CN110966276B

CN110966276B - Multi-way valve, hydraulic system and engineering machinery

Info

Publication number: CN110966276B
Application number: CN201911414607.3A
Authority: CN
Inventors: 崔骁; 王晓娟; 徐艳翠
Original assignee: Jiangsu Xugong Construction Machinery Research Institute Co ltd; Jiangsu Advanced Construction Machinery Innovation Center Ltd
Current assignee: Jiangsu Xugong Construction Machinery Research Institute Co ltd; Jiangsu Advanced Construction Machinery Innovation Center Ltd
Priority date: 2019-12-31
Filing date: 2019-12-31
Publication date: 2022-02-25
Anticipated expiration: 2039-12-31
Also published as: CN110966276A

Abstract

The invention discloses a multi-way valve, a hydraulic system and engineering machinery, relates to the field of engineering machinery, and aims to optimize the structure of the multi-way valve. The multi-way valve comprises a first working valve, a second working valve and a control valve. The first working valve comprises a first valve body and a first valve core arranged in the first valve body; the second working valve comprises a second valve body and a second valve core arranged in the second valve body; the control valve comprises a third valve body and a third valve core arranged in the third valve body; the control valve is communicated with the first working valve and the second working valve through the valve inner flow passage so as to control a working oil source of the first working valve and/or the second working valve; and the central axis of the first valve core, the central axis of the second valve core and the central axis of the third valve core are coplanar. The multi-way valve provided by the technical scheme realizes the layout of all the functional modules on the same horizontal plane, and effectively reduces the installation space.

Description

Multi-way valve, hydraulic system and engineering machinery

Technical Field

The invention relates to the field of engineering machinery, in particular to a multi-way valve, a hydraulic system and engineering machinery.

Background

In the field of engineering machinery, a walking hydraulic system comprises a left walking valve, a right walking valve and a straight walking valve. The walking valve belongs to the category of proportional reversing valves. The linear traveling valve is used for realizing the mutual switching of two states of supplying oil to the two traveling valves by one pump source simultaneously and supplying oil to the two traveling valves by the two pump sources respectively so as to avoid the interference of the load fluctuation of other actuating mechanisms on the traveling linkage valve group when the traveling motor and other actuating mechanisms perform composite actions.

Proportional reversing valves are common direction control elements in the hydraulic technology field. In the proportional reversing valve commonly used in the field of engineering machinery, hydraulic pilot control is mostly used. The working principle is as follows: the hydraulic oil from the pilot pump generates a linearly-changed pilot pressure by adjusting the operating mechanism, and the pressure directly drives the main valve core to displace and is balanced with the spring force at one end of the valve core, so that the proportional control of the position of the main valve core is finally realized.

In engineering machinery applications, most proportional directional valves have three working positions, so that bidirectional movement or rotation control of actuators such as hydraulic cylinders, hydraulic motors and the like and other special middle-position functions are realized. From the control theory, the traditional three-position four-way pilot proportional reversing valve belongs to open-loop control, and hydraulic interference in the valve core movement process is ignored. However, in some situations with large inertia load, frequent start and stop, large flow or high-speed actuating mechanism and need to perform precise flow regulation, the hydrodynamic force is a non-negligible interference factor. Such operating conditions are very common in actuating mechanisms such as excavator swing motors, travel motors, boom cylinders, etc. The additional hydraulic force can influence the displacement of the valve core, so that the valve port flow area of the proportional directional valve cannot be linearly changed according to an input signal, and the operation experience of the whole machine is influenced.

Disclosure of Invention

The invention provides a multi-way valve, a hydraulic system and engineering machinery, which are used for optimizing the structure of the multi-way valve.

An embodiment of the present invention provides a multi-way valve, including:

the first working valve comprises a first valve body and a first valve core arranged in the first valve body;

the second working valve comprises a second valve body and a second valve core arranged in the second valve body; and

the control valve comprises a third valve body and a third valve core arranged in the third valve body; the control valve is communicated with the first working valve and the second working valve through an inner valve flow passage so as to control a working oil source of the first working valve and/or the second working valve;

and the central axis of the first valve core, the central axis of the second valve core and the central axis of the third valve core are coplanar.

In some embodiments, the first working valve further comprises:

a first pilot reducing valve configured as a reducing valve;

a second pilot reducing valve configured as a reducing valve;

the first elastic connecting piece is arranged between the first pilot pressure reducing valve core of the first pilot pressure reducing valve and the first valve core; and

and the second elastic connecting piece is arranged between the second pilot pressure reducing valve core of the second pilot pressure reducing valve and the first valve core.

In some embodiments, the first pilot pressure reduction valve comprises:

the first pilot pressure reducing valve body is provided with a first pilot pressure reducing valve oil hole, and the first pilot pressure reducing valve core is installed in the first pilot pressure reducing valve oil hole; and

the first electromagnet is arranged at the first end of the first pilot pressure reducing valve core;

the first end of the first elastic connecting piece is abutted against the second end of the first pilot pressure reducing valve core, and the second end of the first elastic connecting piece is abutted against the first end of the first valve core.

In some embodiments, the second pilot pressure reduction valve comprises:

the second pilot pressure reducing valve body is provided with a second pilot pressure reducing valve oil hole, and the second pilot pressure reducing valve core is installed in the second pilot pressure reducing valve oil hole; and

the second electromagnet is arranged at the second end of the second pilot pressure reducing valve core;

wherein the second resilient coupling is disposed between the first end of the second pilot pressure relief spool and the second end of the first spool.

In some embodiments, the second elastic connector comprises:

the first end of the first spring abuts against the second end of the first valve core, and the second end of the first spring abuts against the second pilot pressure reducing valve body; and

and the first end of the second spring is propped against the second end of the first valve core, and the second end of the second spring is propped against the first end of the second pilot pressure reducing valve core.

In some embodiments, the second working valve is configured as a three-position, four-way reversing valve and the median function of the second working valve is Y-shaped.

In some embodiments, the second working valve further comprises:

a third pilot reducing valve configured as a reducing valve;

a fourth pilot reducing valve configured as a reducing valve;

a third elastic connection member provided between a third pilot pressure reducing valve spool of the third pilot pressure reducing valve and the second valve spool; and

and the fourth elastic connecting piece is arranged between the fourth pilot pressure reducing valve spool of the fourth pilot pressure reducing valve and the second valve spool.

In some embodiments, the third pilot pressure relief valve comprises:

the third pilot pressure reducing valve body is provided with a third pilot pressure reducing valve oil hole, and the third pilot pressure reducing valve core is installed in the third pilot pressure reducing valve oil hole; and

the third electromagnet is arranged at the first end of the third pilot pressure reducing valve core;

and the first end of the third elastic connecting piece is abutted against the second end of the third pilot pressure reducing valve core, and the second end of the third elastic connecting piece is abutted against the first end of the second valve core.

In some embodiments, the fourth pilot pressure reduction valve comprises:

the fourth pilot pressure reducing valve body is provided with a fourth pilot pressure reducing valve oil duct, and the fourth pilot pressure reducing valve core is installed in the fourth pilot pressure reducing valve oil duct; and

and the fourth electromagnet is arranged at the second end of the fourth pilot pressure reducing valve core.

