CN115978027A - Engineering machinery hydraulic multi-way reversing valve - Google Patents
Engineering machinery hydraulic multi-way reversing valve Download PDFInfo
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- CN115978027A CN115978027A CN202211605085.7A CN202211605085A CN115978027A CN 115978027 A CN115978027 A CN 115978027A CN 202211605085 A CN202211605085 A CN 202211605085A CN 115978027 A CN115978027 A CN 115978027A
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Abstract
The invention belongs to the technical field of hydraulic multi-way reversing valves, and discloses a hydraulic multi-way reversing valve for engineering machinery. The engineering machinery hydraulic multi-way reversing valve comprises a first main valve, a second main valve and a control valve, wherein the first main valve and the second main valve are three-position eight-way reversing valves with a middle position function, a right position function and a left position function, and the control valve is a two-position two-way reversing valve and is provided with a normal position and a control position. The hydraulic multi-way reversing valve for the engineering machinery can enable the oil return oil path of the oil cylinder with smaller load to generate back pressure, so that the load difference of the two oil cylinders is reduced, and the two oil cylinders can be accurately controlled to work simultaneously.
Description
Technical Field
The invention relates to the technical field of hydraulic multi-way reversing valves, in particular to a hydraulic multi-way reversing valve for engineering machinery.
Background
With the social development and progress, the urban construction is rapidly advanced, the use amount of engineering machinery is greatly increased, and the requirements on the performance of the existing engineering machinery are higher.
In the prior art, a forklift generally uses two oil cylinders including a boom oil cylinder and a bucket oil cylinder to control the operation of a bucket, and a hydraulic oil path control system on the forklift generally uses a multi-way directional valve to control the extension and retraction of the two oil cylinders, so that when the two oil cylinders extend out and retract simultaneously, the running speeds of the two oil cylinders can be accurately controlled due to the fact that loads are basically the same; when one oil cylinder is controlled to extend out and the other oil cylinder is controlled to contract simultaneously, because the load difference of the two oil cylinders is large, the working pressure of the oil cylinder with large load is large, the flow of the hydraulic oil flowing in is small, the running speed of the oil cylinder is slow, the flow of the hydraulic oil flowing in is large due to the small working pressure of the oil cylinder with small load, the running speed of the oil cylinder is fast, the speed of the two oil cylinders is difficult to control, and the operation difficulty of an operator is increased.
In order to solve the above problems in the prior art, a load pressure compensator is generally added to each reversing link of a multi-way reversing valve, and the load pressure compensator has a complex structure, high machining precision and high cost.
Disclosure of Invention
In view of the above problems, the present invention discloses a hydraulic multi-way directional control valve for engineering machinery, which overcomes or at least partially solves the above problems.
The engineering machinery hydraulic multi-way reversing valve comprises a first main valve, a second main valve and a control valve;
the first valve port of the first main valve and the second valve port of the first main valve are both communicated with the oil inlet, the third valve port of the first main valve is communicated with the first valve port of the control valve, the fourth valve port of the first main valve is communicated with the oil return port, the fifth valve port of the first main valve is communicated with the control cavity of the control valve through a first damper, the sixth valve port of the first main valve is communicated with the first working port, the seventh valve port of the first main valve is communicated with the second valve port of the second main valve, and the eighth valve port of the first main valve is communicated with the second working port;
when the first main valve is in a neutral position function, the first valve port of the first main valve, the third valve port of the first main valve, the fourth valve port of the first main valve, the fifth valve port of the first main valve, the sixth valve port of the first main valve and the eighth valve port of the first main valve are all in a blocking state, and the second valve port of the first main valve and the seventh valve port of the first main valve are in a communication state;
when the first main valve is in a right-position function, the second port of the first main valve, the fourth port of the first main valve, the fifth port of the first main valve and the seventh port of the first main valve are all in a blocking state, the first port of the first main valve is communicated with the eighth port of the first main valve, and the third port of the first main valve is communicated with the sixth port of the first main valve;
when the first main valve is in a left-position function, the second port of the first main valve, the third port of the first main valve and the seventh port of the first main valve are all in a blocking state, the first port of the first main valve is simultaneously communicated with the fifth port of the first main valve and the sixth port of the first main valve, and the fourth port of the first main valve is communicated with the eighth port of the first main valve;
