Threaded plug-in type adjustable flow distributing and collecting valve

Abstract

The invention relates to the technical field of synchronous valves, in particular to a threaded plug-in type adjustable flow distributing and collecting valve which comprises a valve body, a plurality of main oil way holes are formed in the valve body and located in the middle of the valve body, and the threaded plug-in type adjustable flow distributing and collecting valve further comprises a first throttling hole and a second throttling hole which are formed in the valve body. The two first throttling holes and the two second throttling holes are located in the two sides of the main oil way hole correspondingly, linkage is achieved through all parts of the valve element assembly, the two-way flow is automatically balanced when the pressure difference is small, the pressure is dynamically compensated through a conical hole of the synchronizing mechanism and an electric control valve when the pressure difference is large, and the situation that under the high-load operation condition, the pressure difference is large is greatly reduced. The pressure difference between the two sides of the first valve element and the second valve element; when the bimetallic compensation ring is in a low-temperature state (lower than 40 DEG C), a gap between the V-shaped groove and the corresponding first valve core or the second valve core is increased, so that the device is prevented from being blocked during cold start; and in a high-temperature state (higher than 80 DEG C), a gap of a sealing surface is reduced, and leakage is avoided.

Description

Technical Field

[0001] This invention relates to the field of synchronization valve technology, specifically to a threaded cartridge adjustable diverter / combiner valve. Background Technology

[0002] As a core component of hydraulic synchronization control systems, flow divider / combiner valves are widely used in fields such as construction machinery and metallurgical equipment where multiple actuators need to work together. They achieve synchronous movement of hydraulic cylinders / motors by evenly distributing or combining oil flow. Traditional threaded cartridge flow divider / combiner valves mostly use a fixed throttling orifice structure combined with valve core displacement compensation for synchronous adjustment. However, in practical applications, the following significant drawbacks have been found: Firstly, the synchronization accuracy of existing structures relies excessively on machining precision. Because dimensional tolerances (typically ±0.02mm) are unavoidable during the manufacturing process of fixed throttling orifices, when the load pressure difference between the two working oil circuits exceeds 3MPa, the coupling effect of the asymmetric hydraulic forces on both sides of the valve core and the spring preload deviation will cause the flow difference to expand exponentially. Experimental data shows that under pressure differences of up to 8MPa, the synchronization error can reach 10%-15%, severely restricting the dynamic response performance of high-precision synchronization systems.

[0003] Secondly, traditional valve body-spool assemblies are not adaptable to wide temperature range conditions. The valve spool and valve body are often made of the same metal material (such as 40Cr steel and copper alloy valve sleeves). During cold starts in low-temperature environments below 40℃, the metal contraction effect causes the mating clearance to shrink to 3-6μm. At this time, the elastic modulus of the nitrile rubber sealing ring increases to 2-3 times that at room temperature, and the valve spool starting torque increases by more than 60%, easily causing movement jamming. In high-temperature conditions above 80℃, the radial expansion of the valve body can reach 1.3-1.8 times that at low temperatures. The increased mating clearance leads to an abnormally high internal leakage, with the cross-leakage between the two working chambers reaching 12%-18% of the rated flow, and the synchronization accuracy decreasing by more than 20%.

[0004] Based on the above-mentioned shortcomings, we propose a threaded cartridge adjustable diverter / combiner valve. Summary of the Invention

[0005] To solve the above-mentioned technical problems, the present invention provides a threaded cartridge type adjustable flow divider / combiner valve, including a valve body, on which a main oil passage is formed, having multiple main oil passages located in the middle of the valve body, and further including a first throttling orifice and a second throttling orifice formed on the valve body, the first throttling orifice and the second throttling orifice being located on both sides of the main oil passage, and having two of each, and further including: A valve core assembly is installed inside the valve body. When the pressure difference between the first throttling orifice and the second throttling orifice is small, hydraulic oil of the same flow rate is drawn out or injected into the first throttling orifice and the second throttling orifice respectively. A synchronization mechanism is installed inside the valve body to compensate for the hydraulic oil pressure on the side with greater pressure when there is a large pressure difference between the two sets of first throttling orifices.

