阅读说明：本技术 一种液压多路换向阀 (Hydraulic multi-way reversing valve ) 是由 韩国昊 李红生 邵倩倩 于 2020-07-21 设计创作，主要内容包括：本发明提出一种换向阀,包括：进油联,至少一个换向联,出油联。根据本发明实施例的换向阀,结构简单、性价比高、节能。(The invention provides a reversing valve, which comprises: the oil inlet is connected, at least one reversing connection is connected, and the oil outlet is connected. The reversing valve provided by the embodiment of the invention has the advantages of simple structure, high cost performance and energy conservation.)

1. A hydraulic multiple directional control valve, comprising: an oil inlet connection, at least one reversing connection and an oil outlet connection;

the oil inlet union comprises: the damping device comprises an oil inlet coupling shell, a first damper, an oil inlet coupling end cover, a control piston with the section being in a shape of '┤', a spring and an oil supplementing check valve, wherein the oil inlet coupling shell is provided with an oil inlet coupling oil passage which is communicated up and down and an oil inlet coupling step blind hole with a right opening and a small left and a large right opening; the first damper is arranged at the outlet end of the oil inlet connecting oil duct; the oil inlet connecting end cover is arranged on the oil inlet connecting shell to seal the right end of the oil inlet connecting step blind hole, and the left end of the oil inlet connecting end cover is provided with a step; the horizontal limb of the control piston is matched in the small hole section of the oil inlet connecting step blind hole, the vertical limb of the control piston is matched in the large hole section of the oil inlet connecting step blind hole, the middle part of the horizontal limb of the control piston is constructed into a slope reducing section, a through flow groove is arranged in the control piston, a first end of the through flow groove penetrates through the left end face of the control piston, and a second end of the through flow groove penetrates through the outer peripheral wall of the horizontal limb of the control piston at the position close to the vertical limb of the control piston; the spring is sleeved on the horizontal limb of the control piston, the left end of the spring is propped against the step surface of the oil inlet connecting step blind hole, the right end of the spring is propped against the vertical limb of the control piston, the spring normally pushes the control piston to the right so that the right end face of the control piston abuts against the left end face of the oil inlet connecting end cover, a control cavity is formed between the right end face of the control piston and the left end face of the oil inlet connecting end cover in the oil inlet connecting step blind hole, the first oil port and the second oil port are both connected with the oil inlet connecting step blind hole, when the right end face of the control piston abuts against the left end face of the oil inlet end cover, the control piston disconnects the first oil port and the second oil port, when the control piston moves leftwards against the acting force of the spring, the first oil port and the second oil port are connected through the slope reducing section; the oil supplementing one-way valve is arranged in the oil inlet connecting shell, and the outlet end of the oil supplementing one-way valve is connected with the control cavity;

the reversing union comprises: the reversing connection shell comprises a reversing connection shell body, a left end cover, a left piston, a left spring, a right end cover, a right piston, a right spring, a reversing valve core, a left handle, a right handle and an oil inlet check valve, wherein a valve hole which is communicated left and right is formed in the reversing connection shell body, the valve hole is a step hole with two large sides and a small middle part, the reversing connection shell body is provided with a first opening, a second opening, a third opening, a fourth opening, a fifth opening and a sixth opening, a first through flow groove, a second through flow groove, a third through flow groove, a second through flow groove and a fifth through flow groove which are arranged at left and right intervals are formed in the inner peripheral wall of a small diameter section of the valve hole, the first opening is opposite to the second opening from top to bottom, the first opening is connected with the outlet end of the oil inlet connection oil duct, the third opening is connected with the first through flow groove, the sixth opening is connected with the second through flow groove, and the fourth opening is connected with the third, the fifth opening is connected with the fourth runner; the left end cover is arranged on the reversing connection shell to seal the left end of the valve hole; the left piston is arranged in the left large-diameter section of the valve hole; the left end of the left spring abuts against the left end cover, the right end of the left spring abuts against the left piston, the left spring normally pushes the left piston to the right so that the right end face of the left piston abuts against the left step face of the valve hole, and a left piston cavity is defined between the left end cover and the left piston; the right end cover is arranged on the reversing connection shell to seal the right end of the valve hole; the right piston is arranged in the right large-diameter section of the valve hole; the right end of the right spring abuts against the right end cover, the left end of the right spring abuts against the right piston, the right spring normally pushes the right piston to the left so that the left end face of the right piston abuts against the right step face of the valve hole, a right piston cavity is defined between the right end cover and the right piston, the left piston cavity is connected with the right piston cavity, and the right piston cavity is connected with the control cavity; the reversing valve core is arranged in the small-diameter section of the valve hole, a sixth through flow groove, a seventh through flow groove and an eighth through flow groove which are arranged at intervals from left to right are formed in the outer peripheral wall of the reversing valve core, a connecting oil duct which is normally connected with the first through flow groove and the fifth through flow groove is formed in the reversing valve core, the left end of the reversing valve core sequentially penetrates through the left piston, the left spring and the left end cover leftwards and extends out of the left end face of the left end cover, the right end of the reversing valve core sequentially penetrates through the right piston, the right spring and the right end cover rightwards and extends out of the right end face of the right end cover, and the reversing valve core is switchable among a middle position, a left position and a right; the left handle is respectively and pivotally connected with the reversing connection shell and the left end of the reversing valve core; the right handle is respectively and pivotally connected with the reversing connection shell and the right end of the reversing valve core; the oil inlet check valve is arranged in the reversing linkage shell, the inlet end of the oil inlet check valve is connected with the fifth opening, and the outlet end of the oil inlet check valve is connected with the fourth through groove;

