A double pump confluence hydraulic circuit combination valve

Abstract

The present invention discloses a dual-pump confluence hydraulic circuit combination valve in the field of hydraulic valve technology, comprising a valve body unit, a hollow shell, and a small liquid inlet pipe, a large liquid inlet pipe and a return pipe respectively arranged on three sides of the outer shell, and the three are connected to the inside of the shell, and the small liquid inlet pipe, the large liquid inlet pipe and the return pipe are not at the same horizontal height. The present invention sets a cylindrical valve core unit, and enables it to switch different hydraulic circuits by rotating and displacing inside the valve body, so as to realize the on-off switching control between the circuits, thereby realizing the confluence liquid supply function of the small flow pump and the large flow pump, the independent liquid supply function of the small flow pump, and the simultaneous overflow function of the small flow pump and the large flow pump.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic valves, and in particular to a dual-pump confluence hydraulic circuit combination valve. Background Art

[0002] During the operation of a hydraulic press, the slider on the machine is generally required to perform actions such as fast forward, working speed, and fast reverse, so as to achieve specific action control. The existing technology generally completes this through a hydraulic system consisting of a double pump and an unloading valve group. When the slider is required to perform fast forward and fast reverse actions, the two pumps supply oil at the same time, and the system pressure is low at this time; when the slider is required to perform working speed actions, the unloading valve group unloads the large flow pump and the small flow pump continues to supply oil, and the system pressure is high at this time.

[0003] In the prior art, a valve group is generally integrated by combining multiple functional valves. Therefore, the structure of the valve group is complex and bulky, and high installation space requirements are required during installation and use. In addition, the combination of multiple functional valves will make the cost higher. Summary of the invention

[0004] In view of the fact that the above-mentioned existing unloading valve group is generally composed of a plurality of functional valves, the structure of the valve group is complex and bulky, and high requirements are placed on the installation space during installation and use. In addition, the combination of a plurality of functional valves will lead to a high cost. The inventors have proposed a dual-pump confluence hydraulic circuit combination valve to solve such problems.

[0005] In order to solve the above technical problems, the present invention provides the following technical solutions: a double pump confluence hydraulic circuit combination valve, comprising:

[0006] The valve body unit comprises a shell with a hollow interior, and a small liquid inlet pipe, a large liquid inlet pipe and a return pipe respectively arranged on three sides of the exterior of the shell, and the three are connected with the interior of the shell, and the small liquid inlet pipe, the large liquid inlet pipe and the return pipe are not at the same level;

[0007] The valve core unit comprises a valve core shaft located in the housing, and the valve core shaft has a cylindrical structure, a confluence groove is spirally inclinedly provided on the valve core shaft, an auxiliary pipe is provided inside the lower part of the valve core shaft, and both ends of the auxiliary pipe pass through the valve core shaft to communicate with the outside, and a limiting ball is provided on the outer wall of the valve core shaft, and the position of the limiting ball on the valve core shaft is opposite to the confluence groove;

[0008] The regulating unit includes a threaded rod vertically threadedly connected to the top of the shell, and the end of the threaded rod extends into the shell, a pressure plate arranged at the end of the threaded rod, and a spring arranged below the pressure plate, and the end of the spring abuts against the top of the valve core shaft; and an electric control valve flange-connected to the bottom of the shell.

[0009] As a preferred solution of the dual-pump converging hydraulic circuit combination valve described in the present invention, wherein: an inner chamber with a diameter matching the valve core shaft diameter is opened inside the outer shell, a spirally inclined limit groove is opened on the inner wall of the outer shell, and the limit ball is slidably connected in the limit groove.

[0010] As a preferred solution of the dual-pump converging hydraulic circuit combination valve described in the present invention, wherein: a small liquid inlet port connected to the inner warehouse is opened inside the small liquid inlet pipe, the outer end of the small liquid inlet port is connected to the outlet of the small flow pump, and a connecting pipe with an "L"-shaped structure is opened below the small liquid inlet port, and the top and the end of the "L"-shaped structure are respectively connected to the small liquid inlet port and the inner warehouse.

[0011] As a preferred solution of the dual-pump converging hydraulic circuit combination valve described in the present invention, a large liquid inlet connected to the inner chamber is opened inside the large liquid inlet pipe, and the outer end of the large liquid inlet is connected to the outlet of the large flow pump.