In some embodiments, the fourth elastic connector comprises:

the first end of the third spring is abutted against the second end of the second valve core, and the second end of the third spring is abutted against the fourth pilot pressure-reducing valve body; and

and the first end of the fourth spring is propped against the second end of the second valve core, and the second end of the fourth spring is propped against the first end of the fourth pilot pressure reducing valve core.

In some embodiments, at least one of the first pilot pressure relief valve and the second pilot pressure relief valve is configured as a two-position three-way spool.

In some embodiments, the first working valve is configured as a three-position, four-way reversing valve and the median function of the first working valve is Y-shaped.

In some embodiments, the control valve is configured as a two-position, four-way reversing valve.

In some embodiments, the axial centerlines of the third valve body, the first valve body, and the second valve body are parallel; and, the third valve body is located between the first valve body and the second valve body.

In some embodiments, the second valve body is provided with a first oil inlet passage, and the first oil inlet passage is respectively communicated with the control valve and the first working oil port a2 of the second working valve through the valve inner flow passage of the second working valve; and the third valve body is provided with a second oil inlet path which is communicated with a first working oil port A3 of the control valve.

In some embodiments, the first valve body, the second valve body, and the third valve body are integral.

An embodiment of the present invention further provides a hydraulic system, including:

a first actuator;

a second actuator;

the multi-way valve provided by any technical scheme of the invention;

an oil outlet of the first pump is communicated with a first working oil port A2 of the second working valve, a second working oil port B2 of the second working valve is communicated with return oil, and a third working oil port Atr of the second working valve and a fourth working oil port Btr of the second working valve are communicated with the second actuator; and

and an oil outlet of the second pump is communicated with a first working oil port A3 of the control valve, a second working oil port B3 of the control valve is communicated with a first working oil port A2 of the second working valve, a third working oil port of the control valve is communicated with a first working oil port of the first working valve, and a fourth working oil port of the control valve is communicated with an oil supplementing oil way.

The embodiment of the invention also provides engineering machinery comprising the hydraulic system provided by any technical scheme of the invention.

According to the multi-way valve provided by the embodiment of the invention, the arrangement forms of the first working valve, the second working valve and the control valve are adopted, so that the central axis of the first valve core of the first working valve, the central axis of the second valve core of the second working valve and the central axis of the third valve core of the control valve are coplanar, the structure of the multi-way valve is very compact and exquisite, the valve bodies of the three valves can be connected into a whole, the structure of the multi-way valve is reduced, the size is smaller, and the structure of the multi-way valve is more compact. According to the multi-way valve provided by the technical scheme, the positions and the sizes of the working valve ports can be reasonably arranged, the layout of the functional modules on the same horizontal plane is realized, and the installation space is effectively reduced.

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limiting the invention. In the drawings:

FIG. 1 is a schematic diagram of a multi-way valve provided in accordance with an embodiment of the present invention;

FIG. 2 is a schematic cross-sectional view of a multi-way valve according to an embodiment of the present invention;

FIG. 3 is a schematic sectional view A-A of FIG. 2;

fig. 4 is a schematic cross-sectional view of a control valve of a multi-way valve according to an embodiment of the present invention;

FIG. 5 is a schematic diagram of the single operation of a first working valve of the multiple-way valve according to the embodiment of the invention;

FIG. 6 is a schematic diagram of the second working valve of the multi-way valve operating alone according to the embodiment of the present invention;

fig. 7 is a schematic view of the first working valve and the second working valve of the multi-way valve working together according to the embodiment of the invention.

Detailed Description

The technical solution provided by the present invention is explained in more detail with reference to fig. 1 to 7.

The embodiment of the invention provides a multi-way valve, and particularly relates to a novel engineering machinery walking system multi-way valve structure which is universally applicable to the field of engineering machinery and used for realizing bidirectional proportional control of output flow of a three-position four-way walking linkage reversing valve through current.

The multiplex valve includes a first working valve 10, a second working valve 20, and a control valve 30.

The first working valve 10 includes a first valve body 114 and a first valve spool 106 provided inside the first valve body 114. The second working valve 20 includes a second valve body 200 and a second spool 220 provided inside the second valve body 200. The control valve 30 includes a third valve body 316 and a third valve spool 306 disposed within the third valve body 316.

The control valve 30 is in communication with both the first working valve 10 and the second working valve 20 through the in-valve flow passage to control the source of the working oil of the first working valve 10 and/or the second working valve 20. The flow passage in the valve refers to a flow passage positioned in the valve body. As described later, the first valve body 114, the second valve body 200, and the third valve body 316 are integrated. The entire first working valve 10, the entire second working valve 20, and the entire control valve 30 are communicated with each other by opening a flow passage in at least one of the first valve body 114, the second valve body 200, and the third valve body 316, and the first working valve 10, the second working valve 20, and the control valve 30 have no external connection line therebetween, as shown in fig. 2.

The center axis of the first spool 106 of the first working valve 10, the center axis of the second spool 220 of the second working valve 20, and the center axis of the third spool 306 of the control valve 30 are coplanar. The central axes of the first working valve 10, the second working valve 20 and the control valve 30 are coplanar, so that the valve bodies of the three valves can be connected into a whole, the structure of the multi-way valve is reduced, the size is smaller, and the structure of the multi-way valve is more compact.

Referring to fig. 1, a first oil inlet passage P1 corresponding to the first pump 40 and a second oil inlet passage P2 corresponding to the second pump 50 are main oil passages, and PL is a pilot oil passage. Px is the pilot control pressure of the control valve 30.

Specifically, the control valve 30 is connected to both the first working valve 10 and the second working valve 20, and the control valve 30 is used to control the source of the working hydraulic line.

Referring to fig. 1 and 2, the third valve body 316 is located between the first valve body 114 and the second valve body 200.

Referring to fig. 1 and 2, the second valve body 200 is provided with a first oil inlet passage, corresponding to P1, which is respectively communicated with the control valve 30 and the first working fluid port a2 of the second working valve through the valve inner flow passage of the second working valve 20. The third valve body 316 is provided with a second oil inlet path which is communicated with the first working oil port a3 of the control valve.

The multi-way valve is particularly suitable for operating situations in which there are two oil supply pumps, namely the first pump 40 and the second pump 50 are both connected to the multi-way valve. One working condition is as follows: the first pump 40 supplies oil to the second working valve 20 to meet the actuation requirements of the second actuator. The second pump 50 supplies oil to the first working valve 10 to meet the operation requirement of the first actuator. This is the case when the construction machine is performing only walking operations, for example, and no other actions are performed. The other working condition is as follows: the first pump 40 supplies oil to the first working valve 10 and the second working valve 20 at the same time to meet the operation requirements of the first actuator and the second actuator. The second pump 50 supplies oil to other oil-consuming equipment. The working condition is suitable for the engineering machinery to walk and execute other actions such as excavation and the like. The working condition can distinguish the walking oil from other actions by using the oil phase so as to prevent the walking oil and the other actions from influencing each other.

