Dual-flapper structure two-way actuator and closed-cycle full-flow staged combustion engine

Abstract

The present invention relates to a two-way actuator with a dual-valve structure and a closed-cycle full-flow staged combustion engine, and belongs to the field of rocket engines. A valve cavity is provided inside a valve body. One end of the valve body has an inlet, and the other end has an outlet. Both the inlet and the outlet are communicated with the valve cavity. A small valve core, a first spring, a guide sleeve, a second spring, and a large valve core are sequentially abutted and arranged inside the valve cavity. The guide sleeve is fixedly sealed with the valve cavity and has a flow-through hole penetrating through both ends thereof. One end of the small valve core is in sealed abutment or separation with the inlet, and one end of the large valve core is in sealed abutment or separation with the guide sleeve. The large valve core has a large valve core through-hole penetrating through both ends thereof. This two-way actuator has functions of being opened at low pressure in the forward direction, being sealed at low pressure in the reverse direction, and being sealed at high pressure in the reverse direction, and also has unidirectional sealing functions at high and low pressures, simplifies the engine system, reduces the types of valves, and is more conducive to the overall assembly layout of the engine.

Description

Technical Field

[0001] The present invention relates to the field of rocket engines, and particularly to a two-way automatic device with a double-valve structure and a closed-cycle full-flow staged combustion engine. Background Art

[0002] With the increasingly fierce competition in space technology, the research and development of closed-cycle full-flow staged combustion engines are accelerating at home and abroad. The most typical foreign example is the Raptor engine of SpaceX, which has completed flight tests in cooperation with the Starship. At present, domestic engines have completed the scaled heat test research on multi-nozzles in the thrust chamber and oxygen-rich / fuel-rich gas generators. The closed-cycle full-flow staged combustion engine has key technologies such as high thrust, high coupling, deep thrust variation, multiple starts, and reusability, providing strong power support for reusable launch vehicles and having broad application prospects.

[0003] The closed-cycle full-flow staged combustion engine has the characteristics of high chamber pressure and high performance. High chamber pressure means that engine components (valves, thrust chambers, turbopumps) need to work properly under relatively high pressures. Ensuring dynamic and static seals under high pressure is a design difficulty for each component. Overcoming the sealing problem under high and low pressures is the basis for developing a high-performance full-flow staged combustion cycle scheme.

[0004] At present, the working pressure of the open-cycle fuel-rich liquid oxygen methane engines in service in China is not high, with a maximum working pressure of about 18 MPa. A purge check valve with a single-seal and heat-pressed fluoroplastic structure can meet the working requirements under this pressure. The maximum working pressure of the closed-cycle full-flow staged combustion engine reaches 60 MPa, and the working pressure is relatively high. The purge check valve works throughout the engine purge, cycle pre-cooling, and main engine operation processes, and should have the functions of forward opening at a low purge pressure of 0.2 MPa, reverse closing at a low cycle pre-cooling pressure of 0.4 MPa, and reverse closing at a high main engine working pressure of 60 MPa. Existing check valves cannot meet the requirements of relatively high working pressures. Therefore, ensuring opening and reverse sealing within a wide pressure range becomes a research and development difficulty for the purge check valve. Summary of the Invention

[0005] The technical problem to be solved by the present invention is how to meet the requirements of one-way opening and high and low pressure reverse closing seals under a wide pressure range. The two-way automatic device with a double-valve structure of the present invention is used in the processes of engine purge, cycle pre-cooling, and main engine operation, and is a cryogenic high-pressure two-way automatic device with advantages such as a double-valve seat structure and high and low pressure sealing.

[0006] The technical solution of the present invention to solve the above technical problems is as follows: A two-way actuator with a dual-valve structure includes a valve body, a small valve core, a guide sleeve, a large valve core, a first spring, and a second spring. There is a valve cavity inside the valve body. One end of the valve body has an inlet, and the other end has an outlet. Both the inlet and the outlet are communicated with the valve cavity. The small valve core, the first spring, the guide sleeve, the second spring, and the large valve core are sequentially abutted and arranged in the valve cavity. The guide sleeve is fixedly sealed with the valve cavity and has a flow-through hole penetrating through both ends thereof. One end of the small valve core is in sealed abutment or separation with the inlet, and one end of the large valve core is in sealed abutment or separation with the guide sleeve. The large valve core has a large valve core through-hole penetrating through both ends thereof.

