.
When the hydraulic control floating load sensitive hydraulic system provided by the utility model is used, when the whole vehicle is only in a floating single action, the floating control valve 2 is switched to a lower working state, on one hand, the pressure after the valve is introduced into the control oil port of the load sensitive pump 1 through the third pipeline 9 to push the swash plate of the load sensitive pump 1, so that the outlet of the load sensitive pump 1 keeps lower pressure Pa in a steady state, the pressure Pa is equal to the sum of the set pressure P1 of the floating control valve 2 and the set pressure delta P of the pressure compensator of the load sensitive pump 1, namely Pa=P1+delta P, and the system is in a low energy consumption state; on the other hand, the pressure oil output by the load-sensitive pump 1 is communicated to a pilot oil port of the balance valve 4 through a fourth pipeline 10 to open the balance valve 4, so that a rod cavity and a rodless cavity of the floating oil cylinder 5 are communicated through a fifth pipeline 11, and axle floating is realized.
When the whole vehicle is in combined actions such as floating and steering and the floating load pressure is the highest, the floating control valve 2 can still introduce the valve back pressure into the control oil port of the load sensitive pump 1 through the third pipeline 9, so that the outlet of the load sensitive pump 1 keeps lower pressure Pa in a steady state. When the whole vehicle is in combined actions such as floating and steering and the floating load pressure is not the highest, the floating control valve 2 introduces the load pressure P2 of the load sensitive valve 3 into the control oil port of the load sensitive pump 1 through the third pipeline 9, and the control oil port of the load sensitive pump 1 maintains the pressure Pb according to the actual load steady state, wherein Pb=P2+ΔP.
When the axle is required to be locked, the floating control valve 2 is switched to an upper working state, and the pilot oil port of the balance valve 4 can be communicated with the hydraulic oil tank 6 through the second pipeline 8, so that the balance valve 4 is closed, and the floating oil cylinder 5 is ensured to be in a locking state. At the same time, the floating load pressure is unloaded via the floating control valve 2, the outlet pressure of the load-sensitive pump 1 being dependent only on the load pressure of the load-sensitive valve 3 and the set pressure of the load-sensitive pump 1.
In summary, the hydraulic control floating load sensitive hydraulic system provided by the utility model can realize the hydraulic control floating control function of the electric locomotive and improve the floating and locking reliability of the axle.
On the basis of the above embodiment, it is preferable that the floating control valve 2 includes a three-way pressure reducing valve 2-1, an on-off valve 2-2, and a switching valve 2-3; the inlet of the three-way pressure reducing valve 2-1 is connected with a main oil way of the system, the outlet of the three-way pressure reducing valve 2-1 is connected with an oil port a of the switch valve 2-2, the leakage port of the three-way pressure reducing valve 2-1 is connected with an oil port b of the switch valve 2-2 and then is connected with a second pipeline 8, and the oil port b is communicated with the hydraulic oil tank 6 by the second pipeline 8; the d input port of the switching valve 2-3 is connected with the c oil port of the switching valve 2-2, the e input port of the switching valve 2-3 is connected with the load sensitive signal port of the load sensitive valve 3, and the f output port of the switching valve 2-3 is connected with the control oil port, and the structure is shown in figure 2; when the switch valve 2-2 is not powered, the oil port a is not communicated with other oil ports of the switch valve 2-2, and when the switch valve 2-2 is powered, the oil port a is communicated with the oil port c.
The first pipeline 7 and the sixth pipeline 12 are main oil paths of the system, the seventh pipeline 13 transmits the load pressure of the load sensitive valve 3 to the switching valve 2-3 in the switching valve 2-2, and then the highest load pressure of the system is transmitted to the control oil port of the load sensitive pump 1 through the third pipeline 9. The on-off valve 2-2 may be a floating on-off valve or an electromagnetic directional valve. The device is suitable for a load sensitive system, namely, the system flow is obtained as required, and the low-energy-consumption operation of the system can be realized.
In addition, when the switch valve 2-2 is not powered, the oil port a is not communicated with other oil ports of the switch valve 2-2, namely, the oil port a is not communicated with the oil port b and the oil port c of the switch valve 2-2, namely, when the switch valve 2-2 is not powered, the oil port b is communicated with the oil port c, the switch valve 2-2 is in an upper working state, the pilot oil port of the balance valve 4 is communicated with the hydraulic oil tank 6 through the switch valve 2-2 and the second pipeline 8, the balance valve 4 is closed, and the floating oil cylinder 5 is in a locking state.