Referring to fig. 1 and 2, in some embodiments, the first working valve 10 includes a first valve body 114, a first spool 106, a first pilot reducing valve 102, a second pilot reducing valve 119, a first elastic connector 105, and a second elastic connector. The first valve body 114 is provided with a first oil hole; the first spool 106 is attached to the first oil hole. Both first pilot pressure reduction valve 102 and second pilot pressure reduction valve 119 are configured as pressure reduction valves. A first elastic connection 105 is provided between the first pilot pressure reduction spool 102a of the first pilot pressure reduction valve 102 and the first spool 106. A second elastic connection is provided between the second pilot pressure reducing spool 119a of the second pilot pressure reducing valve 119 and the first spool 106.

The valve position of the first spool 106 is determined by the first pilot pressure reducing valve 102, the second pilot pressure reducing valve 119, the first elastic connection 105, and the second elastic connection in common. Specifically, in the electrically disabled state, the valve position of the first spool 106 is determined by the first pilot pressure reducing valve 102, the second pilot pressure reducing valve 119, the first elastic connection 105, and the second elastic connection. In some embodiments described later, the position of the first spool 106 is determined by the control currents of the first pilot reducing valve 102, the second pilot reducing valve 119, the first elastic connector 105, the second elastic connector, the first electromagnet 101, and the second electromagnet 122.

Referring to fig. 1 and 2, the first working valve 10 is a three-position four-way reversing valve, and the middle position of the first working valve 10 can be Y-shaped.

When the first working valve 10 is in the middle position, the third working oil port AtL of the first working valve 10 and the fourth working oil port BtL of the first working valve are both communicated with the return oil. When the first working valve 10 is at the left position shown in fig. 1, the first working port a1 of the first working valve 10 is communicated with the fourth working port BtL of the first working valve, and the second working port B1 of the first working valve 10 is communicated with the third working port AtL of the first working valve.

Specifically, when the first spool 106 is in the neutral position, neither the first electromagnet 101 nor the second electromagnet 122 is energized. The output ends of the first pilot pressure reducing valve 102 and the second pilot pressure reducing valve 119, i.e., the cavities in which the first elastic connection 105 and the second spring 123 are located, are both communicated with the pilot pressure PL. The first spool 106 is in a force balanced state. The third working oil port (corresponding to the 109 cavity) of the first working valve and the fourth working oil port BtL (corresponding to the 111 cavity) of the first working valve are communicated with the first oil return cavity 110 at the same time.

Referring to fig. 1 and 2, in some embodiments, the first pilot pressure relief valve 102 includes a first pilot pressure relief spool 102a, a first pilot pressure relief valve body 102b, and a first electromagnet 101. The first pilot pressure reducing valve body 102b is provided with a first pilot pressure reducing valve hole, and the first pilot pressure reducing valve spool 102a is attached to the first pilot pressure reducing valve hole. The first electromagnet 101 is attached to a first end of the first pilot pressure reducing spool 102 a. A first end of the first elastic connection 105 abuts against a second end of the first pilot pressure reduction spool 102a, and a second end of the first elastic connection 105 abuts against a first end of the first spool 106.

The first pilot inlet port 103 is an inlet port of the first pilot pressure reducing valve 102, and the first pilot inlet port 103 communicates with the pilot oil PL and is used to input a constant pilot pressure PL. The first oil return port 104 of the first pilot pressure reducing valve 102 is directly connected to the oil tank. The control pressure output ends of the first pilot pressure reducing valve 102 are connected to the two pilot control ends of the first pilot pressure reducing spool 102a, respectively. A first end of the first spool 106 is in direct contact with the first elastic connection 105 and maintains a certain pre-compression force, and a second end of the first spool 106 is screw-coupled with a first set screw 118. The first valve core 106 and the first positioning screw 118 are sleeved with a first spring seat 116, a first spring 115 and a second spring seat 117 in sequence. The second end of the first set screw 118 is in direct contact with the second spring 123 within the axial bore and maintains a certain pre-compression force.

The first electromagnet 101 is specifically a unidirectional high-voltage-resistant proportional electromagnet. The first electromagnet 101 is fastened to the first pilot pressure reducing valve body 102b, the axis of the first electromagnet 101 coincides with the central axis of the first pilot pressure reducing valve body 102b, and the output rod of the first electromagnet 101 is in direct contact with the first pilot pressure reducing valve spool 102a of the first pilot pressure reducing valve 102.

The first pilot pressure reducing valve 102 employs a two-position three-way spool valve. When the first pilot pressure reducing valve 102 is in the right position shown in fig. 1, the pilot oil PL is delivered to the first and second pilot ends of the first pilot pressure reducing valve 102 and to the first end of the first spool 106 via the right position of the first pilot pressure reducing valve 102. When the first pilot pressure reducing valve 102 is in the left position shown in fig. 1, the pilot oil PL does not flow into the first pilot pressure reducing valve 102. The first and second pilot ends of the first pilot reducing valve 102 and the first end of the first spool 106 are devoid of pilot oil.

The first end of the first pilot pressure reducing spool 102a is also provided with a first electromagnet 101. When the first electromagnet 101 is supplied with current, the first electromagnet 101 tends to push the first pilot pressure reducing spool 102a to move in the direction of the first spool 106. However, since the first pilot pressure reducing valve 102 is a pressure reducing valve, the first spool 106 actually moves in the direction of the first electromagnet 101.

A first resilient connection 105 is provided between the second end of the first pilot pressure reduction spool 102a and the first end of the first spool 106. Specifically, the first elastic coupling 105 is a compression spring, a first end of the first elastic coupling 105 abuts against a second end of the first pilot pressure reducing spool 102a, and a second end of the first elastic coupling 105 abuts against a first end of the first spool 106.

The pilot control component of the second end of the first spool 106 is described below.

Referring to fig. 1 and 2, a second end of the first spool 106 is disposed with a second elastic connection and a second pilot reducing valve 119.

In some embodiments, the second pilot pressure reducing valve 119 includes a second pilot pressure reducing spool 119a, a second pilot pressure reducing valve body 119b, and a second electromagnet 122. The second pilot pressure reducing valve body 119b is provided with a second pilot pressure reducing valve hole, and a second pilot pressure reducing valve spool 119a is attached to the second pilot pressure reducing valve hole. A second electromagnet 122 is mounted to a second end of the second pilot pressure reduction spool 119 a. Wherein the second resilient connection is provided between the first end of the second pilot pressure relief spool 119a and the second end of the first spool 106.

The second pilot input port 121 is an input end of the second pilot pressure reducing valve 119, and the second pilot input port 121 communicates with the pilot oil PL and inputs a constant pilot pressure PL. The second oil return port 120 of the second pilot pressure reducing valve 119 is directly connected to the oil tank.

The second electromagnet 122 is specifically a unidirectional high voltage-resistant proportional electromagnet. The second electromagnet 122 is fastened to the second pilot pressure reducing valve body 119b, the axis of the second electromagnet 122 coincides with the center axis of the second pilot pressure reducing valve body 119b, and the output rod of the second electromagnet 122 directly contacts the second pilot pressure reducing valve body 119a of the second pilot pressure reducing valve 119.