[0007] The beneficial effects of the present invention are: The two-way actuator with a dual-valve structure is a two-way actuator with a dual-valve seat structure, which has the advantages of a wide working pressure range, reliable operation, and simplified engine system, and works throughout the whole process of engine purging, cycle precooling, main engine operation, and shutdown.

[0008] This two-way actuator has the functions of opening at low pressure in the forward direction, sealing at low pressure in the reverse direction, and sealing at high pressure in the reverse direction, and has both high-pressure and low-pressure one-way sealing functions, simplifies the engine system, reduces the types of valves, and is more conducive to the overall assembly layout of the engine.

[0009] Specifically, during engine purging, a low-pressure medium flows in from the inlet, overcomes the elastic force of the first spring, and pushes the small valve core to separate from the inlet, and the two-way actuator opens at low pressure.

[0010] During engine cycle precooling, a low-pressure medium is introduced from the outlet. The medium pressure difference force generated at both ends of the large valve core is not sufficient to overcome the elastic force of the second spring, and the large valve core will not move towards the guide sleeve and fit and seal with the guide sleeve; the low-pressure medium flows through the large valve core through-hole and the flow-through hole to the small valve core, and a medium pressure difference force is generated acting on both ends of the small valve core. The medium pressure difference force and the elastic force of the first spring are jointly transmitted to the small valve core, so that the small valve core is in sealed abutment with the inlet, ensuring the low-pressure reverse sealing of the two-way actuator.

[0011] During engine main engine operation, a high-pressure medium is instantaneously introduced from the outlet. The high-pressure medium flows into the valve cavity through the large valve core through-hole. Due to the throttling effect, a certain medium pressure difference force is generated on both end faces of the large valve core. The medium pressure difference force overcomes the elastic force of the second spring, so that the large valve core moves towards the guide sleeve and fits and seals with the guide sleeve, ensuring the reverse high-pressure sealing of the two-way actuator.

[0012] On the basis of the above technical solution, the present invention can also be improved as follows.

[0013] Further, it further includes a small valve core sealing ring. The edge of the end of the inlet facing the valve cavity has a sealing protrusion. The small valve core sealing ring is connected to one end of the small valve core, and the small valve core sealing ring is in sealed abutment or separation with the sealing protrusion.

[0014] The beneficial effects of adopting the above further scheme are as follows: Between one end of the small valve core and the inlet, sealing is achieved through the small valve core sealing ring and the sealing protrusion. After the small valve core is subjected to the medium pressure from the outlet and the elastic force of the first spring, the sealing protrusion is pressed into the small valve core sealing ring, and the small valve core sealing ring deforms and closely cooperates with the sealing protrusion to ensure the sealing performance.

[0015] Furthermore, one end of the guide sleeve has a guide sleeve counterbore, the first spring is arranged in the guide sleeve counterbore, the other end of the small valve core is in sliding fit with the guide sleeve counterbore, and abuts against one end of the first spring.

[0016] The beneficial effects of adopting the above further scheme are as follows: The guide sleeve counterbore positions and guides the small valve core and the first spring.

[0017] Furthermore, it further includes a first spring energy storage sealing ring. One end of the guide sleeve counterbore has a guide sleeve annular groove, and the first spring energy storage sealing ring is embedded in the guide sleeve annular groove and is in sealing fit with the side wall of the small valve core.

[0018] The beneficial effects of adopting the above further scheme are as follows: The first spring energy storage sealing ring prevents the medium from entering the guide sleeve counterbore, enabling a pressure difference to be generated between the two end faces of the small valve core due to the medium flowing in from the inlet, overcoming the elastic force of the first spring, ensuring that the two-way actuator maintains a fully open state at low pressure, and preventing flutter.