the first valve port of the second main valve is communicated with the oil inlet, the third valve port of the second main valve is communicated with the first valve port of the control valve, the fourth valve port of the second main valve is communicated with the oil return port, the fifth valve port of the second main valve is communicated with the control cavity of the control valve through a second damper, the sixth valve port of the second main valve is communicated with the third working port, the seventh valve port of the second main valve is communicated with the oil return port, and the eighth valve port of the second main valve is communicated with the fourth working port;
when the second main valve is in a neutral position function, the first valve port of the second main valve, the third valve port of the second main valve, the fourth valve port of the second main valve, the fifth valve port of the second main valve, the sixth valve port of the second main valve, and the eighth valve port of the second main valve are all in a blocking state, and the second valve port of the second main valve and the seventh valve port of the second main valve are in a communication state;
when the second main valve is in a right-position function, the second port of the second main valve, the fourth port of the second main valve, the fifth port of the second main valve and the seventh port of the second main valve are all in a blocking state, the first port of the second main valve is communicated with the eighth port of the second main valve, and the third port of the second main valve is communicated with the sixth port of the second main valve;
when the second main valve is in a left-position function, the second port of the second main valve, the third port of the second main valve and the seventh port of the second main valve are all in a blocking state, the first port of the second main valve is simultaneously communicated with the fifth port of the second main valve and the sixth port of the second main valve, and the fourth port of the second main valve is communicated with the eighth port of the second main valve;
a second valve port of the control valve is communicated with the oil return port, and a control cavity of the control valve is communicated with the oil return port through a third damper;
when the control valve is in a normal state, the first valve port of the control valve is directly communicated with the second valve port of the control valve; when oil in a control cavity in the control valve drives the control valve to be switched to a control position, the first valve port of the control valve is in throttling communication with the second valve port of the control valve.
Preferably, the engineering machinery hydraulic multi-way reversing valve is also provided with a first one-way valve; the first check valve is positioned between the first valve port of the first main valve and the oil inlet, so that oil flows to the first valve port of the first main valve in a one-way mode.
Preferably, the engineering machinery hydraulic multi-way reversing valve is also provided with a second one-way valve; the second one-way valve is positioned between the first valve port of the second main valve and the oil inlet, so that the oil flows to the first valve port of the second main valve in a one-way mode.
Preferably, the first main valve is a manual control valve.
Preferably, one end of the first main valve is provided with a handle, and the other end of the first main valve is provided with a first main valve spring.
Preferably, the second main valve is a manual control valve.
Preferably, one end of the second main valve is provided with a handle, and the other end of the second main valve is provided with a second main valve spring.
Preferably, the control valve is provided with a control spring to drive the control valve in a normal position.
Preferably, the control spring is a pressure adjustable spring.
Preferably, the first main valve, the second main valve and the control valve share a valve body.
The hydraulic multi-way reversing valve for the engineering machinery has the following beneficial technical effects:
1. in the invention, two three-position eight-way main valves and a two-position two-way control valve are arranged, the two main valves are respectively in control connection with the two oil cylinders, and the control valve can selectively control the back pressure of the oil return passages of the two main valves, so that when one oil cylinder has a larger load and the other oil cylinder has a smaller load, the oil return passages of the oil cylinders with smaller loads can generate back pressure by controlling the control valve to be switched to a throttling working position, thereby reducing the difference between the loads of the two oil cylinders and achieving the accurate control of the simultaneous working of the two oil cylinders.
2. In the invention, only one control valve is arranged to replace two load pressure compensators in the prior art, so that the structure is simpler, the flow channel of the valve body of the multi-way reversing valve is simplified, the casting cost and the processing cost of the valve body are reduced, and the use cost is reduced.
Drawings
FIG. 1 is a schematic diagram of a hydraulic multi-way directional valve of a construction machine according to the embodiment;
FIG. 2 is a schematic diagram of a system of the present embodiment of the hydraulic multi-way directional control valve of the construction machinery;
FIG. 3 is a schematic diagram of a system for controlling the extending of a boom cylinder and the retracting of a bucket cylinder by the hydraulic multi-way directional valve of the construction machinery according to the embodiment;
fig. 4 is a schematic diagram of a system for controlling retraction of a boom cylinder and extension of a bucket cylinder by the hydraulic multi-way directional valve of the construction machine according to the embodiment.
