A self-adjusting, high-sealing-performance lifting valve for a regenerative waste gas incinerator

Abstract

This invention discloses a self-adjusting high-sealing-performance lifting valve for a regenerative waste gas incinerator. By employing a positioning bracket to directly connect and fix the valve seat and valve cover, the positioning bracket maintains the relative state of the valve seat and valve cover when the inner and outer walls of the furnace deform, thereby significantly reducing the non-parallelism between the valve seat and valve plate. Simultaneously, further combined with an automatically adjustable and balanced valve plate assembly, the lifting valve possesses self-adjusting high-sealing performance, effectively improving the reliability of the seal between the valve seat and valve plate assembly, and effectively solving the problems existing in the prior art.

Description

Technical Field

[0001] This invention relates to lift valve technology, specifically to a lift valve for a regenerative waste gas incinerator. Background Technology

[0002] In regenerative thermal oxidizers (RTO), the lift valve is a crucial component, installed at the inlet and outlet of the furnace. Depending on the air volume, a single RTO may have multiple lift valves. The primary function of the lift valve is to cut off and treat the inlet exhaust gas before its discharge. Some of the discharged gas flows directly to the chimney, while others require further treatment such as denitrification before reaching the chimney. Therefore, if the lift valve's sealing performance is inadequate, the burning exhaust gas will leak directly into the atmosphere. This highlights the critical importance of sealing performance for an RTO.

[0003] The lifting valve in a conventional regenerative thermal oxidizer (RTO) incinerator opens and closes every 3 minutes, with a required opening and closing time of approximately 2 seconds. This high frequency of opening and closing leads to violent collisions between the valve seat and valve plate, inevitably causing scratches, dents, and fatigue on the sealing surface. Furthermore, during operation, the cyclical temperature changes in the lower furnace body alter the dimensions of the outer and inner walls, affecting the parallelism between the valve seat and valve plate and significantly reducing sealing performance. Additionally, the rolling bearing adjustment components in existing RTO incinerators use bearing steel, which rusts over time. During operation, flue gas enters the bearings, increasing friction and corroding the balls. Moreover, the components of existing lifting valves are primarily made of sheet metal or welded sheet metal, resulting in a large number of fasteners and compromising the concentricity of the parts.

[0004] For details, see Figure 1 The figure shows the common structure of the lift valve installed on an existing regenerative waste gas incinerator. As shown in the figure, the existing lift valve is mainly composed of several parts that work together, including a rolling bearing adjusting assembly (1), a valve seat liner (2), an inner furnace wall (3), a valve seat (4), a valve plate assembly (5), a valve stem assembly (6), a valve cover (7), a graphite packing assembly (8), an outer furnace wall (9), a cylinder (10), and a cylinder bracket (11). When installing and using this type of lift valve, the valve seat liner (2) is fixed to the lower furnace wall (3) with bolts, and the sealing surface adopts a hard seal structure. The lift valve uses two rolling bearing adjusting assemblies (1) for adjustment to ensure the parallelism of the left and right valve plates and valve seats.

[0005] The lift valve with this structure has many problems in practical applications, the main problems being as follows:

[0006] (1) The valve seat liner (2) and valve seat (4) are fixed to the inner furnace wall (3) with bolts, and the valve cover (7) is fixed to the outer furnace wall (9) with bolts. Before the equipment is running, the front and rear rolling bearing adjustment components (1) will be adjusted to make the valve seat (4) parallel to the valve plate assembly (5). After the equipment is running, the furnace body will deform due to temperature changes, causing the valve seat (4) and valve plate assembly (5) to lose parallelism, resulting in leakage of the sealing surface.

[0007] (2) The sealing form of the valve seat (4) and the valve plate assembly (5) is a linear hard seal. Due to the high frequency of use of this valve, it is easy to cause violent collision between the valve seat and the valve plate. Scratches, bumps and fatigue of the sealing surface are inevitable, and the sealing performance and service life will be affected to varying degrees.

[0008] (3) Since the cylinder bracket is installed on the outer furnace body and is below the neutral line of the lifting valve, when the valve is closed, the cylinder tends to sink. At this time, the packing in the graphite packing assembly (8) will be tight at the top and loose at the bottom. Over time, the packing will leak.

[0009] (4) The bearings used in the rolling bearing adjustment assembly (1) are ball bearings. They are exposed to pollution and corrosion from exhaust gas for a long time, which can cause them to jam and require frequent replacement. They are also large in size, which affects the flow capacity of the lifting valve. In highly corrosive working conditions, it is almost impossible to find suitable rolling bearings.

[0010] (5) Most of the parts of the lift valve are cut and welded from sheet metal, resulting in uneven load-bearing capacity, large amount of fasteners, heavy weight, and inability to guarantee dimensional and positional tolerances.

[0011] (6) The valve stem assembly (6) of the lifting valve and the cylinder (10) are generally connected by a threaded connection, which requires a very high degree of relative position; and when the concentricity changes significantly after wear during operation, the cylinder will experience greater wear and affect its service life.