[0006] Preferably, the valve core assembly includes a first fixed cylinder installed in the valve body near the hand-held end. A first spring is installed on the inner wall of the first fixed cylinder near the main oil passage. A first valve core is slidably installed in the valve body. The first valve core is cylindrical. One end of the first spring is fixed to the first fixed cylinder, and the other end is fixed to the inner wall of the first valve core near the first fixed cylinder. The first valve core has a third throttling orifice and a first damping orifice. The third throttling orifice overlaps with the first throttling orifice. The first damping orifice is located between the third throttling orifice and the main oil passage. The valve core assembly also includes a second fixed cylinder installed in the valve body. A second valve core is slidably installed in the valve body. The second valve core has the same shape as the first valve core and is connected to the second fixed cylinder by a second spring. The second valve core has a fourth throttling orifice and a second damping orifice. The fourth throttling orifice and the second throttling orifice overlap. The second damping orifice is located between the fourth throttling orifice and the main oil passage. The number of the third throttling orifice, the fourth throttling orifice, the first damping orifice, and the second damping orifice are all equal to the number of the first throttling orifice.

[0007] Preferably, the valve core assembly further includes a fixed cover installed on the side of the first valve core near the main oil passage, a support rod installed on the side of the second valve core near the main oil passage, a slider fixed at the end of the support rod away from the second valve core, the slider being located on the inner wall of the fixed cover and the two being slidably connected, and a third spring sleeved on the fixed cover, the two ends of the third spring being fixed to one side of the first valve core and the second valve core respectively.

[0008] Preferably, there are two synchronization mechanisms with identical structures, including a pipe connecting the two third throttling orifices, a square block fixed on the pipe, a groove on the square block communicating with the pipe, and four conical holes on the square block arranged in a straight line. The first two and the last two conical holes face opposite directions, and a guide plate is fixed inside each conical hole in a spiral arrangement. A through hole is provided on the square block, and the through hole is aligned with the four conical holes. The other synchronization mechanism is located near the second valve core, with the center point of the main oil passage forming a planar mirror image. The synchronization mechanism also includes a conversion component.

[0009] Preferably, the conversion element includes an electrically controlled valve mounted opposite to the groove, wherein a single electrically controlled valve can only block two conical holes or one through hole at a time.

[0010] Preferably, both the first valve core and the second valve core have annular grooves on their surfaces, and there are multiple annular grooves.

[0011] Preferably, all first and second valve cores are fitted with sealing components. The sealing components increase the sealing between the first valve core, the second valve core and the inner wall of the valve body according to different ambient temperatures. The sealing components include bimetallic compensation rings fitted on the first and second valve cores respectively, and the outer metal expansion coefficient is higher than that of the inner layer. The overall shape is "⊥".

[0012] Preferably, the outer layer of the bimetallic compensation ring is a manganese-copper alloy layer with a thickness of 0.8 mm, and the inner layer is an Invar alloy layer with a thickness of 1.5 mm. Both are formed by explosive welding, and V-shaped grooves are formed on both the outer and inner walls of the bimetallic compensation ring, with a fluororubber pad filling the V-shaped groove on the inner wall.

[0013] The present invention has at least the following beneficial effects: 1. Through the linkage of various components of the valve core assembly, this device automatically balances the two flow paths when the pressure difference is small, and dynamically compensates the pressure through the conical orifice of the synchronization mechanism and the solenoid valve when the pressure difference is large, which greatly reduces the pressure difference between the first valve core and the second valve core under high load operation. 2. When the bimetallic compensation ring is in a low temperature state (below 40℃), the inner layer of Invar alloy shrinks mainly, the ring body shrinks radially inward, and the gap between the V-groove and the corresponding first valve core or second valve core increases, so as to avoid jamming when the device is cold-started. At high temperatures (above 80°C), the outer manganese-copper alloy expands much more than the inner layer. When heated, the ring expands radially outward, squeezing the fluororubber gasket in the V-groove, thus reducing the gap between the sealing surfaces and preventing leakage. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram of the first cross-sectional structure inside the present invention; Figure 3 This is a schematic diagram of the internal second cross-section structure of the present invention; Figure 4 This is a schematic diagram of the internal third cross-section structure of the present invention; Figure 5 This is a schematic diagram of the cross-sectional structure of the bimetallic compensation ring of the present invention; Figure 6 This is a schematic diagram of the cross-sectional structure of the present invention under the current collection state; Figure 7 This is a schematic diagram of the cross-sectional structure under the flow splitting state of the present invention.