Detailed Description
The technical solution of the present invention will be further described in detail with reference to the accompanying drawings and embodiments.
Referring to fig. 1 to 4, the hydraulic multi-way directional control valve for construction machinery in the present embodiment includes a first main valve 1, a second main valve 2, and a control valve 3 in the same valve body. Wherein, the first main valve 1 and the second main valve 2 are both three-position eight-way reversing valves, and respectively have a middle-position function, a right-position function and a left-position function. The control valve 3 is a two-position two-way reversing valve and is provided with a normal position and a control position. The valve body is provided with an oil inlet 41 communicated with external pressure oil, an oil return port 42 communicated with an external oil tank, and a first working port 51, a second working port 52, a third working port 53 and a fourth working port 54 communicated with an external control element.
The first port 11 and the second port 12 of the first main valve are both communicated with the oil inlet 41, the third port 13 of the first main valve is communicated with the first port 31 of the control valve, the fourth port 14 of the first main valve is communicated with the oil return port 42, the fifth port 15 of the first main valve is communicated with the control chamber 33 of the control valve through a first damper 61, the sixth port 16 of the first main valve is communicated with the first working port 51, the seventh port 17 of the first main valve is communicated with the second port 22 of the second main valve, and the eighth port 18 of the first main valve is communicated with the second working port 52.
When the first main valve 1 is in the neutral position function, the first port 11 of the first main valve, the third port 13 of the first main valve, the fourth port 14 of the first main valve, the fifth port 15 of the first main valve, the sixth port 16 of the first main valve, and the eighth port 18 of the first main valve are all in the blocked state, and the second port 12 of the first main valve and the seventh port 17 of the first main valve are in the connected state.
When the first main valve 1 is in the right position function, the second port 12 of the first main valve, the fourth port 14 of the first main valve, the fifth port 15 of the first main valve and the seventh port 17 of the first main valve are all in a blocked state, the first port 11 of the first main valve is in a state of communication with the eighth port 18 of the first main valve, and the third port 13 of the first main valve is in a state of communication with the sixth port 16 of the first main valve.
When the first main valve 1 is in the left position function, the second port 12, the third port 13, and the seventh port 17 of the first main valve are all in the blocked state, the first port 11 of the first main valve is simultaneously communicated with the fifth port 15 and the sixth port 16 of the first main valve, and the fourth port 14 of the first main valve is communicated with the eighth port 18 of the first main valve.
The first port 21 of the second main valve communicates with the oil inlet 41, the third port 23 of the second main valve communicates with the first port 31 of the control valve, the fourth port 24 of the second main valve communicates with the oil return port 42, the fifth port 25 of the second main valve communicates with the control chamber 33 of the control valve through the second damper 62, the sixth port 26 of the second main valve communicates with the third working port 53, the seventh port 27 of the second main valve communicates with the oil return port 42, and the eighth port 28 of the second main valve communicates with the fourth working port 54.
When the second main valve 2 is in the neutral position, the first port 21 of the second main valve, the third port 23 of the second main valve, the fourth port 24 of the second main valve, the fifth port 25 of the second main valve, the sixth port 26 of the second main valve, and the eighth port 28 of the second main valve are all in the closed state, and the second port 22 of the second main valve and the seventh port 27 of the second main valve are in the communication state.
When the second main valve 2 is in the right position function, the second port 22 of the second main valve, the fourth port 24 of the second main valve, the fifth port 25 of the second main valve, and the seventh port 27 of the second main valve are all in the blocking state, the first port 21 of the second main valve and the eighth port 28 of the second main valve are in the communication state, and the third port 23 of the second main valve and the sixth port 26 of the second main valve are in the communication state.
When the second master valve 2 is in the left position function, the second port 22 of the second master valve, the third port 23 of the second master valve, and the seventh port 27 of the second master valve are all in the blocked state, the first port 21 of the second master valve is in communication with both the fifth port 25 of the second master valve and the sixth port 26 of the second master valve, and the fourth port 24 of the second master valve is in communication with the eighth port 28 of the second master valve.
The second port 32 of the control valve communicates with the return port 42, and the control chamber 33 of the control valve communicates with the return port 42 through the third damper 63.