[0012] As a preferred solution of the dual-pump converging hydraulic circuit combination valve described in the present invention, the return pipe as a whole is two groups of pipes arranged in parallel up and down, and the two groups of pipes are respectively provided with a main return port and an auxiliary return port connected to the interior of the inner warehouse, and the outer ends of the main return port and the auxiliary return port are connected to the return oil tank.

[0013] As a preferred solution of the dual-pump converging hydraulic circuit combination valve described in the present invention, the two ends of the valve core shaft are conical structures, the top end of the valve core shaft is provided with a top block for a limit spring, and the valve core shaft is rotated as a whole and inserted in the inner chamber.

[0014] As a preferred solution of the dual-pump converging hydraulic circuit combination valve described in the present invention, wherein: the converging groove is in a spirally inclined shape as a whole, and the spiral inclination angle is consistent with the limit groove, the inner ends of the small liquid inlet, the large liquid inlet and the main return port are all abutted on the spiral movement path of the converging groove, the height of the converging groove in the horizontal direction is lower than the limit groove, and the end and top of the spiral structure of the converging groove are the lower converging end and the upper converging end respectively.

[0015] As a preferred solution of the dual-pump converging hydraulic circuit combination valve described in the present invention, wherein: an auxiliary groove is opened inside the auxiliary pipe, a bottom port is laterally connected to the lower part of the auxiliary groove, and a top port is laterally connected to the top end, the outer ends of the auxiliary groove and the top port both extend outward and penetrate the valve core shaft, and the outer end of the bottom port abuts against the inner wall of the inner chamber, and the outer end of the top port is located below the converging groove.

[0016] As a preferred solution of the dual-pump converging hydraulic circuit combination valve described in the present invention, the electric control valve includes a flange pipe flanged to the lower end of the outer shell, a control module arranged on the outside of the flange pipe, and a valve plate arranged inside the flange pipe and controlled by the control module.

[0017] As a preferred solution of the dual-pump converging hydraulic circuit combination valve described in the present invention, a flow channel connected to the inner chamber is opened inside the flange pipe, the valve plate is arranged in the flow channel, and the lower end of the flow channel is connected to the hydraulic press oil suction system.

[0018] The beneficial effects of the present invention are as follows: by setting a cylindrical valve core unit, and enabling it to switch different hydraulic circuits by rotating and displacing inside the valve body, the on-off switching control between the circuits is realized, thereby realizing the confluence and liquid supply function of the small flow pump and the large flow pump, the independent liquid supply function of the small flow pump, and the simultaneous overflow function of the small flow pump and the large flow pump, so that the device has multiple functions, obtains the combination effect of multiple functions, and thus meets different usage requirements;

[0019] By integrating multiple functions, the volume of the entire control valve is reduced, saving the space and cost of installation. In addition, the on-off switching between different oil ports is realized by rotation, which avoids the impact and collision between parts, improves the protection of components, and increases the service life of the entire control valve.

[0020] By gradually rotating the valve core shaft to switch between different oil ports, the pressure shock caused by rapid opening and closing of the valve port can be effectively avoided, thereby improving the protection of the equipment, increasing the stability of the equipment during operation and extending its service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for describing the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work. Among them:

[0022] Figure 1 It is a schematic diagram of the overall structure of the dual-pump converging hydraulic circuit combination valve of the present invention.

[0023] Figure 2 It is an overall schematic diagram of the valve body unit of the dual-pump converging hydraulic circuit combination valve of the present invention.

[0024] Figure 3 It is a structural schematic diagram of the valve core unit of the dual-pump confluence hydraulic circuit combination valve of the present invention.

[0025] Figure 4 It is a schematic diagram of the internal structure of the valve core unit of the dual-pump converging hydraulic circuit combination valve of the present invention.

[0026] Figure 5 It is a schematic diagram of the maximum flow output state structure of the dual-pump confluence hydraulic circuit combination valve of the present invention.

[0027] Figure 6 It is a plan view of the internal structure of the dual-pump converging hydraulic circuit combination valve in the maximum flow state of the present invention.

[0028] Figure 7 It is a schematic diagram of the structure of the small flow output state of the dual-pump converging hydraulic circuit combination valve of the present invention.

[0029] Figure 8 It is a plan view of the internal structure of the dual-pump converging hydraulic circuit combination valve in the low-flow output state of the present invention.