[0019] Furthermore, the side wall of the valve body has a leak detection port, the side wall of the guide sleeve has a guide sleeve leak detection port, and the leak detection port, the guide sleeve leak detection port, and the guide sleeve counterbore are sequentially communicated.

[0020] The beneficial effects of adopting the above further scheme are as follows: By setting the leak detection port and the guide sleeve leak detection port, it is possible to detect whether there is medium flowing into the guide sleeve counterbore, thereby detecting the sealing performance of the first spring energy storage sealing ring. At the same time, it can prevent the formation of a dead cavity in the guide sleeve counterbore and avoid jamming of the small valve core due to the pressure in the guide sleeve counterbore.

[0021] Furthermore, it further includes graphite sealing gaskets. The inner wall of the valve cavity has an annular guide sleeve positioning groove, the outer wall of the guide sleeve has a guide sleeve positioning protrusion, the guide sleeve positioning protrusion is located in the annular guide sleeve positioning groove, there are two graphite sealing gaskets, and the two graphite sealing gaskets are respectively located at both ends of the guide sleeve positioning protrusion and seal the guide sleeve positioning protrusion and the annular guide sleeve positioning groove.

[0022] The beneficial effects of adopting the above further scheme are as follows: The graphite sealing gaskets fix the position of the guide sleeve and at the same time ensure the static seal between the guide sleeve and the inner wall of the valve cavity.

[0023] Further, one end of the large spool valve has a large spool valve counterbore, the second spring is located within the large spool valve counterbore, one end edge of the large spool valve counterbore has a first conical surface, the other end of the guide sleeve has a second conical surface, and the first conical surface is in sealing abutment or separation with the second conical surface.

[0024] The beneficial effect of adopting the above further solution is that: the first conical surface and the second conical surface form a metal conical seal, blocking the flow of the medium at the outlet into the valve cavity, achieving reverse high-pressure sealing.

[0025] Further, it further includes a second spring energy storage sealing ring. The middle of the other end of the large spool valve has a large spool valve convex portion. The second spring energy storage sealing ring is sleeved outside the large spool valve convex portion and is in sealing cooperation with the inner wall of the valve cavity.

[0026] The beneficial effect of adopting the above further solution is that: it prevents the medium at the outlet from flowing between the guide sleeve and the inner wall of the valve cavity, forming a dynamic seal.

[0027] Further, one end of the large spool valve convex portion facing the outlet has a limit protrusion.

[0028] The beneficial effect of adopting the above further solution is that: the limit protrusion leaves a gap between the end face of the large spool valve convex portion and the end face of the valve cavity. After high-pressure medium flows in from the outlet, part of the medium can flow into this gap, thereby forming a pressure difference at both ends of the large spool valve. The large spool valve moves to be in sealing abutment with the guide sleeve under the action of the pressure difference.

[0029] The present invention also provides a closed-cycle full-flow staged combustion engine, including a two-way actuator with a double-valve structure.

[0030] The beneficial effect of the present invention lies in that: the present invention proposes a two-way actuator with a double-valve seat structure and a double-valve structure that can be applied to a full-flow staged combustion engine, which has the advantages of a wide working pressure range, reliable operation, and simplified engine system, and works throughout the processes of engine purging, cycle pre-cooling, main engine operation, and shutdown.

[0031] This two-way actuator adopts two sealing types, namely metal conical sealing (the first conical surface and the second conical surface) and non-metal sealing (the small spool valve sealing ring and the sealing protrusion), and can achieve effective reverse sealing within the range of (0 - 60) MPa. It has a wide working pressure range, reliable performance, and can be applied to various stages of purging, cycle pre-cooling, main engine operation, shutdown, and thrust adjustment of a closed-cycle full-flow staged combustion engine.

[0032] This two-way actuator has the functions of opening at low pressure in the forward direction, sealing at low pressure in the reverse direction, and sealing at high pressure in the reverse direction, and has both high-pressure and low-pressure one-way sealing functions, simplifies the engine system, reduces the types of valves, and is more conducive to the overall assembly layout of the engine.