However, when the switch valve 2-2 is powered on, the oil port a is communicated with the oil port c, the switch valve 2-2 is in a lower working state, pressure oil output by the load sensitive pump 1 is communicated with a pilot oil port of the balance valve 4 through the three-way pressure reducing valve 2-1 and the switch valve 2-2, the balance valve 4 is opened, and a rod cavity and a rodless cavity of the floating oil cylinder 5 are communicated with each other, so that axle floating is realized.
Preferably, the floating control valve 2 comprises a two-way pressure reducing valve, a switch valve 2-2 and a switch valve 2-3, wherein an inlet of the two-way pressure reducing valve is connected with a main oil way of the system, an outlet of the two-way pressure reducing valve is connected with an oil port a of the switch valve 2-2, and an oil port b of the switch valve 2-2 is connected with a second pipeline 8; the d input port of the switching valve 2-3 is connected with the c oil port of the switching valve 2-2, the e input port of the switching valve 2-3 is connected with the load sensitive signal port of the load sensitive valve 3, and the f output port of the switching valve 2-3 is connected with the control oil port; when the switch valve 2-2 is not powered, the oil port a is not communicated with other oil ports of the switch valve 2-2, and when the switch valve 2-2 is powered, the oil port a is communicated with the oil port c. Namely, the two-way pressure reducing valve can replace the three-way pressure reducing valve 2-1.
On the basis of the above embodiment, the switching valve 2-3 preferably comprises a shuttle valve or a one-way valve group.
It should be noted that the shuttle valve is a common control element, and its main function is to control the pressure and flow of the liquid, so as to implement adjustment and control of the mechanical movement by the hydraulic system. The shuttle valve is generally composed of a valve body, a valve core, a guide piece and the like, and the working principle of the shuttle valve is that the hydraulic control of an acting piece is realized by changing the position of the valve core and adjusting a flow channel of oil. Its function is to be able to select the highest pressure output among the pressures at a plurality of locations. And the shuttle valve can be replaced by a one-way valve group, so that the effect of hydraulic control on the acting element is realized.
Preferably, the load sensing valve 3 comprises a pre-valve compensating load sensing valve or a post-valve compensating load sensing valve.
The load-sensitive valve 3 is a closed-loop system with differential pressure feedback, and can realize the follow-up control of the load pressure by the load-sensitive pump 1 under the flow instruction condition. The load sensing valve 3 may feed back the pressure of the load to the load sensing pump 1, causing the load sensing pump 1 to output a slightly greater pressure than the load is required, the difference being set by the spring of the load sensing valve 3. When the load is reduced, the pressure of the oil output by the load sensitive pump 1 is reduced, so that the consumption of energy sources is reduced, and the energy is saved very much. Namely, the system not only can ensure that the pressure of the load-sensitive pump 1 is automatically matched with the load required, but also can accurately control the speed of the load.
In addition, the load sensitive valve 3 in two forms of the pre-valve compensation type and the post-valve compensation type are suitable for the system, and the type of the load sensitive valve 3 can be determined according to actual conditions and actual demands in the actual application process.
Preferably, the balancing valve 4 comprises a pilot operated check valve set or a hydraulic balancing valve.
The pilot operated check valve is a valve that can make the check valve flow in reverse direction by controlling the fluid pressure. The hydraulic control one-way valve plays an important role in hydraulic supporting equipment of coal mine machinery. The hydraulic control one-way valve is different from the common one-way valve in that a control oil way is added, when the control oil way is not connected with pressure oil, the hydraulic control one-way valve works like the common one-way valve, and the pressure oil only flows from the oil inlet to the oil outlet and cannot flow reversely. When the control oil way is provided with control pressure input, the piston ejector rod of the hydraulic control one-way valve moves under the action of pressure oil, the ejector rod is used for ejecting the one-way valve, so that the oil inlet and the oil outlet are communicated, and if the oil outlet is larger than the oil inlet, the oil can reversely flow. The hydraulic control check valve group is formed by integrating a plurality of hydraulic control check valves. In addition, the hydraulic balance valve can replace a hydraulic control one-way valve group, so that similar using effects are achieved.