[0030] Fig. 9 It is a schematic diagram of the overflow protection state structure of the dual-pump converging hydraulic circuit combination valve of the present invention.

[0031] Fig.10 It is a plan view of the internal structure of the double-pump converging hydraulic circuit combination valve in the overflow protection state of the present invention.

[0032] Fig.11 It is a schematic diagram of the structure of different rotation amplitudes of the valve plate of the dual-pump confluence hydraulic circuit combination valve of the present invention.

[0033] Reference numerals: 100, valve body unit; 101, housing; 101a, inner chamber; 101b, limit groove; 102, small liquid inlet pipe; 102a, small liquid inlet port; 102b, connecting pipe; 103, large liquid inlet pipe; 103a, large liquid inlet port; 104, reflux pipe; 104a, main reflux port; 104b, secondary reflux port; 200, valve core unit; 201, valve core shaft; 201a, top block; 20 2. Confluence groove; 202a, lower confluence end; 202b, upper confluence end; 203, auxiliary pipe; 203a, auxiliary groove; 203b, bottom opening; 203c, top opening; 204, limit ball; 300, adjustment unit; 301, threaded rod; 302, pressure plate; 303, spring; 400, electric control valve; 401, flange pipe; 401a, circulation channel; 402, control module; 403, valve plate. DETAILED DESCRIPTION

[0034] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the specific implementation methods of the present invention are described in detail below in conjunction with the accompanying drawings.

[0035] In the following description, many specific details are set forth to facilitate a full understanding of the present invention, but the present invention may also be implemented in other ways different from those described herein, and those skilled in the art may make similar generalizations without violating the connotation of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0036] Example 1

[0037] Reference Figures 1 to 11 , which is the first embodiment of the present invention, comprises: a dual-pump confluence hydraulic circuit combination valve, comprising,

[0038] The valve body unit 100 includes a shell 101 with a hollow interior, and a small liquid inlet pipe 102, a large liquid inlet pipe 103 and a return pipe 104 respectively arranged on three sides of the exterior of the shell 101, and the three are connected to the interior of the shell 101, and the small liquid inlet pipe 102, the large liquid inlet pipe 103 and the return pipe 104 are not at the same level; the small liquid inlet pipe 102, the large liquid inlet pipe 103 and the return pipe 104 are all fixedly connected to the shell 101, and the three can be connected to other external equipment through flanges or the like;

[0039] The valve core unit 200 includes a valve core shaft 201 located in the housing 101, and the valve core shaft 201 has a cylindrical structure, a confluence groove 202 spirally and obliquely opened on the valve core shaft 201, an auxiliary pipe 203 arranged inside the lower part of the valve core shaft 201, and both ends of the auxiliary pipe 203 pass through the valve core shaft 201 to communicate with the outside, and a limiting ball 204 arranged on the outer wall of the valve core shaft 201, and the position of the limiting ball 204 on the valve core shaft 201 is opposite to the confluence groove 202; the valve core shaft 201 is integrally plugged into the housing 101, and is limited in the horizontal direction of the housing 101, and can rotate in a circle in the housing 101, and the confluence groove 202, the auxiliary pipe 203 and the limiting ball 204 are all arranged on the valve core shaft 201, so the three will change their positions accordingly with the rotation of the valve core shaft 201;

[0040] The regulating unit 300 includes a threaded rod 301 which is vertically threadedly connected to the top of the housing 101, and the end of the threaded rod 301 extends into the housing 101, a pressure plate 302 is arranged at the end of the threaded rod 301, and a spring 303 is arranged below the pressure plate 302, and the end of the spring 303 abuts against the top of the valve core shaft 201; and an electric control valve 400 which is flange-connected to the bottom of the housing 101; the spring 303 is elastically supported between the pressure plate 302 and the top of the valve core shaft 201, and when the threaded rod 301 and the pressure plate 302 remain stationary, it will always apply downward pressure to the valve core shaft 201.

[0041] Furthermore, when the position of the valve core shaft 201 remains stationary, the position of the pressure plate 302 in the housing 101 can be changed by rotating the threaded rod 301. The position of the pressure plate 302 changes, while the position of the valve core shaft 201 remains unchanged, which will cause the pressure plate 302 to be squeezed and contracted, thereby generating a greater reaction force, thereby achieving the purpose of adjusting and controlling the elastic force of the spring 303, and achieving the purpose of adjusting the overall elastic pressure of the valve group according to different usage requirements, thereby better meeting different usage requirements.