the oil outlet union comprises an oil outlet union shell and a second damper arranged in the oil outlet union shell, the oil outlet union shell is provided with a first oil outlet and a second oil outlet, the second opening is connected with the first oil outlet, one end of the second damper is connected with the second oil outlet, the other end of the second damper is connected with the second oil outlet, and the inlet end of the oil supplementing one-way valve and the sixth opening are connected with the second oil outlet.

2. The hydraulic multi-way reversing valve of claim 1, wherein when the reversing valve spool is in the neutral position, the sixth vent groove connects the first opening and the second opening, and the first vent groove, the second vent groove, the third vent groove, the fourth vent groove, and the fifth vent groove are disconnected by an outer peripheral wall of the reversing valve spool in pairs.

3. The hydraulic multi-way directional valve according to claim 1, wherein when the direction change valve spool is in the left position, the right handle pushes the direction change valve spool to move leftward against the force of the left spring to compress the left piston chamber, the outer peripheral wall of the direction change valve spool opens the first opening and the second opening, the outer peripheral wall of the direction change valve spool opens the first through flow groove and the second through flow groove, the outer peripheral wall of the direction change valve spool opens the second through flow groove and the third through flow groove, the outer peripheral wall of the direction change valve spool opens the third through flow groove and the fourth through flow groove, and the outer peripheral wall of the direction change valve spool opens the fourth through flow groove and the fifth through flow groove.

4. The hydraulic multi-way valve according to claim 1, wherein when the direction change valve spool is in the right position, the left handle pushes the direction change valve spool rightward against the force of the right spring to move rightward to compress the right piston chamber, the outer peripheral wall of the direction change valve spool opens the first opening and the second opening, the outer peripheral wall of the direction change valve spool opens the first through-flow groove and the second through-flow groove, the outer peripheral wall of the direction change valve spool opens the second through-flow groove and the third through-flow groove, the outer peripheral wall of the direction change valve spool opens the third through-flow groove and the fourth through-flow groove, and the outer peripheral wall of the direction change valve spool opens the fourth through-flow groove and the fifth through-flow groove.

5. The hydraulic multi-way reversing valve according to claim 1, wherein the oil inlet union further comprises an overflow valve, the overflow valve is arranged in the oil inlet union housing, an inlet end of the overflow valve is connected with the first oil port, and an outlet end of the overflow valve is connected with an inlet end of the oil replenishing check valve, the sixth opening and the second oil port respectively.

Technical Field

The invention belongs to the technical field of hydraulic valves, and particularly relates to a hydraulic multi-way reversing valve.

Background

The multi-way reversing valve is an integrated valve formed by combining a plurality of single-connection reversing valves and a plurality of auxiliary valves such as a safety overflow valve, a one-way valve and the like, has a compact structure, and is widely applied to engineering machinery, construction machinery, agricultural machinery and environmental sanitation equipment. The multi-way valve is divided into an integral structure and a sheet structure, the integral structure and the sheet structure are complex, the process difficulty is high, and the sheet structure is combined by an oil inlet connection valve, a reversing connection valve and an oil outlet connection valve, so that the multi-way valve is simple in structure, good in manufacturability and flexible in combination.