To further illustrate the method of using the hydraulically floating load-sensitive hydraulic system provided by the present utility model, an example is provided below.
When the whole vehicle is only in a floating single action, the switch valve 2-2 in the floating control valve 2 is powered, and the switch valve 2-2 is switched to work in a lower position. On one hand, the pressure behind the valve of the three-way pressure reducing valve 2-1 is introduced into a control oil port of the load sensitive pump 1 through the switch valve 2-2 and the switch valve 2-3 to push a swash plate of the load sensitive pump 1, so that the pressure Pa of an outlet of the load sensitive pump 1 is kept lower in a steady state. This pressure Pa is equal to the sum of the set pressure P1 of the three-way pressure-reducing valve 2-1 plus the pressure compensator set pressure Δp of the load-sensitive pump 1, i.e. pa=p1+Δp, when the system is in a low energy consumption state.
On the other hand, the pressure oil output by the load sensitive pump 1 is communicated with a pilot oil port of the balance valve 4 through the three-way pressure reducing valve 2-1 and the switch valve 2-2, and the balance valve 4 is opened, so that a rod cavity and a rodless cavity of the floating oil cylinder 5 are communicated with each other, and axle floating is realized.
When the whole vehicle is in combined actions such as floating and steering and the floating load pressure is the highest, the switching valve 2-3 still introduces the valve back pressure of the three-way pressure reducing valve 2-1 into the control oil port of the load sensitive pump 1 through the switching valve 2-2 and the switching valve 2-3, and the lower pressure Pa is kept at the steady state of the outlet of the load sensitive pump 1.
When the whole vehicle is in combined actions such as floating and steering and the floating load pressure is not the highest, the switching valve 2-3 introduces the load pressure P2 of the load sensitive valve 3 into the control oil port of the load sensitive pump 1 through the switching valve 2-3, and the outlet of the load sensitive pump 1 keeps pressure Pb according to the actual load steady state, wherein Pb=P2+DeltaP. In addition, in order to prevent the whole vehicle from tipping, a three-way pressure reducing valve 2-1 is arranged at the communication part of the rod cavity and the rodless cavity of the floating oil cylinder 5 to provide back pressure and supplement oil for a floating system.
When the axle is required to be locked, the switch valve 2-2 in the floating control valve 2 is powered off, and the switch valve 2-2 is in an upper working state. The pilot oil port of the balance valve 4 is communicated with the hydraulic oil tank 6 through the switch valve 2-2, the balance valve 4 is closed, and the floating oil cylinder 5 is ensured to be in a locking state. At the same time, the floating load pressure is relieved via the switching valve 2-2 and the second line 8, the outlet pressure of the load-sensitive pump 1 being dependent only on the load pressure of the load-sensitive valve 3 and the set pressure of the load-sensitive pump 1.
In addition to the hydraulic control floating load sensitive hydraulic system, the utility model also provides an electric arm vehicle comprising the hydraulic control floating load sensitive hydraulic system disclosed in the embodiment, and the structure of other parts of the electric arm vehicle is referred to the prior art, and is not repeated herein.
It should be noted that the first line 7, the second line 8, the third line 9, the fourth line 10, the fifth line 11, the sixth line 12, and the seventh line 13 are mentioned in this specification, wherein the first line, the second line, the third line, the fourth line, the fifth line, the sixth line, and the seventh line are merely for distinguishing the difference of the positions, and are not sequentially separated.
It should be noted that the direction or positional relationship indicated by "up and down", "in and out", etc. in the present application is based on the direction or positional relationship shown in the drawings, and is merely for convenience of description and understanding, and does not indicate or imply that the device or element to be referred to must have a specific direction, be configured and operated in a specific direction, and therefore should not be construed as limiting the present utility model.
In the present specification, each embodiment is described in a progressive manner, and each embodiment is mainly described in a different point from other embodiments, and identical and similar parts between the embodiments are all enough to refer to each other. Any combination of all the embodiments provided in the present utility model is within the protection scope of the present utility model, and will not be described herein.
The hydraulic control floating load sensitive hydraulic system and the electric arm vehicle provided by the utility model are described in detail. The principles and embodiments of the present utility model have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the method of the present utility model and its core ideas. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the utility model can be made without departing from the principles of the utility model and these modifications and adaptations are intended to be within the scope of the utility model as defined in the following claims.