[0033] Use a spring seal ring to replace the traditional bellows as the dynamic seal for cryogenic high-pressure media. It has good low-temperature sealing effect, simple structure of the two-way automatic valve, and small overall dimensions. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 FIG. is a schematic structural view of a two-way automatic valve with a double-valve structure according to the present invention;

[0035] Figure 2 FIG. is a schematic view of the two-way automatic valve with a double-valve structure according to the present invention in the state of engine purging and forward low-pressure opening;

[0036] Figure 3 FIG. is a schematic view of the two-way automatic valve with a double-valve structure according to the present invention in the state of engine cycle precooling and reverse low-pressure closing;

[0037] Figure 4 FIG. is a schematic view of the two-way automatic valve with a double-valve structure according to the present invention in the state of engine main operation and reverse high-pressure closing;

[0038] Figure 5 is Figure 1 a partial enlarged view of the X position of a two-way automatic valve with a double-valve structure of

[0039] In the drawings, the list of components represented by each reference numeral is as follows:

[0040] 1. Housing; 2. First spring energy storage seal ring; 3. Small valve core; 4. Graphite sealing gasket; 5. Cover body; 6. First spring; 7. Large valve core; 701. Large valve core through hole; 702. Large valve core counterbore; 703. First conical surface; 704. Outer convex part of the large valve core; 8. Second spring energy storage seal ring; 9. Second spring; 10. Guide sleeve; 101. Flow hole; 102. Guide sleeve counterbore; 103. Leak detection port of the guide sleeve; 104. Second conical surface; 11. Stud; 12. Flat washer; 13. Saddle spring washer; 14. Nut; 15. Inlet; 16. Outlet; 17. Leak detection port; 18. Small valve core seal ring. DETAILED DESCRIPTION OF THE INVENTION

[0041] The principles and features of the present invention are described below. The examples given are only used to explain the present invention and are not intended to limit the scope of the present invention.

[0042] Such as Figures 1 - 5As shown in the figure, this embodiment provides a two-way actuator with a dual-valve structure, including a valve body, a small valve core 3, a guide sleeve 10, a large valve core 7, a first spring 6 and a second spring 9. The valve body has a valve cavity. One end of the valve body has an inlet 15, and the other end has an outlet 16. The inlet 15 and the outlet 16 are both communicated with the valve cavity. The small valve core 3, the first spring 6, the guide sleeve 10, the second spring 9 and the large valve core 7 are sequentially abutted and arranged in the valve cavity. The guide sleeve 10 is fixedly sealed with the valve cavity and has a flow-through hole 101 penetrating through both ends thereof. One end of the small valve core 3 is in sealing abutment or separation with the inlet 15, and one end of the large valve core 7 is in sealing abutment or separation with the guide sleeve 10. The large valve core 7 has a large valve core through-hole 701 penetrating through both ends thereof.

[0043] The two-way actuator with a dual-valve structure is a two-way actuator with a dual-valve seat structure, which is used to replace the existing purge check valve. It has the advantages of a wide working pressure range, reliable operation and simplified engine system, and works throughout the whole process of engine purge, cycle precooling, main engine operation and shutdown.

[0044] This two-way actuator has the functions of opening at low pressure in the forward direction, sealing at low pressure in the reverse direction and sealing at high pressure in the reverse direction. It combines the functions of high-pressure and low-pressure one-way sealing, simplifies the engine system, reduces the types of valves, and is more conducive to the overall assembly layout of the engine. Specifically, in the existing engine system, without using the two-way actuator of this embodiment, two types of check valves are required at the same time, and two or three branches need to be added to the system; while after using the two-way actuator of this application, adding this two-way actuator on one branch of the system can meet the system functions.

[0045] Specifically, during engine purge, a low-pressure medium flows in from the inlet 15, overcomes the elastic force of the first spring 6, and pushes the small valve core 3 to separate from the inlet 15, and the two-way actuator opens at low pressure.