The existing load-sensitive multi-way valve can be applied to engineering machinery which comprises a plurality of actuating mechanisms and has compound action, and forms a load-sensitive hydraulic system together with a hydraulic load-sensitive pump. The maximum load pressure control signal acts on a pressure compensator of the load sensitive pump, and the load sensitive pump senses the pressure-flow demand of the system and provides adjustable flow according to the flow demand when the working condition of the system changes. The pressure of the load sensitive pump is set to a lower fixed value so that the pump pressure exceeds the maximum load pressure by a lower fixed value and is continuously adjusted with the maximum load pressure so that the system avoids flow loss.

However, the existing load-sensitive multi-way directional control valve has the following problems in use:

(1) the load pressure control signal acquisition point of the existing load-sensitive multi-way reversing valve is generally arranged in front of or behind each reversing valve, then is connected to a load pressure feedback channel of the reversing valve through a shuttle valve and a flow channel or directly through the flow channel, and finally outputs a signal through an oil inlet joint or a tail joint and acts on a load-sensitive pump compensator through a connecting pipeline to control the flow of a pump. Because the connecting pipeline between the multiple directional control valves and the load sensitive pump is very long, and the flow channels in the load sensitive multiple directional control valves are changed more, when the maximum load pressure control signal is fed back to the compensator of the load sensitive pump through the internal oil channels of the multiple directional control valves and the connecting pipeline, the pressure attenuation is larger, the pressure set value of the pressure compensator of the load sensitive pump must be increased to ensure stable flow, but larger flow loss is caused;

(2) the reversing connection of the load-sensitive multi-way reversing valve in the prior art is mostly a closed-center reversing valve, each reversing connection comprises a two-way pressure compensator and a shuttle valve, and although better flow control characteristics can be realized, the structure is complex and high in cost, and multiple executing mechanisms are not required to perform compound actions in many practical working conditions, so that the function waste and the cost performance are caused.

Disclosure of Invention

The present invention is directed to solving, at least to some extent, one of the technical problems in the related art.

Therefore, the invention aims to provide a hydraulic multi-way reversing valve for a load-sensitive pump system, which has simple structure, high cost performance and energy saving.

According to an embodiment of the present invention, a hydraulic multi-way directional control valve includes: an oil inlet connection, at least one reversing connection and an oil outlet connection;

the oil inlet union comprises: the damping device comprises an oil inlet coupling shell, a first damper, an oil inlet coupling end cover, a control piston with the section being in a shape of '┤', a spring and an oil supplementing check valve, wherein the oil inlet coupling shell is provided with an oil inlet coupling oil passage which is communicated up and down and an oil inlet coupling step blind hole with a right opening and a small left and a large right opening; the first damper is arranged at the outlet end of the oil inlet connecting oil duct; the oil inlet connecting end cover is arranged on the oil inlet connecting shell to seal the right end of the oil inlet connecting step blind hole, and the left end of the oil inlet connecting end cover is provided with a step; the horizontal limb of the control piston is matched in the small hole section of the oil inlet connecting step blind hole, the vertical limb of the control piston is matched in the large hole section of the oil inlet connecting step blind hole, the middle part of the horizontal limb of the control piston is constructed into a slope reducing section, a through flow groove is arranged in the control piston, a first end of the through flow groove penetrates through the left end face of the control piston, and a second end of the through flow groove penetrates through the outer peripheral wall of the horizontal limb of the control piston at the position close to the vertical limb of the control piston; the spring is sleeved on the horizontal limb of the control piston, the left end of the spring is propped against the step surface of the oil inlet connecting step blind hole, the right end of the spring is propped against the vertical limb of the control piston, the spring normally pushes the control piston to the right so that the right end face of the control piston abuts against the left end face of the oil inlet connecting end cover, a control cavity is formed between the right end face of the control piston and the left end face of the oil inlet connecting end cover in the oil inlet connecting step blind hole, the first oil port and the second oil port are both connected with the oil inlet connecting step blind hole, when the right end face of the control piston abuts against the left end face of the oil inlet end cover, the control piston disconnects the first oil port and the second oil port, when the control piston moves leftwards against the acting force of the spring, the first oil port and the second oil port are connected through the slope reducing section; the oil supplementing one-way valve is arranged in the oil inlet connecting shell, and the outlet end of the oil supplementing one-way valve is connected with the control cavity;