When the control valve 3 is in a normal state, the first valve port 31 of the control valve is directly communicated with the second valve port 32 of the control valve. When the oil in the control valve chamber 33 drives the control valve 3 to switch to the control position, the first valve port 31 of the control valve is in throttling communication with the second valve port 32 of the control valve.
As shown in fig. 1, the hydraulic multi-way directional control valve for construction machinery according to the present embodiment is further provided with a first check valve 71. The first check valve 71 is located between the first port 11 of the first main valve and the oil inlet 41, so that the oil flows to the first port 11 of the first main valve in a single direction, thereby preventing the oil from flowing back to the first working port 51 or the second working port 52 when the first main valve 1 is in the left-position function or the right-position function.
As shown in fig. 1, in the hydraulic multi-way directional control valve for construction machinery of the present embodiment, a second check valve 72 is further provided. The second check valve 72 is located between the first port 21 of the second main valve and the oil inlet 41, so that the oil flows to the first port 21 of the second main valve in a single direction, thereby preventing the oil from flowing back from the third working port 53 or the fourth working port 54 when the second main valve 2 is in the left-position function or the right-position function.
Referring to fig. 1, in the hydraulic multi-way directional control valve for construction machinery of the present embodiment, both the first main valve 1 and the second main valve 2 are manual control valves. The handle is arranged at one end of the main valve, the main valve spring is arranged at the other end of the main valve, and the switching of the main valve between different positions can be changed by means of the handle and the main valve spring.
Referring to fig. 1, in the hydraulic multi-way directional control valve for construction machinery of the present embodiment, a control spring is provided on the control valve 3 to drive the control valve 3 to a normal position. Furthermore, the control spring adopts a pressure adjustable spring, so that the oil pressure of the control cavity can be changed when the control valve is switched between a normal position and a control position, and different control effects are achieved.
In the embodiment, the first main valve, the second main valve and the control valve are designed by the same valve body, so that the casting cost and the processing cost of the valve body can be reduced, and the use cost of the hydraulic multi-way reversing valve of the engineering machinery is lower.
Referring to fig. 1 to 4, the working process of controlling the bucket cylinder and the boom cylinder to operate by using the hydraulic multi-way valve of the construction machine according to the embodiment is as follows:
the hydraulic multi-way directional control valve of the engineering machinery of the embodiment is connected to a hydraulic system, specifically, an oil inlet 41 is communicated with an oil outlet of a hydraulic pump 81, an oil return port 42 is communicated with an oil tank 82, a rodless cavity of a bucket cylinder 91 is communicated with a first working port 51, a rod cavity of the bucket cylinder 91 is communicated with a second working port 52, a rodless cavity of a boom cylinder 92 is communicated with a third working port 53, and a rod cavity of the boom cylinder 92 is communicated with a fourth working port 54.
When the first main valve 1 and the second main valve 2 are in the neutral position function, the second valve port 12 of the first main valve is communicated with the seventh valve port 17 of the first main valve, and the second valve port 22 of the second main valve is communicated with the seventh valve port 27 of the second main valve, the hydraulic pump 81 is started to output high-pressure oil, the high-pressure oil flows to the second valve port 12 of the first main valve through the oil inlet 41, and flows back to the oil tank 82 through the seventh valve port 17 of the first main valve, the second valve port 22 of the second main valve, the seventh valve port 27 of the second main valve and the oil return port 42 in sequence, and low-pressure starting of the hydraulic pump 81 is realized.