[0015] In the diagram: 1. Valve body; 11. Main oil passage hole; 12. First throttling orifice; 13. Second throttling orifice; 3. Valve core assembly; 31. First fixed cylinder; 32. First spring; 33. First valve core; 34. Third throttling orifice; 35. First damping orifice; 36. Second fixed cylinder; 37. Second spring; 38. Second valve core; 39. Fourth throttling orifice; 310. Second damping orifice; 311. Fixed cover; 312. Support rod; 313. Slider; 314. Third spring; 4. Synchronization mechanism; 41. Through pipe; 42. Square block; 43. Groove; 44. Conical hole; 45. Guide plate; 46. Through hole; 47. Conversion component; 471. Electrically controlled valve; 5. Annular groove; 6. Bimetallic compensation ring; 61. Manganese-copper alloy layer; 62. Invar alloy layer; 63. V-groove; 64. Fluororubber pad. Detailed Implementation

[0016] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0017] Example 1: Please see Figures 1-7 This invention provides a technical solution: a threaded cartridge type adjustable flow divider / combiner valve, comprising a valve body 1, wherein the valve body 1 has multiple main oil passage holes 11 located in the middle of the valve body 1, and further comprising a first throttling hole 12 and a second throttling hole 13 formed on the valve body 1, wherein the first throttling hole 12 and the second throttling hole 13 are respectively located on both sides of the main oil passage holes 11, and there are two of each, and further comprising: Valve core assembly 3 is installed inside valve body 1. When the pressure difference between the first throttling orifice 12 and the second throttling orifice 13 is small, hydraulic oil of the same flow rate is drawn out or injected into the first throttling orifice 12 and the second throttling orifice 13 respectively. Synchronization mechanism 4 is installed inside valve body 1 and is used to compensate the hydraulic oil pressure on the side with greater pressure when the pressure difference between the two sets of first throttle orifices 12 is large.

[0018] The valve core assembly 3 includes a first fixed cylinder 31 installed inside the valve body 1 near the hand-held end. A first spring 32 is installed on the inner wall of the first fixed cylinder 31 near the main oil passage 11. A first valve core 33 is slidably installed inside the valve body 1. The first valve core 33 is cylindrical. One end of the first spring 32 is fixed to the first fixed cylinder 31, and the other end is fixed to the inner wall of the first valve core 33 near the first fixed cylinder 31. A third throttling orifice 34 and a first damping orifice 35 are engaged on the first valve core 33. The third throttling orifice 34 overlaps with the first throttling orifice 12, and the first damping orifice 35 is located between the third throttling orifice 34 and the main oil passage 11. The valve core assembly 3 further includes a second fixed cylinder 36 installed inside the valve body 1. A second valve core 38 is slidably installed inside the valve body 1. The second valve core 38 has the same shape as the first valve core 33 and is connected to the second fixed cylinder 36 by a second spring 37. The second valve core 38 has a fourth throttling hole 39 and a second damping hole 310. The fourth throttling hole 39 and the second throttling hole 13 overlap. The second damping hole 310 is located between the fourth throttling hole 39 and the main oil passage hole 11. The number of the third throttling hole 34, the fourth throttling hole 39, the first damping hole 35, and the second damping hole 310 are all equal to the number of the first throttling hole 12.

[0019] For ease of understanding, such as Figure 6 , 7 As shown, the first damping orifice 35 and the second damping orifice 310 are fixed throttle ports in this valve, and the hydraulic oil pressures at these positions are P1 and P2, respectively. The first throttle orifice 12 and the third throttle orifice 34, the second throttle orifice 13 and the fourth throttle orifice 39 respectively form two variable throttle ports, and the hydraulic oil pressures at these positions are P3 and P4, respectively. The hydraulic oil pressure at the main oil passage port 11 is P0.