the reversing union comprises: the reversing connection shell comprises a reversing connection shell body, a left end cover, a left piston, a left spring, a right end cover, a right piston, a right spring, a reversing valve core, a left handle, a right handle and an oil inlet check valve, wherein a valve hole which is communicated left and right is formed in the reversing connection shell body, the valve hole is a step hole with two large sides and a small middle part, the reversing connection shell body is provided with a first opening, a second opening, a third opening, a fourth opening, a fifth opening and a sixth opening, a first through flow groove, a second through flow groove, a third through flow groove, a second through flow groove and a fifth through flow groove which are arranged at left and right intervals are formed in the inner peripheral wall of a small diameter section of the valve hole, the first opening is opposite to the second opening from top to bottom, the first opening is connected with the outlet end of the oil inlet connection oil duct, the third opening is connected with the first through flow groove, the sixth opening is connected with the second through flow groove, and the fourth opening is connected with the third, the fifth opening is connected with the fourth runner; the left end cover is arranged on the reversing connection shell to seal the left end of the valve hole; the left piston is arranged in the left large-diameter section of the valve hole; the left end of the left spring abuts against the left end cover, the right end of the left spring abuts against the left piston, the left spring normally pushes the left piston to the right so that the right end face of the left piston abuts against the left step face of the valve hole, and a left piston cavity is defined between the left end cover and the left piston; the right end cover is arranged on the reversing connection shell to seal the right end of the valve hole; the right piston is arranged in the right large-diameter section of the valve hole; the right end of the right spring abuts against the right end cover, the left end of the right spring abuts against the right piston, the right spring normally pushes the right piston to the left so that the left end face of the right piston abuts against the right step face of the valve hole, a right piston cavity is defined between the right end cover and the right piston, the left piston cavity is connected with the right piston cavity, and the right piston cavity is connected with the control cavity; the reversing valve core is arranged in the small-diameter section of the valve hole, a sixth through flow groove, a seventh through flow groove and an eighth through flow groove which are arranged at intervals from left to right are formed in the outer peripheral wall of the reversing valve core, a connecting oil duct which is normally connected with the first through flow groove and the fifth through flow groove is formed in the reversing valve core, the left end of the reversing valve core sequentially penetrates through the left piston, the left spring and the left end cover leftwards and extends out of the left end face of the left end cover, the right end of the reversing valve core sequentially penetrates through the right piston, the right spring and the right end cover rightwards and extends out of the right end face of the right end cover, and the reversing valve core is switchable among a middle position, a left position and a right; the left handle is respectively and pivotally connected with the reversing connection shell and the left end of the reversing valve core; the right handle is respectively and pivotally connected with the reversing connection shell and the right end of the reversing valve core; the oil inlet check valve is arranged in the reversing linkage shell, the inlet end of the oil inlet check valve is connected with the fifth opening, and the outlet end of the oil inlet check valve is connected with the fourth through groove;

the oil outlet union comprises an oil outlet union shell and a second damper arranged in the oil outlet union shell, the oil outlet union shell is provided with a first oil outlet and a second oil outlet, the second opening is connected with the first oil outlet, one end of the second damper is connected with the second oil outlet, the other end of the second damper is connected with the second oil outlet, and the inlet end of the oil supplementing one-way valve and the sixth opening are connected with the second oil outlet.

Advantageously, when the reversing valve core is in the neutral position, the sixth through flow groove connects the first opening and the second opening, and the first through flow groove, the second through flow groove, the third through flow groove, the fourth through flow groove and the fifth through flow groove are disconnected in pairs by the peripheral wall of the reversing valve core.

Advantageously, when the direction changing valve core is in the left position, the right handle pushes the direction changing valve core to move leftward against the action force of the left spring to compress the left piston cavity, the outer peripheral wall of the direction changing valve core disconnects the first opening and the second opening, the outer peripheral wall of the direction changing valve core connects the first through flow groove and the second through flow groove, the outer peripheral wall of the direction changing valve core disconnects the second through flow groove and the third through flow groove, the outer peripheral wall of the direction changing valve core connects the third through flow groove and the fourth through flow groove, and the outer peripheral wall of the direction changing valve core disconnects the fourth through flow groove and the fifth through flow groove.