When controlling both the first main valve 1 and the second main valve 2 to switch to the right function, the first port 11 of the first main valve communicates with the eighth port 18 of the first main valve, the third port 13 of the first main valve communicates with the sixth port 16 of the first main valve, the first port 21 of the second main valve communicates with the eighth port 28 of the second main valve, and the third port 23 of the second main valve communicates with the sixth port 26 of the second main valve. The high-pressure oil outputted by the hydraulic pump 81 flows through the oil inlet 41 to the first port 11 of the first main valve through the first check valve 71 and flows to the first port 21 of the second main valve through the second check valve 72. Wherein, the high-pressure oil flowing to the first port 11 of the first main valve flows to the rod chamber of the bucket cylinder 91 through the eighth port 18 and the second working port 52 of the first main valve, and the low-pressure oil in the rodless chamber of the bucket cylinder 91 flows back to the oil tank 82 through the first working port 51, the sixth port 16 of the first main valve, the third port 13 of the first main valve, the first port 31 of the control valve, the second port 32 of the control valve and the oil return port 42. The high-pressure oil flowing to the first port 21 of the second main valve flows to the rod chamber of the boom cylinder 92 through the eighth port 28 and the fourth port 54 of the second main valve, and the low-pressure oil in the rodless chamber of the boom cylinder 92 flows back to the oil tank 82 through the third port 53, the sixth port 26 of the second main valve, the third port 23 of the second main valve, the first port 31 of the control valve, the second port 32 of the control valve, and the oil return port 42. At this time, since the fifth valve port 15 of the first main valve and the fifth valve port 25 of the second main valve are both in a sealed state, the control chamber 33 of the control valve is free from high-pressure oil, so that the control valve 3 is in a normal position under the action of the control spring, the oil flowing to the first valve port 31 of the control valve smoothly flows back to the oil tank 82, and further the bucket cylinder 91 and the boom cylinder 92 are both contracted and have a small load difference therebetween, so that the operating speeds of the two cylinders can be accurately controlled.
When controlling both the first main valve 1 and the second main valve 2 to switch to the left position function, the first port 11 of the first main valve communicates with the fifth port 15 of the first main valve and the sixth port 16 of the first main valve at the same time, the fourth port 14 of the first main valve communicates with the eighth port 18 of the first main valve, the first port 21 of the second main valve communicates with the fifth port 25 of the second main valve and the sixth port 26 of the second main valve at the same time, and the fourth port 24 of the second main valve communicates with the eighth port 28 of the second main valve. The high-pressure oil outputted by the hydraulic pump 81 flows through the oil inlet 41 to the first port 11 of the first main valve through the first check valve 71 and flows to the first port 21 of the second main valve through the second check valve 72. Wherein the high-pressure oil flowing to the first port 11 of the first master valve flows to the rodless chamber of the bucket cylinder 91 through the first port 11 of the first master valve, the sixth port 16 of the first master valve, and the first working port 51, and the low-pressure oil in the rod chamber of the bucket cylinder 91 directly flows back to the oil tank 82 through the second working port 52, the eighth port 18 of the first master valve, the fourth port 14 of the first master valve, and the oil return port 42. The high-pressure oil flowing to the first port 21 of the second main valve flows to the rodless chamber of the boom cylinder 92 through the first port 21 of the second main valve, the sixth port 26 of the second main valve, and the third port 53, and the low-pressure oil in the rod chamber of the boom cylinder 92 directly flows back to the oil tank 82 through the fourth port 54, the eighth port 28 of the second main valve, the fourth port 24 of the second main valve, and the oil return port 42. At this time, the difference in load between the bucket cylinder 91 and the boom cylinder 92 is small, so that the operating speeds of the two cylinders can be accurately controlled.
When the first main valve 1 is controlled to switch to the right position function and the second main valve 2 is controlled to switch to the left position function, the high-pressure oil outputted by the hydraulic pump 81 flows to the first port 11 of the first main valve through the first check valve 71 and to the first port 21 of the second main valve through the second check valve 72 via the oil inlet 41. Wherein, the high-pressure oil flowing to the first port 11 of the first main valve flows to the rod chamber of the bucket cylinder 91 through the eighth port 18 and the second working port 52 of the first main valve, and the low-pressure oil in the rodless chamber of the bucket cylinder 91 flows back to the oil tank 82 through the first working port 51, the sixth port 16 of the first main valve, the third port 13 of the first main valve, the first port 31 of the control valve, the second port 32 of the control valve and the oil return port 42. The high-pressure oil flowing to the first port 21 of the second main valve flows to the rodless chamber of the boom cylinder 92 through the first port 21 of the second main valve, the sixth port 26 of the second main valve, and the third port 53, and the low-pressure oil in the rod chamber of the boom cylinder 92 directly flows back to the oil tank 82 through the fourth port 54, the eighth port 28 of the second main valve, the fourth port 24 of the second main valve, and the oil return port 42. At this time, part of the high-pressure oil at the first port 21 of the second main valve enters the fifth port 25 of the second main valve, and flows into the control chamber 33 of the control valve through the second damper 62, and part of the high-pressure oil in the control chamber 33 of the control valve flows into the oil return port 42 through the third damper 63 and flows back to the oil tank 82, so that the high-pressure oil in the control chamber 33 overcomes the action of the control spring to switch the control valve 3 to the working position, so that the oil at the first port 31 of the control valve generates a back pressure through throttling, flows to the second port 32 of the control valve, and flows back to the oil tank 82 through the oil return port 42, at this time, the contracting load of the bucket cylinder 91 is small, the extending load of the boom cylinder 92 is large, and the load difference between the bucket cylinder 91 and the boom cylinder 92 is not large under the action of the back pressure, thereby realizing the precise control of the operating speeds of the two cylinders.