[0042] Among them, the electric control valve 400 includes a flange pipe 401 flange-connected to the lower end of the shell 101, a control module 402 arranged on the outside of the flange pipe 401, and a valve plate 403 arranged inside the flange pipe 401 and controlled by the control module 402. The electric control valve 400 is an electric control valve in the existing mature technology. The flange pipe 401 can control the valve plate 403 to change the corresponding angle in the control module 402 according to the needs in the actual working process.

[0043] Furthermore, a circulation channel 401a connected to the inner chamber 101a is opened inside the flange tube 401, and a valve plate 403 is arranged in the circulation channel 401a. The lower end of the circulation channel 401a is connected to the hydraulic press oil suction system. The valve plate 403 is rotatably connected in the circulation channel 401a and can be rotated at different angles according to the control of the control module 402.

[0044] During use, combine Fig.11 , the valve plate 403 located in the circulation channel 401a, when it is in a vertical state in the circulation channel 401a, there is a large gap D between the two side edges of the valve plate 403 and the inner wall of the circulation channel 401a, when the valve plate 403 rotates in the circulation channel 401a, the distance between the valve plate 403 and the inner wall of the circulation channel 401a will be reduced accordingly, and the reduced distance is the spacing X. The gap D and the spacing X are both channels for liquid exchange between the inner chamber 101a and the circulation channel 401a; when the flow rate remains unchanged, reducing the exchange channel between the inner chamber 101a and the circulation channel 401a will make it impossible for the liquid in the inner chamber 101a to flow out quickly through the circulation channel 401a, and then the liquid will accumulate in the inner chamber 101a, increasing the pressure in the inner chamber 101a. It is inferred that the valve plate 403 rotates at different angles in the circulation channel 401a, which can apply different pressures to the inside of the inner chamber 101a, thereby meeting the pressure requirements of the hydraulic system in the actual working process.

[0045] Among them, an inner chamber 101a with a diameter matching the diameter of the valve core shaft 201 is opened inside the outer shell 101, and a spirally inclined limiting groove 101b is opened on the inner wall of the outer shell 101, and the limiting ball 204 is slidably connected in the limiting groove 101b. The limiting ball 204 is located in the limiting groove 101b so that the valve core shaft 201 as a whole is also limited by the limiting groove 101b, but the difference is that when the valve core shaft 201 rotates, it can slide along the spiral direction of the limiting groove 101b through the limiting ball 204 to offset the limitation from the limiting groove 101b. Therefore, when the valve core shaft 201 rotates in the inner chamber 101a, the whole moves in a spiral rotation and upward manner.

[0046] Among them, a small liquid inlet 102a connected to the inner warehouse 101a is opened inside the small liquid inlet pipe 102, and the outer end of the small liquid inlet 102a is connected to the outlet of the small flow pump, and an "L"-shaped connecting pipe 102b is opened below the small liquid inlet 102a, and the top and the end of the "L"-shaped structure are respectively connected to the small liquid inlet 102a and the inner warehouse 101a. The liquid transported into the small liquid inlet pipe 102 by the small flow pump can be transported into the inner warehouse 101a through the two channels of the small liquid inlet 102a and the inner warehouse 101a.

[0047] Among them, a large liquid inlet 103a connected to the inner chamber 101a is opened inside the large liquid inlet pipe 103, and the outer end of the large liquid inlet 103a is connected to the outlet of the large flow pump. The liquid transported by the large flow pump can be transported to the inner chamber 101a through the large liquid inlet 103a.

[0048] Among them, the two ends of the valve core shaft 201 are conical structures, and the top of the valve core shaft 201 is provided with a top block 201a for limiting the spring 303. The top block 201a limits the spring 303 at the top of the valve core shaft 201, so that it always maintains a vertical manner and applies downward pressure to the valve core shaft 201.

[0049] During use, the valve core shaft 201 is rotated as a whole and inserted into the inner chamber 101a. The valve core shaft 201 is located in the inner chamber 101a as a whole, and the valve core shaft 201 divides the inner chamber 101a into three parts. The uppermost part is used to provide a telescopic space for the valve core shaft 201 to move upward, and the lower part is used to accommodate the liquid delivered through the small liquid inlet pipe 102. Therefore, the liquid located in the lower end of the inner chamber 101a can transfer its own pressure to the valve core shaft 201 through contact with the bottom end of the valve core shaft 201, thereby achieving the purpose of pushing the valve core shaft 201 to spirally rise in the inner chamber 101a.