Referring to fig. 1 and 2, in some embodiments, the second elastic connection includes a first spring 115 and a second spring 123. A first end of the first spring 115 abuts against a second end of the first spool 106, and a second end of the first spring 115 abuts against the second pilot pressure reducing valve body 119 b. A first end of the second spring 123 abuts against a second end of the first spool 106, and a second end of the second spring 123 abuts against a first end of the second pilot pressure reduction spool 119 a.

The first valve body 114 and the second pilot pressure reducing valve body 119b are fixedly connected together. The second pilot pressure reducing valve oil hole of the second pilot pressure reducing valve body 119b communicates with the first oil hole of the first valve body 114. A first spring mounting seat 116 and a second spring mounting seat 117 are mounted in the second pilot reducing valve oil hole. The first spring mount 116 abuts the first valve body 114. One end of the second pilot pressure reducing valve body 119b facing the first valve spool 106 is provided with a step, and the second spring mounting seat 117 abuts against the bottom surface of the step of the second pilot pressure reducing valve body 119 b. The first spring 115 is a compression spring, and is interposed between the first spring mount 116 and the second spring mount 117.

Referring to fig. 1 and 2, a second electromagnet 122 is disposed at an outer portion of a side of the second pilot pressure reducing valve oil hole away from the first valve body 114. When the second electromagnet 122 is supplied with current, the second electromagnet 122 tends to urge the second pilot pressure reduction spool 119a to move in the direction of the first spool 106. However, since the second pilot pressure reducing valve 119 is a pressure reducing valve, the first spool 106 actually moves in the direction of the second electromagnet 122.

A first end of the second pilot pressure reduction spool 119a abuts a second end of the second spring 123. A second end of the second pilot pressure reduction spool 119a abuts the second electromagnet 122.

A first set screw 118 is secured to a second end of the first spool 106. A first end of the second spring 123 abuts against the first set screw 118. Specifically, the second end of the first set screw 118 is provided with a groove in which the first end of the second spring 123 is mounted.

In some embodiments, at least one of first pilot pressure relief valve 102 and second pilot pressure relief valve 119 is configured as a two-position, three-way spool.

In some embodiments, the second working valve 20 is configured as a three-position, four-way reversing valve, and the mid-position function of the second working valve 20 can be Y-shaped. The multi-way valve provided by the technical scheme meets the requirement of reversing three working positions of a common execution mechanism, and can realize a special middle-position function.

When second spool 220 is in the neutral position, neither third electromagnet 219 nor fourth electromagnet 202 is energized. The output ends of the third pilot pressure reducing valve 218 and the fourth pilot pressure reducing valve 203 (corresponding to the cavity in which the second elastic connection and the fourth spring 205 are located) are both communicated with the pilot pressure PL. The second spool 220 is in a force balance state. And a third working oil port Atr (corresponding to the 213 cavity) of the second working valve is communicated with the 214 oil return cavity, and a fourth working oil port Btr (corresponding to the 211 cavity) of the second working valve is communicated with the 210 cavity of the second oil return cavity, so that a Y-shaped neutral position function is realized.

The valve position switching process of the first working valve 10 will be described below.

Taking the example of oil supply to the left-traveling-connection first working valve fourth working port BtL cavity, when a proportional current signal is sent to the second electromagnet 122 alone, the output rod of the second electromagnet 122 pushes the second pilot pressure reducing valve spool 119a of the second pilot pressure reducing valve 119 to move left, so that the valve port between the output port (corresponding to the cavity where the fourth spring 205 is located) of the second pilot pressure reducing valve 119 and the second pilot input port 121 is gradually closed. Meanwhile, the flow area between the second pilot input port 121 and the second oil return chamber 120 gradually increases from zero. The pressure in the output chamber of the second pilot pressure reducing valve 119 decreases, and the first spool 106 moves rightward by the left constant pilot pressure PL, and the displacement thereof is converted into a force signal by the second spring 123, and acts on the left side of the second pilot pressure reducing valve 119, canceling the electromagnetic force, and so on until the first spool 106 is balanced at a certain position. The second pilot reducing valve 119 outputs a control pressure between 0 and PL to act on the right end of the first spool 106. This control pressure is balanced with the sum of the spring forces of the first spring 115 and the left pilot pressure PL. Because the stiffness of the second spring 123 is small, the influence of the variation of the elastic force of the second spring 123 on the force balance of the first valve spool 106 in the stroke range of the first valve spool 106 is negligible. Neglecting the weak hydrodynamic force and the friction force applied to the first pilot pressure reducing spool 102a, in the equilibrium state, the output force of the second spring 123 is equal to the output force of the output rod of the second electromagnet 122. During this process, the first pilot pressure relief spool 102a remains stationary and the chamber in which the first resilient connection 105 is located is at a constant pilot pressure.

After the first spool 106 moves rightwards, the oil in the pump 50 flows from the 307 chamber to the 108 chamber through the third spool 306 of the control valve 30, then flows to the 112 chamber through a flow passage (shown by a dotted line) between the 108 chamber and the 112 chamber, and then flows to the fourth working port BtL of the first working valve through the opened valve port. Meanwhile, the 109 chamber (corresponding to the third working port AtL of the first working valve) reaches 110 the oil return chamber after passing through the first valve core 106. The oil chamber 107 and the oil chamber 113 are also oil return chambers, and play a role in balancing the stress of the first valve core 106 and preventing pressure build-up.

When the third working port AtL of the first working valve and the fourth working port BtL of the first working valve generate flow, the steady-state hydraulic force acting on the first valve core 106 will cause the first valve core 106 to move leftward, resulting in a smaller compression amount of the second spring 123 on the right side. At this time, the flow area before the output port (corresponding to the cavity where the second spring 123 is located) and the oil return port of the first pilot pressure reducing valve 102 increases. Thus, the pressure at the output port is reduced to counteract the hydrodynamic interference, and the first spool 106 tends to stabilize in its original position. The above process embodies the function of negative feedback, and the position deviation of the first valve core 106 caused by any external factors is inhibited by the displacement-force feedback function of the second spring 123, so that the position of the second valve core 220 is only related to the magnitude of the proportional electric signal input by the second electromagnet 122, and the load-resisting rigidity of the main valve core can be greatly improved, thereby improving the control performance of the whole machine.

Thanks to the bilateral symmetry design of the pilot

pressure reducing valves

102 and 119, when the electromagnet 101 is electrified, the spool 106 of the left traveling valve deflects leftwards, the P2 leads oil to the third working port AtL of the first working valve, and the fourth working port BtL of the first working valve is connected to the oil tank. This principle of operation is completely consistent with the electromagnet 122 being energized, as follows.