When the first main valve 1 is controlled to switch to the left position function and the second main valve 2 is controlled to switch to the right position function, the high-pressure oil outputted by the hydraulic pump 81 flows to the first port 11 of the first main valve through the first check valve 71 and to the first port 21 of the second main valve through the second check valve 72 via the oil inlet 41. Wherein the high-pressure oil flowing to the first port 11 of the first master valve flows to the rodless chamber of the bucket cylinder 91 through the first port 11 of the first master valve, the sixth port 16 of the first master valve, and the first working port 51, and the low-pressure oil in the rod chamber of the bucket cylinder 91 directly flows back to the oil tank 82 through the second working port 52, the eighth port 18 of the first master valve, the fourth port 14 of the first master valve, and the oil return port 42. The high-pressure oil flowing to the first port 21 of the second main valve flows to the rod chamber of the boom cylinder 92 through the eighth port 28 and the fourth port 54 of the second main valve, and the low-pressure oil in the rodless chamber of the boom cylinder 92 flows back to the oil tank 82 through the third port 53, the sixth port 26 of the second main valve, the third port 23 of the second main valve, the first port 31 of the control valve, the second port 32 of the control valve, and the oil return port 42. At this time, because a part of the high-pressure oil at the first valve port 11 of the first main valve enters the fifth valve port 15 of the first main valve, and flows into the control chamber 33 of the control valve through the first damper 61, and a part of the high-pressure oil in the control chamber 33 of the control valve flows into the oil return port 42 through the third damper 63 and flows back to the oil tank 82, so that the high-pressure oil in the control chamber 33 overcomes the action of the control spring to switch the control valve 3 to the working position, so that the oil at the first valve port 31 of the control valve generates a back pressure through throttling and flows into the second valve port 32 of the control valve and flows back to the oil tank 82 through the oil return port 42, at this time, the bucket cylinder 91 extends out to have a large load, the boom cylinder 92 contracts to have a small load, and a load difference between the bucket cylinder 91 and the boom cylinder 92 is not large under the action of the return back pressure, thereby realizing accurate control of the operating speeds of the two cylinders.
Claims (10)
1. The hydraulic multi-way reversing valve for the engineering machinery is characterized by comprising a first main valve, a second main valve and a control valve;
the first valve port of the first main valve and the second valve port of the first main valve are both communicated with the oil inlet, the third valve port of the first main valve is communicated with the first valve port of the control valve, the fourth valve port of the first main valve is communicated with the oil return port, the fifth valve port of the first main valve is communicated with the control cavity of the control valve through a first damper, the sixth valve port of the first main valve is communicated with the first working port, the seventh valve port of the first main valve is communicated with the second valve port of the second main valve, and the eighth valve port of the first main valve is communicated with the second working port;
when the first main valve is in a neutral position function, the first valve port of the first main valve, the third valve port of the first main valve, the fourth valve port of the first main valve, the fifth valve port of the first main valve, the sixth valve port of the first main valve and the eighth valve port of the first main valve are all in a blocking state, and the second valve port of the first main valve and the seventh valve port of the first main valve are in a communication state;
when the first main valve is in the right position function, the second port of the first main valve, the fourth port of the first main valve, the fifth port of the first main valve and the seventh port of the first main valve are all in a blocking state, the first port of the first main valve is communicated with the eighth port of the first main valve, and the third port of the first main valve is communicated with the sixth port of the first main valve;
when the first main valve is in a left-position function, the second port of the first main valve, the third port of the first main valve and the seventh port of the first main valve are all in a blocking state, the first port of the first main valve is simultaneously communicated with the fifth port of the first main valve and the sixth port of the first main valve, and the fourth port of the first main valve is communicated with the eighth port of the first main valve;
the first valve port of the second main valve is communicated with the oil inlet, the third valve port of the second main valve is communicated with the first valve port of the control valve, the fourth valve port of the second main valve is communicated with the oil return port, the fifth valve port of the second main valve is communicated with the control cavity of the control valve through a second damper, the sixth valve port of the second main valve is communicated with the third working port, the seventh valve port of the second main valve is communicated with the oil return port, and the eighth valve port of the second main valve is communicated with the fourth working port;