Advantageously, when the direction changing valve core is in the right position, the left handle pushes the direction changing valve core to move rightward to compress the right piston cavity by overcoming the acting force of the right spring, the peripheral wall of the direction changing valve core disconnects the first opening and the second opening, the peripheral wall of the direction changing valve core disconnects the first through flow groove and the second through flow groove, the peripheral wall of the direction changing valve core connects the second through flow groove and the third through flow groove, the peripheral wall of the direction changing valve core disconnects the third through flow groove and the fourth through flow groove, and the peripheral wall of the direction changing valve core connects the fourth through flow groove and the fifth through flow groove.

Advantageously, the oil inlet union further comprises an overflow valve, the overflow valve is arranged in the oil inlet union housing, an inlet end of the overflow valve is connected with the first oil port, and an outlet end of the overflow valve is respectively connected with an inlet end of the oil supplementing one-way valve, the sixth opening and the second oil outlet.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

FIG. 1 is a schematic view of a hydraulic multi-way reversing valve according to one embodiment of the invention;

FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1;

FIG. 3 is a cross-sectional view taken along line B-B of FIG. 1 with the diverter spool in the neutral position;

FIG. 4 is another cross-sectional view taken along line B-B of FIG. 1 with the diverter spool in the left position;

FIG. 5 is a further cross-sectional view taken along line B-B of FIG. 1 with the diverter spool in the right position;

FIG. 6 is a cross-sectional view taken along line C-C of FIG. 1;

FIG. 7 is a schematic view of a reversing valve according to another embodiment of the invention.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.

The direction valve according to an embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

As shown in fig. 1 to 7, a direction valve according to an embodiment of the present invention includes: the oil inlet is connected, at least one reversing connection is connected, and the oil outlet is connected.

The oil inlet union comprises: the damping device comprises an oil inlet coupling housing 1, a first damper 1d, an oil inlet coupling end cover 12, a control piston 1a2 with the section being in the shape of ┤, a spring 1a1 and an oil supplementing check valve 1 c.

The oil inlet connecting shell 1 is provided with an oil inlet connecting channel 11 which is communicated up and down and an oil inlet connecting step blind hole which is opened rightwards and is small in left and big in right, the inlet end of the oil inlet connecting channel 11 is constructed into a first oil port P, and the oil inlet connecting shell 1 is further provided with a second oil port Ls.

The first damper 1d is provided at the outlet end of the oil-intake linkage passage 11.

The oil inlet end cover 12 is arranged on the oil inlet coupling shell 1 to seal the right end of the step blind hole, and the left end of the oil inlet end cover 12 is provided with a step.

The horizontal limb of the control piston 1a2 is fitted in the small hole section of the oil inlet connection step blind hole and the vertical limb of the control piston 1a2 is fitted in the large hole section of the oil inlet connection step blind hole, the middle part of the horizontal limb of the control piston 1a2 is configured into a slope reducing section, a through flow groove 1a21 is arranged in the control piston 1a2, a first end of the through flow groove 1a21 penetrates through the left end face of the control piston 1a2, and a second end of the through flow groove 1a21 penetrates through the outer peripheral wall of the horizontal limb of the control piston 1a2 at the vertical limb adjacent to the control piston 1a 2.

The spring 1a1 is sleeved on the horizontal limb of the control piston 1a2, the left end of the spring 1a1 abuts against the step surface of the oil inlet connecting step blind hole, the right end of the spring 1a1 abuts against the vertical limb of the control piston 1a2, the spring 1a1 normally pushes the control piston 1a2 to the right so that the right end surface of the control piston 1a2 abuts against the left end surface of the oil inlet connecting end cover 12, in the oil inlet joint step blind hole, a control cavity 101 is formed between the right end face of the control piston 1a2 and the left end face of the oil inlet joint end cover 12, the first oil port P and the second oil port Ls are both connected with the oil inlet joint step blind hole, when the right end face of the control piston 1a2 abuts against the left end face of the oil inlet header 12, the control piston 1a2 disconnects the first oil port P and the second oil port Ls, when the control piston 1a2 is moved leftward against the force of the spring 1a1, the first and second oil ports P and Ls are connected by the slope reducing section.