[0050] Among them, the confluence groove 202 is in a spiral inclined shape as a whole, and the spiral inclination angle is consistent with the limit groove 101b. The inner ends of the small liquid inlet 102a, the large liquid inlet 103a and the main reflux port 104a are all abutted on the spiral movement path of the confluence groove 202. The height of the confluence groove 202 in the horizontal direction is lower than the limit groove 101b. The end and top of the spiral structure of the confluence groove 202 are the lower confluence end 202a and the upper confluence end 202b respectively. The height of the confluence groove 202 is lower than the limit groove 101b, so that the confluence groove 202 will not overlap and connect with the limit groove 101b when it rotates following the valve core shaft 201.

[0051] During use, refer to Figure 5 and Figure 6When the hydraulic device needs to perform fast forward and fast reverse actions, the control module 402 controls the valve plate 403 to rotate to the position where the distance between the two sides and the inner wall of the flow channel 401a is the largest. At this time, the pressure in the inner chamber 101a is small, and the small pressure in the inner chamber 101a is applied to the end of the valve core shaft 201, but it is not enough to overcome the pressure applied by the spring 303, so the valve core shaft 201 remains stationary. At this time, the inner end of the small liquid inlet 102a is in contact with the lower confluence end 202a, and the large liquid inlet 101a is in contact with the lower confluence end 202a. The inner end of 03a is connected with a part of the confluence groove 202, and the liquid delivered by the large flow pump flows into the confluence groove 202 from the large liquid inlet 103a, and is guided to the small liquid inlet 102a through the confluence groove 202, while the small liquid inlet 102a is also delivered with the liquid delivered by the small flow pump. At this time, the liquids delivered by the two groups of flow pumps will merge through the connecting pipe 102b and be delivered into the inner chamber 101a, thereby achieving the maximum flow output, thereby meeting the action requirements of fast forward and fast reverse of the execution device;

[0052] During this process, the outer end of the auxiliary pipe 203 always abuts against the inner wall of the inner bin 101 a , and the upper confluence end 202 b at the top of the confluence groove 202 is not connected to the return pipe 104 .

[0053] Example 2

[0054] Reference Figure 7-8 , which is the second embodiment of the present invention. This embodiment is different from the first embodiment in that: the loop between the small liquid inlet pipe 102 and the large liquid inlet pipe 103 is disconnected, the large liquid inlet pipe 103 is connected with the reflux pipe 104, and the continuous output of the small liquid inlet pipe 102 is maintained to meet the small flow output demand.

[0055] Compared with Example 1, further, the return pipe 104 as a whole is two groups of pipes arranged in parallel up and down, and the two groups of pipes are respectively provided with a main return port 104a and a secondary return port 104b connected to the interior of the inner warehouse 101a, and the outer ends of the main return port 104a and the secondary return port 104b are connected to the return oil tank, and the liquid can be transported into the return oil tank via the main return port 104a and the secondary return port 104b.

[0056] Use process, combined Figure 7 and Figure 8When the hydraulic equipment needs to perform a working speed action, the control module 402 controls the valve plate 403 to rotate and reduces the distance between the two sides and the inner wall of the flow channel 401a. At this time, the pressure in the inner chamber 101a increases, and the inner chamber 101a will apply a larger pressure to the end of the valve core shaft 201. The larger pressure overcomes the pressure applied by the spring 303 to the valve core shaft 201, and thus pushes the valve core shaft 201 to move upward. The upward moving valve core shaft 201 will rise in a spiral rotation due to the cooperation and guidance of the limiting ball 204 and the limiting groove 101b. Due to the rotation of the valve core shaft 201, the position of the lower confluence end 202a changes and is no longer connected to the small liquid inlet 102a. The liquid inlet 103a and the main return port 104a are both on the spiral moving path of the confluence groove 202, so the large liquid inlet 103a will always maintain communication with the confluence groove 202, and as the valve core shaft 201 rises, the confluence groove 202 will make the upper confluence end 202b at its top communicate with the main return port 104a. At this time, the small liquid inlet 102a always keeps the liquid in the small flow pump being transported as usual through the connecting pipe 102b, and the liquid transported by the large flow pump through the large liquid inlet 103a will be guided through the confluence groove 202, and finally transported to the return oil tank through the upper confluence end 202b and the main return port 104a, thereby realizing a small flow output, and then realizing the action requirements of the hydraulic equipment to execute the working speed;

[0057] During this process, the auxiliary tube 203 follows the movement of the valve core shaft 201, and its position changes to a certain extent, but both ends of the auxiliary tube 203 are not connected to any of the small liquid inlet tube 102, the reflux tube 104 and the large liquid inlet tube 103, and both ends are abutted against the inner wall of the inner chamber 101a, so that the whole is in a closed state.