[0020] The valve core assembly 3 also includes a fixed cover 311 installed on the side of the first valve core 33 near the main oil passage 11. A support rod 312 is installed on the side of the second valve core 38 near the main oil passage 11. A slider 313 is fixed to the end of the support rod 312 away from the second valve core 38. The slider 313 is located on the inner wall of the fixed cover 311 and the two are slidably connected. A third spring 314 is sleeved on the fixed cover 311. The two ends of the third spring 314 are fixed to one side of the first valve core 33 and the second valve core 38, respectively.

[0021] The sliding arrangement of slider 313 and fixed cover 311 ensures the relative position of the first valve core 33 and the second valve core 38. During the movement of the first valve core 33 and the second valve core 38, the states (expansion or contraction) of P3 and P4 are opposite.

[0022] There are two synchronization mechanisms 4 with identical structures. One includes a pipe 41 connecting the two third throttling holes 34. A square block 42 is fixed on the pipe 41. The square block 42 has a groove 43 connected to the pipe 41. The square block 42 has four conical holes 44 arranged in a straight line. The first two conical holes 44 and the last two conical holes 44 face opposite directions. A guide plate 45 is fixed inside each conical hole 44. The guide plates 45 are arranged in a spiral. The square block 42 has a through hole 46. The through hole 46 and the four conical holes 44 are on the same straight line. The other synchronization mechanism 4 is distributed near the second valve core 38 in a plane mirror image formed by the center point of the main oil passage hole 11. The synchronization mechanism 4 also includes a conversion element 47.

[0023] The conversion component 47 includes an electrically controlled valve 471 installed relative to the groove 43. A single electrically controlled valve 471 can only block two conical holes 44 or one through hole 46 at a time. It can block two adjacent conical holes 44 and a single through hole 46 according to different pressure changes in the valve body 1. When the pressure difference between the corresponding sides of the first valve core 33 and the second valve core 38 is large, it can reduce the pressure difference and improve the accuracy of equipment operation.

[0024] The first valve core 33 and the second valve core 38 are both provided with annular grooves 5, and there are multiple annular grooves 5. The annular grooves 5 can effectively reduce the friction force experienced by the first valve core 33 and the second valve core 38 when sliding in the valve body 1, and reduce the error range of the device.

[0025] All first valve cores 33 and second valve cores 38 are fitted with sealing components. The sealing components increase the sealing between the first valve core 33, the second valve core 38 and the inner wall of the valve body 1 according to different ambient temperatures. The sealing components include bimetallic compensation rings 6 respectively fitted on the first valve core 33 and the second valve core 38, and the outer metal expansion coefficient is higher than that of the inner layer. The whole is shaped like a "⊥".

[0026] The outer layer of the bimetallic compensation ring 6 is a manganese-copper alloy layer 61 with a thickness of 0.8 mm, and the inner layer is an Invar alloy layer 62 with a thickness of 1.5 mm. The two are formed by explosive welding, and both the outer and inner walls of the bimetallic compensation ring 6 are provided with V-grooves 63, with the V-grooves 63 on the inner wall filled with fluororubber pads 64.

[0027] The coefficient of thermal expansion of manganese-copper alloy layer 61 is (α=20×10⁻). 6 / ℃) is much higher than that of Invar alloy layer 62 (α=1.2×10⁻ 6In low-temperature operating environments (below 40℃), the inner layer of the bimetallic compensation ring 6, dominated by the shrinkage of the Invar alloy layer 62, contracts radially inward, increasing the gap between the V-groove 63 and the corresponding first valve core 33 or second valve core 38, thus preventing start-up jamming. However, once the operating environment temperature rises (above 80℃), the bimetallic compensation ring 6 expands radially outward after being heated, squeezing the fluororubber gasket 64 inside the V-groove 63, thus reducing the gap between the sealing surfaces and preventing leakage.

[0028] The working principle of this invention is as follows: The core control components of this device are symmetrical, and the connecting component between the first valve core 33 and the second valve core 38 is a sliding connection and is constrained by the third spring 314. The variable throttling ports P3 and P4 are always in the open state, but the size of the opening will change with the pressure. That is, when the pressure difference between the fixed throttling ports P1 and P2 is equal, the flow rate will be equal synchronously. Therefore: Collection status: like Figure 6 As shown, the pressure at inlet P3 and P4 is greater than the pressure at outlet P0, and the first valve core 33 and the second valve core 38 are squeezed, thereby driving the slider 313 to slide inside the fixed cover 311, and finally sticking tightly to one side of the first valve core 33. When the difference between P3 and P4 is small (set according to the actual application scenario and the pressure value detected by the pressure detection system), the two solenoid valves 471 block the four conical holes 44, and the hydraulic oil is drawn into the main oil passage hole 11 through the through hole 46, without compensating for P2 or P1. At this time, two situations will occur: 1. When the load is the same: P3=P4, that is, P1=P2, the pressure difference before and after the left and right fixed throttling orifices is the same, and the flow rate is the same.