Claims (7)
1. A hydraulically floating load-sensitive hydraulic system, comprising:
a load-sensitive pump (1) connected to the hydraulic tank (6);
a floating control valve (2) connected to the load-sensitive pump (1) via a first line (7) and a third line (9);
a load-sensitive valve (3) connected to the float control valve (2) via a sixth line (12) and a seventh line (13);
a balancing valve (4) connected to the floating control valve (2) via a fourth line (10) and a fifth line (11);
a floating cylinder (5) connected to the balance valve (4);
the first pipeline (7) and the sixth pipeline (12) are system main oil ways, the seventh pipeline (13) is used for transmitting the load pressure of the load sensitive valve (3) to the floating control valve (2), and the third pipeline (9) is used for transmitting the highest load pressure of the system to a control oil port of the load sensitive pump (1);
the fourth pipeline (10) is connected with a pilot oil port of the balance valve (4), and an unloading port of the floating control valve (2) is connected with the hydraulic oil tank (6) through a second pipeline (8); when the fourth pipeline (10) is communicated with high-pressure oil, the balance valve (4) is opened, so that a rod cavity and a rodless cavity of the floating oil cylinder (5) are communicated through the fifth pipeline (11), and the floating oil cylinder (5) is in a floating state; when the fourth pipeline (10) is communicated with oil return, the balance valve (4) is closed, so that the floating oil cylinder (5) is closed.
2. The hydraulically floating load sensitive hydraulic system according to claim 1, characterized in that the floating control valve (2) comprises a three-way pressure reducing valve (2-1), an on-off valve (2-2) and a switching valve (2-3);
the inlet of the three-way pressure reducing valve (2-1) is connected with the main oil way of the system, the outlet of the three-way pressure reducing valve (2-1) is connected with an oil port a of the switch valve (2-2), the leakage port of the three-way pressure reducing valve (2-1) is connected with an oil port b of the switch valve (2-2) and then is connected with the second pipeline (8), and the oil port b is communicated with the hydraulic oil tank (6) by the second pipeline (8);
the d input port of the switching valve (2-3) is connected with the c oil port of the switching valve (2-2), the e input port of the switching valve (2-3) is connected with the load sensitive signal port of the load sensitive valve (3), and the f output port of the switching valve (2-3) is connected with the control oil port;
when the switch valve (2-2) is not powered, the oil port a is not communicated with other oil ports of the switch valve (2-2), and when the switch valve (2-2) is powered, the oil port a is communicated with the oil port c.
3. The hydraulically floating load sensitive hydraulic system according to claim 1, characterized in that the floating control valve (2) comprises a two-way pressure reducing valve, a switch valve (2-2) and a switching valve (2-3), the inlet of the two-way pressure reducing valve is connected with the system main oil circuit, the outlet of the two-way pressure reducing valve is connected with the a oil port of the switch valve (2-2), and the b oil port of the switch valve (2-2) is connected with the second pipeline (8);
the d input port of the switching valve (2-3) is connected with the c oil port of the switching valve (2-2), the e input port of the switching valve (2-3) is connected with the load sensitive signal port of the load sensitive valve (3), and the f output port of the switching valve (2-3) is connected with the control oil port;
when the switch valve (2-2) is not powered, the oil port a is not communicated with other oil ports of the switch valve (2-2), and when the switch valve (2-2) is powered, the oil port a is communicated with the oil port c.
4. A hydraulically floating load sensitive hydraulic system according to claim 2 or 3, characterized in that the switching valve (2-3) comprises a shuttle valve or a one-way valve group.
5. A hydraulically floating load sensitive hydraulic system according to any of claims 1 to 3, characterized in that the load sensitive valve (3) comprises a pre-valve compensated load sensitive valve or a post-valve compensated load sensitive valve.
6. A hydraulically floating load sensitive hydraulic system according to any one of claims 1 to 3, characterized in that the balancing valve (4) comprises a hydraulically controlled one-way valve group or a hydraulic balancing valve.
7. An electric arm vehicle comprising a hydraulically floating load sensitive hydraulic system according to any one of claims 1-6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322333317.4U CN220487970U (en) | 2023-08-29 | 2023-08-29 | Hydraulic control floating load sensitive hydraulic system and electric arm vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322333317.4U CN220487970U (en) | 2023-08-29 | 2023-08-29 | Hydraulic control floating load sensitive hydraulic system and electric arm vehicle |
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