[0046] During engine cycle precooling, a low-pressure medium is introduced from the outlet 16. The medium pressure difference force generated at both ends of the large valve core 7 is not enough to overcome the elastic force of the second spring 9, and the large valve core 7 will not move towards the guide sleeve 10 and fit and seal with the guide sleeve 10; the low-pressure medium flows through the large valve core through-hole 701 and the flow-through hole 101 to the small valve core 3, and a medium pressure difference force is generated at both ends of the small valve core 3. The medium pressure difference force and the elastic force of the first spring 6 are jointly transmitted to the small valve core 3, so that the small valve core 3 is in sealing abutment with the inlet 15, ensuring the low-pressure reverse sealing of the two-way actuator.

[0047] When the engine main unit is working, high-pressure medium is instantaneously introduced from outlet 16. The high-pressure medium flows into the valve cavity through the through-hole 701 of the large valve core. Due to the throttling effect, a certain medium pressure difference force is generated on both end faces of the large valve core 7. The medium pressure difference force overcomes the elastic force of the second spring 9, causing the large valve core 7 to move towards the guide sleeve 10 and fit and seal with the guide sleeve 10, ensuring the reverse high-pressure seal of the two-way automatic device.

[0048] Specifically, the valve body includes a housing 1 and a cover 5. The housing 1 and the cover 5 are connected by a flange structure, and a valve cavity is formed inside between the two. The connection structure of the housing 1 and the cover 5 is specifically that one end of the stud 11 is threadedly connected to the flange of the housing 1, and the other end passes through the saddle-shaped elastic gasket 13 and the flat gasket 12 and is threadedly connected to the nut 14. The stud 11, the saddle-shaped elastic gasket 13, the flat gasket 12 and the nut 14 form a set of connection components, and multiple sets of connection components are provided at intervals along the circumference of the housing 1.

[0049] Specifically, four threaded holes evenly distributed along the circumference of the valve body and a valve body annular sealing groove are machined on the inlet end face of the housing 1 and the outlet end face of the cover 5. A graphite sealing gasket is installed in the valve body annular sealing groove and is connected to the engine system pipeline.

[0050] On the basis of the above technical solution, it further includes a small valve core sealing ring 18. The edge of one end of the inlet 15 facing the valve cavity has a sealing protrusion. The small valve core sealing ring 18 is connected to one end of the small valve core 3, and the small valve core sealing ring 18 is in sealing contact or separation with the sealing protrusion.

[0051] Between one end of the small valve core 3 and the inlet 15, sealing is achieved through the small valve core sealing ring 18 and the sealing protrusion. After the small valve core 3 is subjected to the medium pressure from the outlet 16 and the elastic force of the first spring 6, the sealing protrusion is pressed into the small valve core sealing ring 18, and the small valve core sealing ring 18 deforms and closely cooperates with the sealing protrusion to ensure the sealing performance.

[0052] Specifically, as Figure 5 shown, the cross-section of the small valve core sealing ring 18 is convex-shaped.

[0053] On the basis of the above technical solution, one end of the guide sleeve 10 has a guide sleeve counterbore 102. The first spring 6 is arranged in the guide sleeve counterbore 102. The other end of the small valve core 3 is in sliding fit with the guide sleeve counterbore 102 and abuts against one end of the first spring 6.

[0054] The guide sleeve counterbore 102 positions and guides the small valve core 3 and the first spring 6.

[0055] Specifically, the machining accuracy of the outer cylindrical surface of the small valve core 3 should be relatively high, and it forms a key kinematic pair with the guide sleeve counterbore 102 of the guide sleeve 10.

[0056] On the basis of the above technical solution, it further includes a first spring energy storage sealing ring 2. One end of the guide sleeve counterbore 102 has a guide sleeve annular groove, and the first spring energy storage sealing ring 2 is embedded in the guide sleeve annular groove and is in sealing cooperation with the side wall of the small valve core 3.