The oil supplementing one-way valve 1c is arranged in the oil inlet coupling shell 1, and the outlet end of the oil supplementing one-way valve 1c is connected with the control cavity 101.

The reversing union comprises: the reversing linkage type hydraulic cylinder comprises a reversing linkage shell 2, a left end cover 2b1, a left piston 2b2, a left spring 2b3, a right end cover 2b4, a right piston 2b5, a right spring 2b6, a reversing valve core 2b, a left handle 2b7, a right handle 2b8 and an oil inlet check valve 2 a.

Wherein, the valve opening that link up about having on the switching-over union casing 2, the valve opening is the little step hole in the big centre in both sides, and switching-over union casing 2 has first opening P01, second opening T01, third opening A, fourth opening B, fifth opening P02 and sixth opening T02, interval arrangement's first through-flow groove 21, second through-flow groove 22, third through-flow groove 23, fourth through-flow groove 24 and fifth through-flow groove 25 about having on the internal perisporium of the path section of valve opening, first opening P01 and second opening T01 are relative from top to bottom and first opening P01 links to each other with the exit end of oil feed union oil duct 11, and third opening A links to each other with first through-flow groove 21, and sixth opening T02 links to each other with second through-flow groove 22, and fourth opening B links to each other with third through-flow groove 23, and fifth opening P02 links to each other with fourth through-flow groove 24.

The left end cover 2b1 is arranged on the reversing union housing 2 to close the left end of the valve hole.

The left piston 2b2 is provided in the left large diameter section of the valve hole.

The left end of the left spring 2b3 abuts against the left end cover 2b1 and the right end of the left spring 2b3 abuts against the left piston 2b2, the left spring 2b3 normally pushes the left piston 2b2 to the right so that the right end face of the left piston 2b2 abuts against the left step face of the valve hole, and a left piston cavity 201 is defined between the left end cover 2b1 and the left piston 2b 2.

The right end cap 2b4 is provided on the reversing union housing 2 to close the right end of the valve hole.

The right piston 2b5 is provided in the right large diameter section of the valve hole.

The right end of the right spring 2b6 abuts against a right end cover 2b4 and the left end of the right spring 2b6 abuts against a right piston 2b5, the right spring 2b6 normally pushes the right piston 2b5 to the left so that the left end face of the right piston 2b5 abuts against the right step face of the valve hole, a right piston cavity 202 is defined between the right end cover 2b4 and the right piston 2b5, the left piston cavity 201 is connected with the right piston cavity 202, and the right piston cavity 202 is connected with the control cavity 101.

The reversing valve core 2b is arranged in the small-diameter section of the valve hole, a sixth through flow groove 2b01, a seventh through flow groove 2b02 and an eighth through flow groove 2b03 which are arranged at left and right intervals are formed in the outer peripheral wall of the reversing valve core 2b, a connecting oil channel 2b04 which is normally connected with the first through flow groove 21 and the fifth through flow groove 25 is formed in the reversing valve core 2b, the left end of the reversing valve core 2b sequentially penetrates through the left piston 2b2, the left spring 2b3 and the left end cover 2b1 leftwards and extends out of the left end face of the left end cover 2b1, the right end of the reversing valve core 2b sequentially penetrates through the right piston 2b5, the right spring 2b6 and the right end cover 2b4 rightwards and extends out of the right end face of the right end cover 2b4, and the reversing valve core 2 b.

The left handle 2b7 is pivotally connected to the left end of the direction changing linkage housing 2 and the direction changing valve core 2 b.

The right handle 2b8 is respectively connected with the right ends of the reversing linkage shell 2 and the reversing valve core 2b in a pivoting way.

The oil inlet check valve 2a is arranged in the reversing linkage housing 2, the inlet end of the oil inlet check valve 2a is connected with the fifth opening P02, and the outlet end of the oil inlet check valve 2a is connected with the fourth through groove 24.

The oil outlet union comprises an oil outlet union shell 3 and a second damper 3a arranged in the oil outlet union shell 3, a first oil outlet T1 and a second oil outlet T2 are formed in the oil outlet union shell 3, a second opening T01 is connected with the first oil outlet T1, one end of the second damper 3a is connected with the second oil outlet T2, the other end of the second damper 3a is connected with the second oil outlet Ls, and the inlet end of an oil supplementing one-way valve 1c and the inlet end of a sixth opening T02 are connected with the second oil outlet T2.