when the second main valve is in a neutral position function, the first valve port of the second main valve, the third valve port of the second main valve, the fourth valve port of the second main valve, the fifth valve port of the second main valve, the sixth valve port of the second main valve, and the eighth valve port of the second main valve are all in a blocking state, and the second valve port of the second main valve and the seventh valve port of the second main valve are in a communication state;
when the second main valve is in a right-position function, the second port of the second main valve, the fourth port of the second main valve, the fifth port of the second main valve and the seventh port of the second main valve are all in a blocking state, the first port of the second main valve is communicated with the eighth port of the second main valve, and the third port of the second main valve is communicated with the sixth port of the second main valve;
when the second main valve is in the left position function, the second port of the second main valve, the third port of the second main valve and the seventh port of the second main valve are all in a blocked state, the first port of the second main valve is simultaneously communicated with the fifth port of the second main valve and the sixth port of the second main valve, and the fourth port of the second main valve is communicated with the eighth port of the second main valve;
a second valve port of the control valve is communicated with the oil return port, and a control cavity of the control valve is communicated with the oil return port through a third damper;
when the control valve is in a normal state, the first valve port of the control valve is directly communicated with the second valve port of the control valve; when oil in a control cavity in the control valve drives the control valve to be switched to a control position, the first valve port of the control valve is in throttling communication with the second valve port of the control valve.
2. The hydraulic multiple directional control valve for engineering machinery according to claim 1, characterized in that the hydraulic multiple directional control valve for engineering machinery is further provided with a first one-way valve; the first check valve is positioned between the first valve port of the first main valve and the oil inlet, so that oil flows to the first valve port of the first main valve in a one-way mode.
3. The engineering machinery hydraulic multi-way reversing valve according to claim 1, wherein the engineering machinery hydraulic multi-way reversing valve is further provided with a second one-way valve; the second one-way valve is positioned between the first valve port of the second main valve and the oil inlet, so that the oil flows to the first valve port of the second main valve in a one-way mode.
4. The work machine hydraulic multiple directional control valve of claim 1, wherein the first main valve is a manual control valve.
5. The hydraulic multi-way reversing valve for engineering machinery according to claim 4, wherein a handle is arranged at one end of the first main valve, and a first main valve spring is arranged at the other end of the first main valve.
6. The work machine hydraulic multiple directional control valve of claim 1, wherein the second main valve is a manual control valve.
7. The hydraulic multi-way reversing valve for engineering machinery according to claim 6, wherein a handle is arranged at one end of the second main valve, and a second main valve spring is arranged at the other end of the second main valve.
8. The hydraulic multiple directional control valve for engineering machinery according to claim 1, wherein the control valve is provided with a control spring to drive the control valve to a normal position.
9. The work machine hydraulic multi-way directional valve according to claim 8, wherein the control spring is a pressure adjustable spring.
10. The work machine hydraulic multiple directional control valve according to any one of claims 1-9, wherein the first main valve, the second main valve, and the control valve share a valve body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211605085.7A CN115978027A (en) | 2022-12-14 | 2022-12-14 | Engineering machinery hydraulic multi-way reversing valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211605085.7A CN115978027A (en) | 2022-12-14 | 2022-12-14 | Engineering machinery hydraulic multi-way reversing valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115978027A true CN115978027A (en) | 2023-04-18 |
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ID=85973159
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211605085.7A Pending CN115978027A (en) | 2022-12-14 | 2022-12-14 | Engineering machinery hydraulic multi-way reversing valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115978027A (en) |
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2022
- 2022-12-14 CN CN202211605085.7A patent/CN115978027A/en active Pending
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Application publication date: 20230418 |