[0057] The first spring energy storage sealing ring 2 prevents the medium from entering the guide sleeve counterbore 102, so that pressure differences can be generated on both end faces of the small valve core 3 due to the medium flowing in from the inlet 15, overcoming the elastic force of the first spring 6, ensuring that the two-way actuator maintains a fully open state at low pressure and preventing flutter.

[0058] On the basis of the above technical solution, the side wall of the valve body has a leak detection port 17, the side wall of the guide sleeve 10 has a guide sleeve leak detection port 103, and the leak detection port 17, the guide sleeve leak detection port 103 and the guide sleeve counterbore 102 are communicated in sequence.

[0059] Setting the leak detection port 17 and the guide sleeve leak detection port 103 can detect whether there is medium flowing into the guide sleeve counterbore 102, thereby detecting the sealing performance of the first spring energy storage sealing ring 2. At the same time, it can avoid the formation of a dead cavity in the guide sleeve counterbore 102 and prevent the small valve core 3 from being stuck due to the pressure in the guide sleeve counterbore 102.

[0060] On the basis of the above technical solution, it further includes a graphite sealing gasket 4. The inner wall of the valve cavity has an annular guide sleeve positioning groove, the outer wall of the guide sleeve 10 has a guide sleeve positioning protrusion, the guide sleeve positioning protrusion is located in the annular guide sleeve positioning groove, there are two graphite sealing gaskets 4, and the two graphite sealing gaskets 4 are respectively located at both ends of the guide sleeve positioning protrusion and seal the guide sleeve positioning protrusion and the annular guide sleeve positioning groove.

[0061] The graphite sealing gasket 4 fixes the position of the guide sleeve 10 and at the same time ensures the static seal between the guide sleeve 10 and the inner wall of the valve cavity.

[0062] Specifically, the outer wall of the guide sleeve positioning protrusion has an annular diversion groove, and both the guide sleeve leak detection port 103 and the leak detection port 17 are communicated with the annular diversion groove. In this way, if the seal of the graphite sealing gasket 4 fails, the medium will flow into the annular diversion groove, and thus the leakage can be detected through the leak detection port 17. At the same time, it can also be used to detect whether there is medium flowing into the guide sleeve counterbore 102.

[0063] Specifically, the annular guide sleeve positioning groove is located at one end of the housing 1 away from the inlet 15. After the housing 1 and the cover 5 are assembled, one graphite sealing gasket 4, the guide sleeve positioning protrusion and the other graphite sealing gasket 4 are sequentially pressed tightly in the annular guide sleeve positioning groove.

[0064] On the basis of the above technical solution, one end of the large valve core 7 has a large valve core counterbore 702, the second spring 9 is located in the large valve core counterbore 702, one end edge of the large valve core counterbore 702 has a first conical surface 703, the other end of the guide sleeve 10 has a second conical surface 104, and the first conical surface 703 is in sealing contact with or separated from the second conical surface 104.

[0065] The first conical surface 703 and the second conical surface 104 form a metal conical seal, blocking the flow of the medium at the outlet 16 into the valve cavity and realizing reverse high-pressure sealing.

[0066] Specifically, the bottom of the large valve core counterbore 702 (the end of the large valve core counterbore 702 facing the outlet 16) has the large valve core through hole 701.

[0067] Specifically, the outer diameter of the other end of the guide sleeve 10 is smaller than the outer diameter of one end of the large valve core 7.

[0068] On the basis of the above technical solution, it further includes a second spring energy storage sealing ring 8. The middle of the other end of the large valve core 7 has a large valve core convex part 704. The second spring energy storage sealing ring 8 is sleeved on the outside of the large valve core convex part 704 and is in sealing cooperation with the inner wall of the valve cavity.

[0069] Prevent the medium at the outlet 16 from flowing between the guide sleeve 10 and the inner wall of the valve cavity to form a dynamic seal.

[0070] On the basis of the above technical solution, the end of the large valve core convex part 704 facing the outlet 16 has a limit protrusion.