[0029] 2. When the load is different: Assuming that P4 is greater than P3, that is, P2 is greater than P1, the first valve core 33 and the second valve core 38 move to the left, the right variable throttle orifice becomes smaller, and the left variable throttle orifice becomes larger. After the right throttle orifice becomes smaller, the pressure of P2 decreases. When the pressure of P2 equals the pressure of P1, the valve core stops moving, and the pressure difference between the front and back of the fixed throttle orifices on both sides remains consistent, that is, the flow rate on both sides is the same.

[0030] When the difference between P3 and P4 exceeds the set value: assuming P4 is greater than P3, that is, P2 is greater than P1, the first valve core 33 and the second valve core 38 move to the left, the right variable throttle orifice becomes smaller, and the left variable throttle orifice becomes larger. After the right throttle orifice becomes smaller, the pressure of P2 decreases. The solenoid valve 471 on the P1 side blocks the through hole 46 on the corresponding side and the two tapered holes 44 that become narrower along the direction of hydraulic oil flow. The solenoid valve 471 on the P2 side blocks the through hole 46 on the corresponding side and the two tapered holes 44 that become wider along the direction of hydraulic oil flow. At this time, the tapered holes 44 on P1 and P2 respectively form a high resistance compensation channel and a low resistance acceleration channel, forming a self-balancing flow distribution to reduce the error value.

[0031] During traffic splitting: like Figure 7 As shown, the pressure at the inlet P0 is greater than the pressure at the outlets P3 and P4. Under the action of the pressure at P0, the first valve core 33 and the second valve core 38 separate to the left and right, and finally the slider 313 and the fixed cover 311 are attached to the inner wall away from the first valve core 33.

[0032] When the load is the same: P3=P4, that is, P1=P2, the pressure difference before and after the left and right fixed throttling orifices is the same, and the flow rate is the same.

[0033] When the loads are different: Assuming P4 is greater than P3, that is, P2 is greater than P1, the valve core moves to the left, the variable throttle orifice on the left becomes smaller, and the throttle orifice on the right becomes larger, the pressure of P1 increases. When the pressure of P1 increases to the pressure of P2, the valve core is in a balanced state. Since P1=P2, the pressure difference before and after the fixed throttle orifices on the left and right sides is constant, that is, the flow rates on both sides are the same.

[0034] Similarly, when the difference between P3 and P4 exceeds the set value, the solenoid valve 471 blocks the corresponding conical orifice 44 or through orifice 46 to achieve self-balancing flow distribution.

[0035] It should be noted that, in this document, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, article, or apparatus.

[0036] Although embodiments of the invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A threaded cartridge type adjustable diverter valve, comprising a valve body (1), wherein the valve body (1) has a main oil passage hole (11), there are multiple main oil passage holes (11) located in the middle of the valve body (1), and further comprising a first throttling hole (12) and a second throttling hole (13) opened on the valve body (1), wherein the first throttling hole (12) and the second throttling hole (13) are respectively located on both sides of the main oil passage hole (11), and there are two of each, characterized in that: Also includes: Valve core assembly (3), which is installed inside the valve body (1), when the pressure difference between the first throttle hole (12) and the second throttle hole (13) is small, hydraulic oil of the same flow rate is drawn out or injected into the first throttle hole (12) and the second throttle hole (13) respectively. Synchronization mechanism (4) is installed inside the valve body (1) and is used to compensate the hydraulic oil pressure on the side with greater pressure when the pressure difference between the two sets of first throttle holes (12) is large.