As shown in fig. 3, when the direction switching valve core 2b is at the neutral position, the sixth through-flow groove 2b01 connects the first opening P01 and the second opening T01, and the first through-flow groove 21, the second through-flow groove 22, the third through-flow groove 23, the fourth through-flow groove 24, and the fifth through-flow groove 25 are disconnected by the outer peripheral wall of the direction switching valve core 2 b.

As shown in fig. 4, when the direction changing valve core 2b is in the left position, the right handle 2b8 pushes the direction changing valve core 2b leftward against the force of the left spring 2b3 to move leftward to compress the left piston chamber 201, the outer peripheral wall of the direction changing valve core 2b opens the first opening P01 and the second opening T01, the outer peripheral wall of the direction changing valve core 2b opens the first through flow groove 21 and the second through flow groove 22 through the seventh through flow groove 2b02, the outer peripheral wall of the direction changing valve core 2b opens the second through flow groove 22 and the third through flow groove 23, the outer peripheral wall of the direction changing valve core 2b opens the third through flow groove 23 and the fourth through flow groove 24 through the eighth through flow groove 2b03, and the outer peripheral wall of the direction changing valve core 2b opens the fourth through flow groove 24.

As shown in fig. 5, when the direction changing valve core 2b is in the right position, the left handle 2b7 pushes the direction changing valve core 2b rightward to move rightward against the action of the right spring 2b6 to compress the right piston chamber 202, the outer peripheral wall of the direction changing valve core 2b separates the first opening P01 from the second opening T01, the outer peripheral wall of the direction changing valve core 2b separates the first through flow groove 21 from the second through flow groove 22, the outer peripheral wall of the direction changing valve core 2b connects the second through flow groove 22 from the third through flow groove 23 through the seventh through flow groove 2b02, the outer peripheral wall of the direction changing valve core 2b separates the third through flow groove 23 from the fourth through flow groove 24, and the outer peripheral wall of the direction changing valve core 2b connects the fourth through flow groove 24 from the fifth through flow groove 25 through the.

Advantageously, the oil inlet union further comprises an overflow valve 1b, the overflow valve 1b is arranged in the oil inlet union housing 1, an inlet end of the overflow valve 1b is connected with the first oil port P, and an outlet end of the overflow valve 1b is respectively connected with an inlet end of the oil supplementing check valve 1c, a sixth opening T02 and a second oil port T2.

Here, in the present application, the components are connected to each other through oil passages. Taking "the second oil port LS is connected to the second oil outlet T2", the second oil port LS is connected sequentially through oil passages provided in the oil inlet connection, the at least one reversing connection, and the oil outlet connection, and the second damper 3a is provided in a portion of the oil passage located above the oil outlet connection. As will be appreciated by those skilled in the art.

That is to say, the control chamber 101 is formed in the oil inlet connection, the pressure in the control chamber 101 acts on the control piston 1a2 and is counterbalanced by the spring 1a1, the higher the pressure in the control chamber 101 is, the larger the distance of left movement of the control piston 1a2 is, and further, the first oil port P and the second oil port Ls can be partially connected from the off state to the on state until the first oil port P and the second oil port Ls are completely connected.

The left handle 2b7 and the right handle 2b8 in the reversing linkage control the reversing valve core 2b to be switched among three positions of a middle position, a left position and a right position (as shown in figures 3 to 5). When the direction changing valve core 2b is in the neutral position, the first opening P01 is connected with the second opening P02; when the reversing valve core 2b moves rightwards, oil in the right piston cavity 202 enters the control cavity 101 to push the control piston 1a2 to move leftwards; when the direction switching valve element 2b moves leftward, the oil in the left piston chamber 201 enters the control chamber 101 through the right piston chamber 202, and pushes the control piston 1a2 leftward. That is, when the three-position six-way selector valve is actuated, the control piston 1a2 senses the actuation of the selector valve spool 2b and changes the distance that the control piston 1a2 moves to the left, and the larger the distance that the selector valve spool 2b moves to the left or to the right, the larger the distance that the control piston 1a2 moves to the left.