When the left walking link is connected with the third working port AtL of the first working valve for supplying oil, and when a proportional current signal is sent to the first electromagnet 101 alone, the output rod of the first electromagnet 101 pushes the first pilot pressure reducing valve core 102a of the first pilot pressure reducing valve 102 to move rightwards, so that the valve port between the output port (corresponding to the cavity where the first elastic connecting piece 105 is located) of the first pilot pressure reducing valve 102 and the first pilot input port 103 is gradually closed. Meanwhile, the flow area between the first pilot input port 103 and the first oil return chamber 104 gradually increases from zero. The pressure in the output chamber of the first pilot pressure reducing valve 102 decreases, the first spool 106 moves to the left by the constant pilot pressure PL on the right side, and the displacement thereof is converted into a force signal by the first elastic connection member 105 and acts on the right side of the first pilot pressure reducing valve 102, canceling the electromagnetic force until the first spool 106 is balanced at a certain position. The first pilot reducing valve 102 outputs a control pressure between 0 and PL to act on the left end of the first spool 106. This control pressure is in common with the sum of the spring forces of the first elastic connection 105 and the right pilot pressure PL. The above process ignores the weak hydrodynamic and frictional forces experienced by the second pilot pressure relief spool 119 a. In the equilibrium state, the output force of the first elastic coupling member 105 corresponds to the output force of the output rod of the first electromagnet 101. In this process, the second pilot pressure relief spool 119a remains stationary and the chamber in which the second resilient connection is located is at a constant pilot pressure.

After the first spool 106 moves to the left, the oil in the pump 50 flows from the 307 chamber to the 108 chamber through the third spool 306 of the control valve 30, and then flows to the third working port AtL of the first working valve through the opened valve port. Meanwhile, the 111 chamber (corresponding to the fourth working port BtL of the first working valve) reaches the first oil return chamber 110 after passing through the first valve core 106. The description is too repetitive.

When the third working port AtL of the first working valve and the fourth working port BtL of the first working valve generate flow, the steady-state hydrodynamic force acting on the first valve spool 106 will cause the first valve spool 106 to move rightwards, resulting in a smaller compression amount of the first elastic connection member 105 on the left side. At this time, the flow area before the output port (corresponding to the cavity where the first elastic coupling 105 is located) and the oil return port of the first pilot pressure reducing valve 102 increases. Thus, the pressure at the output port is reduced to counteract the hydrodynamic interference, and the first spool 106 tends to stabilize in its original position. The above process embodies the function of negative feedback, and the position deviation of the first valve core 106 caused by any external factors is inhibited by the displacement-force feedback function of the first elastic connecting piece 105, so that the position of the second valve core 220 is only related to the magnitude of the proportional electric signal input by the second electromagnet 122, and the load-resisting rigidity of the main valve core can be greatly improved, thereby improving the control performance of the whole machine.

A specific implementation of the second working valve 20 will be described below.

In some embodiments, the second working valve 20 includes a second valve body 200, a second spool 220, a third pilot relief valve 218, a fourth pilot relief valve 203, a third resilient connection 215, and a fourth resilient connection.

The second valve body 200 is provided with a second oil hole; the second valve spool 220 is mounted to the second oil hole. Third pilot pressure relief valve 218 is configured as a pressure relief valve. The fourth pilot pressure reducing valve 203 is configured as a pressure reducing valve. A third elastic connection 215 is provided between the third pilot pressure reducing spool 218a of the third pilot pressure reducing valve 218 and the second spool 220. A fourth elastic connection is provided between the fourth pilot pressure reducing spool 203a of the fourth pilot pressure reducing valve 203 and the second spool 220.

The third pilot input port 217 is an input end of the third pilot pressure reducing valve 218, and the third pilot input port 217 communicates with the pilot oil PL for inputting the constant pilot pressure PL. The third oil return port of the third pilot pressure reducing valve 218 is directly connected to the oil tank.

The valve position of the second spool 220 is determined by the third pilot pressure reducing valve 218, the fourth pilot pressure reducing valve 203, the third elastic connection 215, and the fourth elastic connection in common. Specifically, in the electrically disabled state, the valve position of the second spool 220 is determined by the third pilot pressure reducing valve 218, the fourth pilot pressure reducing valve 203, the third elastic connection 215, and the fourth elastic connection.

The central axis of the second working valve 20 is parallel to the central axis of the first working valve 10, and the first valve body 114, the second valve body 200, and a third valve body 316 described later are integrated.

Referring to fig. 1 and 2, the first and second working

valves

10 and 20 are arranged in a substantially identical manner, so that the arrangement can simplify the structure of the multiplex valve.

Referring to fig. 1 and 2, the second working valve 20 is a three-position four-way reversing valve, and the middle position of the second working valve 20 can be Y-shaped. When the second working valve 20 is in the neutral position, both the third working port Atr and the fourth working port Btr of the second working valve 20 are communicated with the return oil. When the second working valve 20 is at the left position as shown in fig. 1, the first working port a2 of the second working valve 20 is communicated with the fourth working port Btr, and the second working port B2 of the second working valve 20 is communicated with the third working port Atr of the second working valve.

Referring to fig. 1 and 2, in some embodiments, third pilot pressure relief valve 218 includes a third pilot pressure relief spool 218a, a third pilot pressure relief valve body 218b, and a third electromagnet 219. The third pilot pressure reducing valve body 218b is provided with a third pilot pressure reducing valve hole, and the third pilot pressure reducing valve spool 218a is attached to the third pilot pressure reducing valve hole. A third electromagnet 219 is mounted to a first end of the third pilot pressure reduction spool 218 a.

A second end of the third pilot reducing valve 218 and the third elastic connection 215 directly contact and maintain a certain pre-compression force, and a second end of the second spool 220 is screw-coupled with the second set screw 207. The third spring seat 209, the third spring 208 and the fourth spring seat 206 are sleeved between the second valve spool 220 and the second positioning screw 207 respectively and sequentially. The second end of the second set screw 207 is in direct contact with and maintains a certain pre-compression force in the axial hole of the fourth spring 205, respectively.

The third electromagnet 219 is a unidirectional high-voltage-resistant proportional electromagnet. The third electromagnet 219 is fastened to the third pilot pressure reducing valve body 218b, the axis of the third electromagnet 219 coincides with the center axis of the third pilot pressure reducing valve body 218b, and the output rod of the third electromagnet 219 directly contacts the third pilot pressure reducing valve spool 218a of the third pilot pressure reducing valve body 218.

The third pilot pressure relief valve 218 employs a two-position three-way spool valve. When the third pilot pressure reducing valve 218 is in the right position shown in fig. 1, the pilot oil PL is delivered to the first and second pilot ends of the third pilot pressure reducing valve 218 and to the first end of the second spool 220 via the right position of the third pilot pressure reducing valve 218. When the third pilot reducing valve 218 is in the left position shown in fig. 1, the pilot oil PL does not flow into the third pilot reducing valve 218, and the first and second pilot ends of the third pilot reducing valve 218 and the first end of the second spool 220 are free of pilot oil.

A third electromagnet 219 is also provided at the first end of the third pilot pressure reduction spool 218 a. When the third electromagnet 219 is supplied with current, the third electromagnet 219 pushes the third pilot pressure reduction spool 218a to move in the direction of the second spool 220.

A third resilient connection 215 is provided between a second end of the third pilot pressure reduction spool 218a and a first end of the second spool 220. Specifically, the third elastic connection member 215 is a compression spring, a first end of the third elastic connection member 215 abuts against a second end of the third pilot pressure reducing spool 218a, and a second end of the third elastic connection member 215 abuts against a first end of the first spool 106.