[0058] The remaining structures are the same as those of Example 1.

[0059] Example 3

[0060] Reference Figure 9-10 , which is the third embodiment of the present invention. This embodiment is different from the second embodiment in that when the pressure is overloaded, the small liquid inlet pipe 102, the large liquid inlet pipe 103 and the return pipe 104 are connected, and the oil output by the small flow pump and the oil output by the large flow pump flow out from the return pipe 104, thereby realizing the overflow protection function.

[0061] Compared with Example 2, further, an auxiliary groove 203a is opened inside the auxiliary pipe 203, and a bottom port 203b is laterally connected to the lower part of the auxiliary groove 203a, and a top port 203c is laterally connected to the top end. The outer ends of the auxiliary groove 203a and the top port 203c extend outward and penetrate the valve core shaft 201, and the outer end of the bottom port 203b abuts against the inner wall of the inner chamber 101a, and the outer end of the top port 203c is located below the confluence groove 202. The top port 203c is not connected to the confluence groove 202, and will not guide the liquid in the confluence groove 202 into the inner chamber 101a.

[0062] Use process, combined Fig.10 and Fig.11 When the pressure of the hydraulic equipment is too high, due to the continuous output of the large flow pump and the small flow pump, the circulation channel 401a is not enough to quickly discharge and release the pressure. The liquid in the inner chamber 101a will continue to increase the squeezing and pushing of the valve core shaft 201. At this time, the valve core shaft 201 continues to spiral upward, and the lower confluence end 202a will dock with the large liquid inlet 103a, and the main return port 104a will dock with the confluence groove 202. The auxiliary pipe 203 at the end of the valve core shaft 201 also spirals up with the valve core shaft 201. The bottom port 203b of the spirally rising auxiliary pipe 203 will dock with the small liquid inlet 102a. The top opening 203c at the top is connected to the secondary return port 104b, so that the liquid delivered by the small flow pump in the small liquid inlet 102a will be guided by the auxiliary pipe 203, and will be delivered to the return tank through the bottom opening 203b, the auxiliary groove 203a and the secondary return port 104b in sequence, and will not be additionally delivered to the inner warehouse 101a, thereby relieving the pressure in the inner warehouse 101a, and the liquid delivered by the large flow pump in the large liquid inlet 103a will also be delivered to the return tank through the confluence groove 202 and the main return port 104a. Therefore, the overflow protection function of the liquid output by the double pump can be realized through the above operation;

[0063] Furthermore, no matter it is the maximum flow output action, the small flow output action or the overflow protection action, the above three operations are all achieved by switching the opening and closing and the on-off of different oil ports through the valve core shaft 201 in the process of gradual rotation and rising. Compared with the direct and rapid opening and closing in the prior art, it can effectively reduce the pressure shock, thereby improving the protection of the equipment, increasing the stability of the equipment during operation and extending its service life.

[0064] The remaining structure is the same as that of Example 2.

[0065] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention rather than to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solutions of the present invention may be modified or replaced by equivalents without departing from the spirit and scope of the technical solutions of the present invention, which should all be included in the scope of the claims of the present invention.