[0071] The limit protrusion makes a gap remain between the end face of the large valve core convex part 704 and the end face of the valve cavity. After high-pressure medium flows in from the outlet 16, part of the medium can flow into this gap, so as to form a pressure difference at both ends of the large valve core 7. Under the action of the pressure difference, the large valve core 7 moves to be in sealing contact with the guide sleeve 10.

[0072] Optionally, the limit protrusion is a dot-shaped protrusion or a strip-shaped protrusion.

[0073] The working principle of a two-way actuator with a double-valve structure in this embodiment is specifically as follows:

[0074] During engine purging, low-pressure medium flows in from the inlet 15 of the housing 1, overcoming the pre-installed force of the first spring 6, and the two-way actuator opens at low pressure. The first spring energy storage sealing ring 2 blocks the low-pressure medium from flowing into the guide sleeve counterbore 102 of the small valve core 3 and the guide sleeve 10, causing a pressure difference between the left and right end faces of the small valve core 3, overcoming the working force of the first spring 6, ensuring that the two-way actuator maintains a fully open state at low pressure and preventing flutter.

[0075] When the engine cycle is pre-cooled, a low-pressure medium is introduced from the outlet 16 of the cover body 5. The medium pressure difference force generated at both ends of the large valve core 7 is not sufficient to overcome the pre-installed force of the second spring 9, and the large valve core 7 will not move to the left to fit and seal with the guide sleeve 10. The low-pressure medium flows into the inner cavity between the housing 1 and the guide sleeve 10, acting on the left and right end faces of the small valve core 3 (the annular area at the right end of the small valve core 3 is larger than the annular area at the left end, where the annular area at the left end refers to the area of the left end of the small valve core 3 minus the cross-sectional area of the inlet 15) to generate a medium pressure difference force. The medium pressure difference force and the pre-installed force of the first spring 6 are jointly transmitted to the small valve core 3, causing the non-metallic sealing surface of the small valve core 3 to fit and press against the valve seat of the housing 1 (as Figure 5 shown), ensuring the low-pressure reverse sealing of the two-way automatic device.

[0076] When the engine main unit is working, a high-pressure medium is instantaneously introduced from the outlet 16 of the cover body 5. The second spring energy storage sealing ring 8 blocks the high-pressure medium from flowing into the inner cavity between the cover body 5 and the guide sleeve 10. The high-pressure medium flows into the valve cavity through the large valve core through-hole 701 of the large valve core 7. Due to the throttling effect, a certain medium pressure difference force is generated on both end faces of the large valve core 7. The medium pressure difference force overcomes the working force of the second spring 9, causing the large valve core 7 to move to the left and fit and seal with the conical inclined surface (the second conical surface 104) of the guide sleeve 10, ensuring the reverse high-pressure sealing of the two-way automatic device.

[0077] This embodiment also provides a closed-cycle full-flow afterburning engine, including a two-way automatic device with a double-valve structure.

[0078] Specifically, the inlet 15 and the outlet 16 of the valve body are connected and communicated with the engine system pipeline.

[0079] In the description of the present invention, it should be noted that the orientation or positional relationship indicated by terms such as "axial direction", "radial direction", "circumferential direction", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0080] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, the meaning of "a plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0081] In the present invention, unless otherwise clearly specified or limited, the first feature being "on" or "under" the second feature may mean that the first and second features are in direct contact, or the first and second features are indirectly in contact through an intermediate medium. Moreover, the first feature being "above", "over" and "on top of" the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the horizontal height of the first feature is higher than that of the second feature. The first feature being "under", "below" and "beneath" the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the horizontal height of the first feature is less than that of the second feature.

[0082] In the description of this specification, the description with reference to terms such as "an embodiment", "some embodiments", "example", "specific example" or "some examples" etc. means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in a suitable manner in any one or more embodiments or examples. In addition, without contradiction, those skilled in the art can combine and combine the different embodiments or examples described in this specification and the features of different embodiments or examples.