Referring to fig. 1 and 2, in some embodiments, fourth pilot pressure relief valve 203 includes a fourth pilot pressure relief spool 203a, a fourth pilot pressure relief valve body 203b, and a fourth electromagnet 202. The fourth electromagnet 202 is specifically a unidirectional high voltage-resistant proportional electromagnet.

The fourth pilot pressure reducing valve body 203b is provided with a fourth pilot pressure reducing valve oil passage, and a fourth pilot pressure reducing spool 203a is attached to the fourth pilot pressure reducing valve oil passage. The fourth pilot input port 201 is an input end of the fourth pilot pressure reducing valve 203, and the fourth pilot input port 201 communicates with the pilot oil PL and inputs a constant pilot pressure PL. The fourth oil return port 204 of the fourth pilot pressure reducing valve 203 is directly connected to the oil tank.

Fourth electromagnet 202 is attached to a second end of fourth pilot pressure reduction spool 203 a. The fourth electromagnet 202 is fastened to the fourth pilot pressure reducing valve body 203b, the axis of the fourth electromagnet 202 coincides with the center axis of the fourth pilot pressure reducing valve body 203b, and the output rod of the fourth electromagnet 202 is in direct contact with the fourth pilot pressure reducing spool 203a of the fourth pilot pressure reducing valve 203.

The fourth resilient connection comprises a third spring 208 and a fourth spring 205. The second valve body 200 and the fourth pilot pressure reducing valve 203 are fixedly connected together. The fourth pilot pressure-reducing valve oil passage of the fourth pilot pressure-reducing valve body 203b communicates with the second oil hole of the second valve body 200. A third spring mounting seat 209 and a fourth spring mounting seat 206 are mounted in the fourth pilot reducing valve oil passage. The third spring mount 209 abuts against the second valve body 200. One end of the fourth pilot pressure-reducing valve body 203b facing the second spool 220 is provided with a step, and the fourth spring mount 206 abuts against a bottom surface of the step of the fourth pilot pressure-reducing valve body 203 b. The third spring 208 is a compression spring and is sandwiched between the third spring mount 209 and the fourth spring mount 206. The fourth spring 205 is a feedback spring.

Referring to fig. 1 and 2, a fourth electromagnet 202 is disposed outside a side of the fourth pilot pressure reducing valve oil passage remote from the first valve body 114. When the fourth electromagnet 202 is supplied with current, the fourth electromagnet 202 tends to push the fourth pilot pressure reduction spool 203a to move toward the second spool 220. However, since fourth pilot reducing valve 203 is a reducing valve, second spool 220 actually moves in the direction of fourth electromagnet 202.

In some embodiments, the fourth resilient connection comprises a third spring 208 and a fourth spring 205.

A first end of the third spring 208 abuts against a second end of the second spool 220, and a second end of the third spring 208 abuts against the fourth pilot pressure reduction valve body 203 b.

A first end of the fourth spring 205 abuts against a second end of the second spool 220 and a second end of the fourth spring 205 abuts against a first end of the fourth pilot pressure reduction spool 203 a. The fourth spring 205 is a feedback spring.

A first end of the fourth pilot pressure reduction spool 203a abuts a second end of the fourth spring 205. A second end of fourth pilot pressure reduction spool 203a abuts fourth electromagnet 202.

A second set screw 207 is fixed to a second end of the second spool 220. The third spring seat 209 and the fourth spring seat 206 abut against both ends of the second set screw 207 under the biasing force of the third spring 208. The second end of the second set screw 207 is provided with a recess in which the first end of the fourth spring 205 is mounted.

In some embodiments, at least one of third pilot relief valve 218 and fourth pilot relief valve 203 is configured as a two-position, three-way spool valve.

According to the technical scheme, the frequency response speed meeting the engineering application requirements and certain load resisting rigidity are achieved, the dynamic interference of the steady-state liquid can be restrained, and accurate control is achieved.

In some embodiments, the control valve 30 is configured as a two-position, four-way reversing valve.

Referring to fig. 1 and 2, the central axes of the first valve spool 106, the second valve spool 220, and the third valve spool 306 are sequentially arranged on a plane, the first pilot end cap 302 of the control valve 30 is fixed to one end of the third valve body, and the first end of the third valve spool 306 of the control valve 30 is sequentially inserted into the straight oil-supplying one-way valve spool 305, the straight oil-supplying one-way valve spring 304, and the straight oil-supplying one-way valve plug 303, and the bolts are tightened. The second end of the third valve core 306 of the control valve 30 is sequentially placed into the lower spring seat 309 of the main valve core of the control valve, the main spring 310 of the control valve, the limit stop iron 311 of the main spring of the control valve and the upper spring seat 313 of the main valve of the control valve, and finally the positioning screw 312 of the spring of the control valve is screwed on, and the second pilot end cover 314 of the control valve 30 is installed on the third valve body in a bolt fastening mode, and the end cover plug 315 of the control valve 30 is plugged at the tail end of the second pilot end cover 314.

Referring to fig. 1 and 2, the control valve 30 is located between the first and second working

valves

10 and 20, which facilitates setting the communication relationship of the control valve 30 with the first and second working

valves

10 and 20. The central axis of the control valve 30 is parallel to the central axis of the first spool 106 and the central axis of the second spool 220 of the second working valve 20, and the central axes of the three valves are coplanar. This arrangement simplifies the structure and communication of the multiple-way valve. Moreover, the manufacturing process is good, the processing cost is low, the reliability is high, the layout is reasonable, the structure is compact, the occupied space is small, the structural design requirement of the whole machine is met, and the profit maximization of enterprises is realized.

When the right traveling valve works alone, the P1 pump fluid enters the second spool 220 from the 212 chamber, when the fourth solenoid 202 sends a command signal, the second spool 220 moves to the right, the fluid in the P1 port (corresponding to the 212 chamber) flows into the Atr port (corresponding to the 213 chamber), and the fluid in the fourth working fluid port Btr (corresponding to the 211 chamber) of the second working valve flows into the second return chamber 210. When the third electromagnet 219 sends a command signal, the second spool 220 moves to the left, the oil in the port P1 (corresponding to the chamber 212) flows into the fourth working port Btr (corresponding to the chamber 211) of the second working valve, and the oil in the third working port Atr (corresponding to the chamber 213) of the second working valve flows into the third oil return chamber 214. The cavity 221 is located in the middle of the valve core hole of the right walking valve and used for achieving other valve body functions.

Taking the example of oil supply from the third working port Atr of the right-hand travel-coupled second working valve, when a proportional current signal is sent to the fourth electromagnet 202 alone, the output rod of the fourth electromagnet 202 pushes the fourth pilot pressure reducing valve spool 203a of the fourth pilot pressure reducing valve 203 to move to the left, so that the valve port between the output port (corresponding to the cavity where the fourth spring 205 is located) of the fourth pilot pressure reducing valve 203 and the fourth input port 201 is gradually closed. Meanwhile, the flow area between the fourth input port 201 and the fourth oil return chamber 204 gradually increases from zero. The pressure in the output chamber thereof is decreased, the second spool 220 is shifted to the right by the left constant pilot pressure PL, the displacement thereof is converted into a force signal by the fourth spring 205, and the force signal is applied to the left side of the fourth pilot pressure reducing spool 203a, and the force signal is cancelled by the electromagnetic force of the fourth electromagnet 202 until the second spool 220 is balanced at a certain position. The fourth pilot reducing valve 203 outputs a control pressure between 0 and PL to act on the right end of the second spool 220.