Claims

1. A dual-pump confluence hydraulic circuit combination valve, characterized in that: include, The valve body unit (100) comprises an outer shell (101) with a hollow interior, and a small liquid inlet pipe (102), a large liquid inlet pipe (103) and a return pipe (104) respectively arranged on three sides of the outer shell (101), and the three are connected to the interior of the outer shell (101), and the small liquid inlet pipe (102), the large liquid inlet pipe (103) and the return pipe (104) are not at the same level; An inner chamber (101a) having a diameter matching that of the valve core shaft (201) is provided inside the outer shell (101), a spirally inclined limiting groove (101b) is provided on the inner wall of the outer shell (101), and a limiting ball (204) is slidably connected in the limiting groove (101b); The valve core unit (200) comprises a valve core shaft (201) located in a housing (101), the valve core shaft (201) being of cylindrical structure, a confluence groove (202) being spirally inclinedly provided on the valve core shaft (201), an auxiliary pipe (203) being provided inside the lower part of the valve core shaft (201), and both ends of the auxiliary pipe (203) passing through the valve core shaft (201) to communicate with the outside, and a limiting ball (204) being provided on the outer wall of the valve core shaft (201), and the limiting ball (204) being located on the valve core shaft (201) at a position opposite to the confluence groove (202); The confluence groove (202) is in an overall spirally inclined shape, and the spiral inclination angle is consistent with the limiting groove (101b); the height of the confluence groove (202) in the horizontal direction is lower than the limiting groove (101b); the end and top of the spiral structure of the confluence groove (202) are respectively a lower confluence end (202a) and an upper confluence end (202b); The regulating unit (300) comprises a threaded rod (301) vertically threadedly connected to the top of the housing (101), the end of the threaded rod (301) extending into the housing (101), a pressure plate (302) arranged at the end of the threaded rod (301), and a spring (303) arranged below the pressure plate (302), the end of the spring (303) abutting against the top of the valve core shaft (201); and an electric control valve (400) flange-connected to the bottom of the housing (101).

2. The dual-pump confluence hydraulic circuit combination valve according to claim 1, characterized in that: The small liquid inlet pipe (102) is provided with a small liquid inlet (102a) in communication with the inner bin (101a); the outer end of the small liquid inlet (102a) is connected to the outlet of a small flow pump; a connecting pipe (102b) with an "L"-shaped structure is provided below the small liquid inlet (102a); and the top and the end of the "L"-shaped structure are respectively connected to the small liquid inlet (102a) and the inner bin (101a).

3. The dual-pump confluence hydraulic circuit combination valve according to claim 2, characterized in that: The large liquid inlet pipe (103) is provided with a large liquid inlet (103a) in communication with the inner chamber (101a), and the outer end of the large liquid inlet (103a) is in communication with the outlet of the large flow pump.

4. The dual-pump confluence hydraulic circuit combination valve according to claim 3 is characterized in that: The return pipe (104) as a whole is composed of two groups of pipes arranged in parallel up and down, and the two groups of pipes are respectively provided with a main return port (104a) and a secondary return port (104b) connected to the interior of the inner bin (101a), and the outer ends of the main return port (104a) and the secondary return port (104b) are connected to the oil return tank.

5. The dual-pump confluence hydraulic circuit combination valve according to claim 1, characterized in that: Both ends of the valve core shaft (201) are in a conical structure, a top block (201a) for a limit spring (303) is provided at the top end of the valve core shaft (201), and the valve core shaft (201) is integrally rotatably inserted into the inner chamber (101a).

6. The dual-pump confluence hydraulic circuit combination valve according to claim 4, characterized in that: The inner ends of the small liquid inlet (102a), the large liquid inlet (103a) and the main reflux port (104a) are all in contact with the spiral motion path of the confluence groove (202).

7. The dual-pump confluence hydraulic circuit combination valve according to claim 1, characterized in that: An auxiliary groove (203a) is provided inside the auxiliary pipe (203), the lower part of the auxiliary groove (203a) is laterally connected to a bottom opening (203b), and the top end is laterally connected to a top opening (203c), the outer ends of the auxiliary groove (203a) and the top opening (203c) both extend outwards and penetrate the valve core shaft (201), and the outer end of the bottom opening (203b) abuts against the inner wall of the inner chamber (101a), and the outer end of the top opening (203c) is located below the confluence groove (202).

8. The dual-pump confluence hydraulic circuit combination valve according to claim 1, characterized in that: The electrically controlled valve (400) comprises a flange pipe (401) flange-connected to the lower end of the housing (101), a control module (402) arranged outside the flange pipe (401), and a valve plate (403) arranged inside the flange pipe (401) and controlled by the control module (402).

9. The dual-pump confluence hydraulic circuit combination valve according to claim 8, characterized in that: The flange pipe (401) is provided with a circulation channel (401a) in communication with the inner chamber (101a). The valve plate (403) is arranged in the circulation channel (401a). The lower end of the circulation channel (401a) is in communication with the hydraulic press oil extraction system.

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