[0083] In the description of the present invention, it should be noted that, unless otherwise clearly specified or limited, the terms "mounted", "connected" and "coupled" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a direct connection, or an indirect connection through an intermediate medium, and it may be the internal communication of two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0084] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present invention shall be included within the protection scope of the present invention.

Claims

1. A two-way automatic machine with a double-valve structure, characterized in that: The invention comprises a valve body, a small valve core (3), a guide sleeve (10), a large valve core (7), a first spring (6), a second spring (9) and a small valve core sealing ring (18), wherein the valve body has a valve cavity, one end of the valve body has an inlet (15), and the other end of the valve body has an outlet (16), the inlet (15) and the outlet (16) are both connected to the valve cavity, the small valve core (3), the first spring (6), the guide sleeve (10), the second spring (9) and the large valve core (7) are sequentially abutted and arranged on the valve cavity. In the valve cavity, the guide sleeve (10) is sealed and fixed to the valve cavity and has flow holes (101) running through both ends thereof. The edge of the inlet (15) facing one end of the valve cavity has a sealing protrusion. The small valve core sealing ring (18) is connected to one end of the small valve core (3). The small valve core sealing ring (18) is sealed in contact with or separated from the sealing protrusion. One end of the large valve core (7) is sealed in contact with or separated from the guide sleeve (10). The large valve core (7) has a large valve core through hole (701) running through both ends thereof.

2. A two-way automatic machine with a double-valve structure according to claim 1, characterized in that: One end of the guide sleeve (10) has a guide sleeve counterbore (102), the first spring (6) is arranged in the guide sleeve counterbore (102), and the other end of the small valve core (3) is slidably matched with the guide sleeve counterbore (102) and abuts against one end of the first spring (6).

3. A two-way automatic machine with a double-sliding door structure according to claim 2, characterized in that: It also includes a first spring energy storage sealing ring (2), one end of the guide sleeve counterbore (102) has a guide sleeve annular groove, the first spring energy storage sealing ring (2) is embedded in the guide sleeve annular groove and seals with the side wall of the small valve core (3).

4. A two-way automatic machine with a double-sliding door structure according to claim 2, characterized in that: The side wall of the valve body has a leak detection port (17), the side wall of the guide sleeve (10) has a guide sleeve leak detection port (103), and the leak detection port (17), the guide sleeve leak detection port (103) and the guide sleeve counterbore (102) are sequentially connected.

5. A two-way automatic machine with a double-sliding door structure according to claim 1, characterized in that: It also includes a graphite sealing gasket (4), the inner wall of the valve cavity has an annular guide sleeve positioning groove, the outer wall of the guide sleeve (10) has a guide sleeve positioning protrusion, the guide sleeve positioning protrusion is located in the annular guide sleeve positioning groove, and there are two graphite sealing gaskets (4), the two graphite sealing gaskets (4) are respectively located at the two ends of the guide sleeve positioning protrusion, and the guide sleeve positioning protrusion is sealed with the annular guide sleeve positioning groove.

6. A two-way automatic machine with a double valve structure according to claim 1, characterized in that: One end of the large valve core (7) has a large valve core counterbore (702), the second spring (9) is located in the large valve core counterbore (702), one end edge of the large valve core counterbore (702) has a first conical surface (703), the other end of the guide sleeve (10) has a second conical surface (104), the first conical surface (703) and the second conical surface (104) are sealed in contact or separated.

7. A two-way automatic machine with a double valve structure according to claim 1, characterized in that: It also includes a second spring energy storage sealing ring (8), and the middle part of the other end of the large valve core (7) has a large valve core outer protrusion (704). The second spring energy storage sealing ring (8) is sleeved on the outside of the large valve core outer protrusion (704) and is sealed with the inner wall of the valve cavity.

8. A two-way automatic machine with a double-sliding door structure according to claim 7, characterized in that: One end of the outer protrusion (704) of the large valve core facing the outlet (16) has a limiting protrusion.

9. A closed cycle full flow afterburning engine, characterized in that: A two-way automatic machine comprising a double valve structure as described in any one of claims 1-8.

Images