Therefore, this control pressure plus the spring force of the third spring 208 and the pilot pressure PL on the left side are balanced, and since the stiffness of the fourth spring 205 is small, the amount of change in the spring force of the fourth spring 205 has a negligible effect on the force balance of the second spool 220 in the stroke range of the second spool 220. Neglecting the weak hydrodynamic and frictional forces experienced by the third pilot pressure relief spool 218a, the output force of the fourth spring 205 is equal to the output force of the output rod of the fourth electromagnet 202 in the equilibrium state. During this process, the left third pilot pressure relief spool 218a remains stationary and the chamber in which the left second elastomeric connector is located is at a constant pilot pressure.

After the second valve spool 220 moves rightwards, the oil of the pump source P1 flows to the third working port Atr of the second working valve through the opened valve port, and meanwhile, the 211 chamber (corresponding to the fourth working port Btr of the second working valve) reaches the second oil return chamber 210 after passing through the second valve spool 220.

When the third working oil port Atr of the second working valve and the fourth working oil port Btr of the second working valve generate flow, the steady-state hydraulic force acting on the second valve spool 220 will make the valve spool move leftward, resulting in the reduction of the compression amount of the fourth spring 205 on the right side, at this time, the flow area before the output port (corresponding to the cavity where the fourth spring 205 is located) and the oil return port of the fourth pilot reducing valve 203 will increase, so the pressure at the output end decreases, the interference effect of the hydraulic force is counteracted, and the second valve spool 220 tends to be stabilized at the original position. The process is embodied by the action of negative feedback, and the position deviation of the second valve core 220 caused by any external factors is inhibited by the displacement-force feedback action of the feedback spring, so that the position of the second valve core 220 is only related to the magnitude of a proportional electric signal input by the electromagnet 202, the load-resisting rigidity of the main valve core can be greatly improved, and the control performance of the whole machine is improved.

When oil is supplied to the cavity of the left walking link Btr, a proportional current signal is sent to the third electromagnet 219 alone, and the output rod of the third electromagnet 219 pushes the third pilot pressure reducing valve spool 218a of the third pilot pressure reducing valve 218 to move rightward, so that the valve port between the output port (corresponding to the cavity where the second elastic connecting piece is located) of the third pilot pressure reducing valve 218 and the third pilot input port 217 is gradually closed. At the same time, the flow area between the third pilot input port 217 and the third return chamber 216 gradually increases from zero. The pressure in the output chamber of the third pilot pressure reducing valve 218 is continuously reduced, the second spool 220 is moved to the left by the constant pilot pressure PL on the right side, and the displacement thereof is converted into a force signal by the second elastic connection member to act on the right side of the third pilot pressure reducing spool 218a, and the force signal is cancelled by the electromagnetic force until the second spool 220 is balanced at a certain position.

The third pilot reducing valve 218 outputs a control pressure between 0 and PL to act on the left end of the second spool 220. This control pressure together with the sum of the spring forces of the second elastic connection is balanced with the right pilot pressure PL. The above process ignores the weak hydrodynamic and frictional forces experienced by the third pilot pressure relief spool 203 a. In the equilibrium state, the output force of the third resilient connecting element 215 is equal to the output force of the output rod of the third electromagnet 219. In this process, the fourth pilot pressure relief spool 203a remains stationary and the chamber in which the fourth resilient connection is located is at a constant pilot pressure.

After the second spool 220 moves to the left, the oil of the pump P1 flows to the fourth working port Btr of the second working valve through the opened valve port. Meanwhile, the chamber 213 (corresponding to the third working port Atr of the second working valve) reaches the first oil return chamber 214 after passing through the second valve core 220.

When the third working port Atr of the second working valve and the fourth working port Btr of the second working valve generate flow, the steady hydraulic force acting on the second spool 220 causes the second spool 220 to move rightwards, resulting in a smaller compression amount of the third elastic connection member 215. At this time, the flow area before the output port (corresponding to the cavity where the third elastic connection 215 is located) and the oil return port of the third pilot pressure reducing valve 218 increases. Thus, the pressure at the output port is reduced to counteract the hydrodynamic interference, and the second spool 220 tends to stabilize in its original position. The above process embodies the function of negative feedback, and the position deviation of the second valve core 220 caused by any external factors is inhibited by the displacement-force feedback function of the third elastic connecting piece 215, so that the position of the second valve core 220 is only related to the magnitude of the proportional electric signal input by the second electromagnet 219, and the load-resisting rigidity of the main valve core can be greatly improved, thereby improving the control performance of the whole machine.

When the left and right travel valves are simultaneously operated and there is another actuator operation, the control valve 30 is activated, and the Px pilot pressure is applied to the 301 chamber to move the third spool 306 of the control valve 30 to the right end (straight travel state). At this point, 212 and 308 chambers are isolated and at the

same time

212 and 112 chambers are connected. Thereby realizing that the P1 pump supplies oil to the left traveling valve (i.e., the first working valve 10). The 307 cavity and the 108 cavity are isolated, and the 307 cavity and the 308 cavity are communicated, so that the purpose of supplying oil to other actuators by the P2 pump is realized. Meanwhile, if the flow required by other actuators is small, the redundant flow can be supplied to the walking linkage through the one-way valve in the control valve 30 core.

According to the technical scheme, the pilot feedback control structure symmetrically arranged on two sides is adopted, and the limiting spring is used for realizing the middle position positioning. When each valve core is in the middle position, the pilot control flow and the proportional electromagnet current are not consumed. Therefore, hydraulic energy and electric energy can be saved, and the installed power of a system pilot stage driving pump, the load of a main controller and the energy consumption of the whole machine are reduced. When the walking valve group is operated, the built-in pilot control structure of the displacement-force feedback structure can realize closed-loop control on the displacement of the main valve core, and has strong inhibition capability on the hydraulic force change caused by load flow fluctuation, thereby realizing accurate control on the walking speed of the motor and greatly improving the overall machine control experience.

Other embodiments of the present invention provide a hydraulic system including a first actuator (not shown), a second actuator (not shown), a multiplex valve, a first pump 40, and a second pump 50.

The first actuator is, for example, a left-hand wheel. The second actuator is, for example, a right road wheel. The specific structure of the multi-way valve is described above, and is not described herein again.

Referring to fig. 1 and 2, an oil outlet of the first pump 40 is communicated with a first working oil port a2 of the second working valve, a second working oil port B2 of the second working valve is communicated with return oil, and a third working oil port Atr of the second working valve and a fourth working oil port Btr of the second working valve are communicated with the second actuator.