When the reversing valve works, the first oil port P is connected with an outlet of a load sensitive pump, the second oil port Ls is connected with a control port of the load sensitive pump, a third opening A and a fourth opening B of a reversing connection are respectively connected with two oil ports of an executing element (an oil cylinder or a motor), and a first oil outlet T1 and a second oil outlet T2 are respectively connected with an oil tank.

As shown in fig. 1, 3 and 7, when the direction valve spool 2b is in the neutral position, the oil at the outlet of the load sensing pump returns to the oil tank through the first oil port P, the first damper 1d, the first opening P01, the second opening T01 and the first oil outlet T1. At this time, since the direction changing valve core 2b is in the middle position, the control piston 1a2 is in the right position closing position, and the second oil port Ls is connected with the oil tank after passing through the second damper 3a and the second oil outlet T2. That is, at this time, the second oil port Ls has substantially no pressure, the pressure at the outlet of the load sensitive pump is only maintained at the lowest pressure set by the load sensitive pump, and the flow rate is substantially 0.

When the reversing linkage is in action, if the reversing valve core 2b is moved rightwards for reversing as shown in fig. 5, the control piston 1a2 correspondingly moves leftwards according to the distance of the right piston 2b5 moving rightwards. When the first port P starts to communicate with the fourth port B and the third port a starts to communicate with the second outlet T2, the control piston 1a2 also starts to move left; when the opening degrees of the first port P and the fourth port B are increased and the opening degrees of the third port a and the second port T2 are increased, the distance that the control piston 1a2 moves to the left is also increased. When the control piston 1a2 moves to the left for a certain distance, the first oil port P is communicated with the second oil port Ls, oil enters the actuating element through the oil inlet check valve 2a and the fourth opening B, the pressure of the second oil port Ls is increased, the pressure of the outlet of the load sensing pump is also increased, the flow output by the load sensing pump is increased, and when the right piston 2B5 moves to the right for a certain distance and keeps unchanged, the left movement distance of the control piston 1a2 also keeps unchanged. At this time, the pressure difference between the first port P and the second port Ls is kept constant (characteristic of the load-sensitive pump) no matter how the load pressure changes, that is, how the pressure at the fourth port B changes. Therefore, when the linkage is switched to act, the load sensitive control of the load sensitive pump can be realized, and the constant speed control of the actuating element can be realized.

As shown in fig. 7, when there are multiple direction-changing sets, as mentioned above, when the first direction-changing set is working, the second direction-changing set is working at the same time, so that due to the second direction-changing set, the oil in the right piston chamber 202 or the left piston chamber 201 of the second direction-changing set will enter the control chamber 101, and the control piston 1a2 will sense the increased flow rate, so as to increase the left movement distance and meet the flow rate requirement of the actuator. During compound action, if the moving distance of the left piston 2b2 or the right piston 2b5 of the two reversing links is kept constant, the flow output by the load-sensitive pump after passing through the control piston 1a2 is also constant no matter how the load is changed, but the flow passing through the 2 reversing links is distributed according to the load size of each reversing link.

The hydraulic multi-way reversing valve has the following beneficial effects:

1. the collection point of the load sensitive pressure control signal is set on the oil inlet joint, unlike the prior art that the collection point is arranged in front of and behind each joint reversing valve, the load sensitive pressure signal in the invention does not need to pass through a shuttle valve and a complex flow channel, so the attenuation of the load sensitive pressure signal is reduced, the set value of a load sensitive pump pressure compensator can be reduced, and the energy-saving effect can be realized;

2. the control piston is arranged in the oil inlet joint, the left piston cavity and the right piston cavity which are controlled by the position of the valve core are arranged in the reversing joint, and the left piston cavity and the right piston cavity are connected with the control cavity of the control piston, so that the position of the control piston can be changed through the action of the reversing valve core, and the opening between the first oil port P and the second oil port Ls is changed, and therefore the flow supplied by the load sensitive pump according to the requirement is realized, and the flow output to the executing element is not changed along with the load under the condition that the opening of the reversing valve core is not changed when each reversing joint independently acts through the matching of the control piston and the load sensitive pump;

3. the reversing connection is arranged in the opening center, and when the reversing valve of the reversing connection is in the middle position, oil at the outlet of the load sensing pump directly returns to the oil tank, so that the pressure at the outlet of the pump can be reduced, and the heat generation is reduced.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.