2. The threaded cartridge type adjustable diverter / combiner valve according to claim 1, characterized in that: The valve core assembly (3) includes a first fixed cylinder (31) installed inside the valve body (1) near the hand-held end. A first spring (32) is installed on the inner wall of the first fixed cylinder (31) near the main oil passage (11). A first valve core (33) is slidably installed inside the valve body (1). The first valve core (33) is cylindrical. One end of the first spring (32) is fixed to the first fixed cylinder (31), and the other end is fixed to the inner wall of the first valve core (33) near the first fixed cylinder (31). A third throttling hole (34) and a first damping hole (35) are clamped on the first valve core (33). The third throttling hole (34) overlaps with the first throttling hole (12), and the first damping hole (35) is located between the third throttling hole (34) and the main oil passage (11). The valve core assembly (3) further includes a second fixed cylinder (36) installed in the valve body (1). A second valve core (38) is slidably installed in the valve body (1). The second valve core (38) has the same shape as the first valve core (33) and is connected to the second fixed cylinder (36) by a second spring (37). A fourth throttling hole (39) and a second damping hole (310) are provided on the second valve core (38). The fourth throttling hole (39) and the second throttling hole (13) overlap. The second damping hole (310) is located between the fourth throttling hole (39) and the main oil passage hole (11). The number of the third throttling hole (34), the fourth throttling hole (39), the first damping hole (35), and the second damping hole (310) are all equal to the number of the first throttling hole (12).

3. A threaded cartridge-type adjustable diverter / combiner valve according to claim 2, characterized in that: The valve core assembly (3) also includes a fixed cover (311) installed on the side of the first valve core (33) near the main oil passage (11). A support rod (312) is installed on the side of the second valve core (38) near the main oil passage (11). A slider (313) is fixed at the end of the support rod (312) away from the second valve core (38). The slider (313) is located on the inner wall of the fixed cover (311) and the two are slidably connected. A third spring (314) is sleeved on the fixed cover (311). The two ends of the third spring (314) are fixed to the side of the first valve core (33) and the second valve core (38) respectively.

4. A threaded cartridge-type adjustable diverter / combiner valve according to claim 3, characterized in that: There are two synchronization mechanisms (4) with the same structure. One includes a pipe (41) that connects the two third throttling holes (34). A square block (42) is fixed on the pipe (41). The square block (42) has a groove (43) that is connected to the pipe (41). The square block (42) has a conical hole (44). There are four conical holes (44) that are arranged in a straight line. The first two conical holes (44) and the last two conical holes (44) are oriented in opposite directions. A guide plate (45) is fixed inside each conical hole (44). The guide plate (45) is arranged in a spiral. A through hole (46) is opened on the square block (42). The through hole (46) and the four conical holes (44) are on the same straight line. The other synchronization mechanism (4) is arranged in a plane mirror image formed by the center point of the main oil passage hole (11) near the second valve core (38). The synchronization mechanism (4) also includes a conversion component (47).

5. A threaded cartridge-type adjustable diverter / combiner valve according to claim 4, characterized in that: The conversion element (47) includes an electrically controlled valve (471) mounted relative to the groove (43), and a single electrically controlled valve (471) can only block two conical holes (44) or one through hole (46) at a time.

6. A threaded cartridge-type adjustable diverter / combiner valve according to claim 5, characterized in that: The first valve core (33) and the second valve core (38) are both provided with annular grooves (5), and there are multiple annular grooves (5).

7. A threaded cartridge-type adjustable diverter / combiner valve according to claim 6, characterized in that: All first valve cores (33) and second valve cores (38) are fitted with sealing components. The sealing components increase the sealing between the first valve core (33), the second valve core (38) and the inner wall of the valve body (1) according to different ambient temperatures. The sealing components include bimetallic compensation rings (6) fitted on the first valve core (33) and the second valve core (38) respectively. The outer metal expansion coefficient is higher than that of the inner layer, and the whole is in the shape of "⊥".

8. A threaded cartridge-type adjustable diverter / combiner valve according to claim 7, characterized in that: The outer layer of the bimetallic compensation ring (6) is a manganese copper alloy layer (61) with a thickness of 0.8 mm, and the inner layer is an Invar alloy layer (62) with a thickness of 1.5 mm. The two are formed by explosive welding. The outer and inner walls of the bimetallic compensation ring (6) are provided with V-shaped grooves (63), and the V-shaped grooves (63) on the inner wall are filled with fluororubber pads (64).

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