Referring to fig. 1 and 2, an oil outlet of the second pump 50 is communicated with a first working oil port A3 of the control valve, a second working oil port B3 of the control valve is communicated with a first working oil port a2 of the second working valve, a third working oil port of the control valve is communicated with the first working oil port of the first working valve, and a fourth working oil port of the control valve is communicated with an oil supplementing oil path.

Still other embodiments of the present invention provide a construction machine including the hydraulic system according to any of the aspects of the present invention.

In the description of the present invention, it is to be understood that the terms "central", "longitudinal", "lateral", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are used only for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be considered as limiting the scope of the present invention.

Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: it is to be understood that modifications may be made to the technical solutions described in the foregoing embodiments, or equivalents may be substituted for some of the technical features thereof, but such modifications or substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A multiple-way valve, comprising:

a first working valve (10) including a first valve body (114) and a first valve spool (106) provided inside the first valve body (114);

the second working valve (20) comprises a second valve body (200) and a second valve core (220) arranged in the second valve body (200); and

a control valve (30) comprising a third valve body (316) and a third valve spool (306) disposed within the third valve body (316); the control valve (30) is communicated with the first working valve (10) and the second working valve (20) through valve inner flow passages so as to control a working oil source of the first working valve (10) and/or the second working valve (20);

wherein a central axis of the first valve spool (106), a central axis of the second valve spool (220), and a central axis of the third valve spool (306) are coplanar; the first valve body (114), the second valve body (200), and the third valve body (316) are unitary, and the third valve body (316) is located between the first valve body (114) and the second valve body (200).

2. The multiple-way valve according to claim 1, characterized in that the first working valve (10) further comprises:

a first pilot pressure reducing valve (102) configured as a pressure reducing valve;

a second pilot pressure reducing valve (119) configured as a pressure reducing valve;

a first elastic connection (105) provided between a first pilot pressure reduction spool (102a) of the first pilot pressure reduction valve (102) and the first spool (106); and

and a second elastic connection member provided between the first spool (106) and a second pilot pressure reducing spool (119a) of the second pilot pressure reducing valve (119).

3. The multiplex valve as recited in claim 2, wherein the first pilot pressure relief valve (102) comprises:

a first pilot pressure reducing valve body (102b) provided with a first pilot pressure reducing valve oil hole to which the first pilot pressure reducing valve spool (102a) is attached; and

a first electromagnet (101) attached to a first end of the first pilot pressure reducing spool (102 a);

wherein a first end of the first resilient connection (105) abuts a second end of the first pilot pressure relief spool (102a), and a second end of the first resilient connection (105) abuts a first end of the first spool (106).

4. The multiplex valve as recited in claim 2, wherein the second pilot pressure reducing valve (119) comprises:

a second pilot pressure reducing valve body (119b) provided with a second pilot pressure reducing valve hole, the second pilot pressure reducing valve spool (119a) being mounted to the second pilot pressure reducing valve hole; and

a second electromagnet (122) attached to a second end of the second pilot pressure reduction spool (119 a);

wherein the second resilient connection is disposed between a first end of the second pilot pressure relief spool (119a) and a second end of the first spool (106).

5. The multiplex valve of claim 4 wherein said second resilient coupling comprises:

a first spring (115) having a first end abutting against a second end of the first spool (106) and a second end abutting against the second pilot pressure reduction valve body (119 b); and

and a second spring (123), a first end of which abuts against a second end of the first valve core (106), and a second end of which abuts against a first end of the second pilot pressure reduction valve core (119 a).

6. The multiple-way valve according to claim 2, characterized in that at least one of the first pilot pressure reduction valve (102) and the second pilot pressure reduction valve (119) is configured as a two-position three-way spool.

7. The multiple-way valve according to claim 2, characterized in that the second working valve (20) is configured as a three-position, four-way reversing valve and the neutral position of the second working valve (20) can be Y-shaped.

8. The multiple-way valve according to claim 1, characterized in that the second working valve (20) further comprises:

a third pilot relief valve (218) configured as a relief valve;

a fourth pilot pressure reducing valve (203) configured as a pressure reducing valve;

a third elastic connection (215) provided between a third pilot pressure reducing spool (218a) of the third pilot pressure reducing valve (218) and the second spool (220); and

and a fourth elastic connection member provided between the second spool (220) and a fourth pilot pressure reducing spool (203a) of the fourth pilot pressure reducing valve (203).

9. The multiplex valve as recited in claim 8, wherein the third pilot relief valve (218) includes:

a third pilot pressure reducing valve body (218b) provided with a third pilot pressure reducing valve hole, to which the third pilot pressure reducing valve spool (218a) is attached; and

a third electromagnet (219) attached to a first end of the third pilot pressure reducing spool (218 a);

wherein a first end of the third resilient connection (215) abuts a second end of the third pilot pressure relief spool (218a), and a second end of the third resilient connection (215) abuts a first end of the second spool (220).

10. The multiplex valve as recited in claim 8, wherein the fourth pilot pressure reducing valve (203) comprises:

a fourth pilot pressure reducing valve body (203b) provided with a fourth pilot pressure reducing valve oil passage, and a fourth pilot pressure reducing valve spool (203a) mounted on the fourth pilot pressure reducing valve oil passage; and

and a fourth electromagnet (202) mounted to a second end of the fourth pilot pressure reduction spool (203 a).

11. The multiplex valve as defined in claim 10 wherein, said fourth resilient connection comprises:

a third spring (208) having a first end abutting against a second end of the second spool (220) and a second end abutting against the fourth pilot pressure reduction valve body (203 b); and

and a fourth spring (205), the first end of which abuts against the second end of the second valve core (220), and the second end of which abuts against the first end of the fourth pilot pressure reduction valve core (203 a).

12. The multiple-way valve according to claim 1, characterized in that the first working valve (10) is configured as a three-position, four-way reversing valve and the neutral position of the first working valve (10) can be Y-shaped.

13. The multiple-way valve according to claim 1, characterized in that the control valve (30) is configured as a two-position four-way reversing valve.

14. The multiplex valve of claim 1, wherein the axial centerlines of the third valve body (316), the first valve body (114), and the second valve body (200) are parallel.

15. The multiple-way valve according to claim 14, characterized in that the second valve body (200) is provided with a first oil inlet passage which is communicated with the control valve (30) and the second working valve first working oil port a2 through the valve inner flow passage of the second working valve (20); and the third valve body is provided with a second oil inlet path which is communicated with a first working oil port A3 of the control valve.

16. A hydraulic system, comprising:

a first actuator;

a second actuator;

the multi-way valve of any one of claims 1 to 15;

the oil outlet of the first pump (40) is communicated with a first working oil port A2 of the second working valve, a second working oil port B2 of the second working valve is communicated with return oil, and a third working oil port Atr of the second working valve and a fourth working oil port Btr of the second working valve are communicated with the second actuator; and

the oil outlet of the second pump (50) is communicated with a first working oil port A3 of the control valve, a second working oil port B3 of the control valve is communicated with a first working oil port A2 of the second working valve, a third working oil port of the control valve is communicated with a first working oil port A1 of the first working valve, and a fourth working oil port of the control valve is communicated with an oil supplementing oil way.

17. A work machine comprising the hydraulic system of claim 16.