[0012] In summary, providing a lift valve solution with low leakage and stable reliability is a problem that urgently needs to be solved in this field. Summary of the Invention

[0013] To address the issues with the sealing reliability of existing lifting valves used in regenerative thermal septic gas incinerators, the present invention aims to provide a self-adjusting lifting valve with high sealing performance for regenerative thermal septic gas incinerators. By adopting an innovative self-adjusting structure in conjunction with a corresponding positioning bracket, the sealing reliability of the lifting valve is effectively improved, thus overcoming the problems existing in the prior art.

[0014] To achieve the above objectives, the present invention provides a self-adjusting high-sealing performance lifting valve for a regenerative waste gas incinerator, comprising an inner bearing assembly, a valve stem assembly, an outer bearing assembly, a cylinder, a valve seat, a valve cover, a valve plate assembly, and a cylinder support.

[0015] It also includes an inner wall welded flange and a positioning bracket;

[0016] The valve seat is installed in the inner wall of the regenerative waste gas incinerator via an inner wall welded flange.

[0017] The valve cover is concentrically fixed in the outer wall of the regenerative waste gas incinerator, corresponding to the valve seat; the valve seat and the valve cover are directly connected and fixed through the positioning bracket.

[0018] The inner valve stem portion of the valve stem assembly has one end mounted in the valve seat via an inner bearing assembly, and the other end connected to the valve plate assembly. The outer valve stem portion of the valve stem assembly is coaxially arranged corresponding to the inner valve stem portion, with one end mounted in the cylinder bracket via an outer bearing assembly and the other end connected to the valve plate assembly. The cylinder bracket is fixedly mounted on the valve cover. The cylinder is mounted on the cylinder bracket and drives the outer valve stem portion connected to the valve stem assembly.

[0019] The valve plate assembly is connected and cooperates with the inner valve stem and outer valve stem of the valve stem assembly through a self-adjusting structure. Under the drive of the valve stem assembly, it can cooperate with the valve seat to form a sealing structure, and automatically adjust to remain parallel to the valve seat after contacting the valve seat.

[0020] Furthermore, the positioning bracket is provided with a positioning step that connects to the valve seat and / or the valve cover.

[0021] Furthermore, the valve plate assembly includes a valve plate, a valve plate seat, a bearing pressure plate, and a spherical bearing; the spherical bearing is connected and engaged with the inner valve stem portion and the outer valve stem portion in the valve stem assembly; the valve plate seat is fixedly mounted on the spherical bearing via the bearing pressure plate; and the valve plate is mounted on the valve plate seat.

[0022] Furthermore, the valve seat is subjected to a cobalt-tungsten alloy overlay treatment on the sealing surface corresponding to the valve plate assembly.

[0023] Furthermore, the valve seat forms a first sealing structure that seals with the valve plate in its normal state and a second sealing structure that seals with the valve plate in its elastically deformed state, corresponding to the sealing surface of the valve plate assembly.

[0024] Furthermore, the valve seat is provided with a compressed air isolation strip structure.

[0025] Furthermore, the cylinder bracket includes a bracket body and a stuffing box, the stuffing box being integrally formed at the front end of the bracket body, and the outer valve stem passing through the stuffing box.

[0026] Furthermore, a graphite packing seal is used between the stuffing box and the outer valve stem.

[0027] Furthermore, the packing box is provided with a compressed air chamber ring at the middle position of the graphite packing.

[0028] Furthermore, a protective cover and a sealing ring are provided around the inner linear bearing.

[0029] The self-adjusting high-sealing performance lift valve for regenerative waste gas incinerators provided by this invention uses a positioning bracket to directly connect and fix the valve seat and valve cover. This allows the positioning bracket to maintain the relative state of the valve seat and valve cover when the inner and outer walls of the furnace deform, significantly reducing the non-parallelism between the valve seat and valve plate. Furthermore, the addition of an automatically adjustable and balanced valve plate assembly further enhances the self-adjusting high-sealing performance of the lift valve, effectively improving the reliability of the seal between the valve seat and valve plate assembly and effectively solving the problems existing in the prior art. Attached Figure Description

[0030] The present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0031] Figure 1 A structural example diagram of a lift valve used in an existing regenerative waste gas incinerator;

[0032] Figure 2 This is an example diagram illustrating the structure of a self-adjusting high-sealing-performance lifting valve for a regenerative waste gas incinerator in this invention.

[0033] Figure 3 This is an example diagram illustrating the fixed connection between the positioning bracket and the valve seat and valve cover in an embodiment of the present invention;

[0034] Figure 4 This is an enlarged example diagram of the connection between the positioning bracket and the valve seat in an embodiment of the present invention;

[0035] Figure 5 This is an enlarged example diagram of the connection between the positioning bracket and the valve cover in an embodiment of the present invention;

[0036] Figure 6 This is an example diagram of the self-adjusting structure of the valve plate assembly in an embodiment of the present invention;

[0037] Figure 7 This is a structural example diagram of the valve plate seat in an embodiment of the present invention;

[0038] Figure 8 This is an example diagram of the sealing surface structure between the valve seat and the valve plate in an embodiment of the present invention;

[0039] Figure 9 This is a structural example diagram of the integrated cylinder bracket in an embodiment of the present invention;

[0040] Figure 10This is an enlarged example view of the connection between the cylinder bracket and the valve cover in an embodiment of the present invention;

[0041] Figure 11 This is a structural example diagram of the stuffing box in an embodiment of the present invention;

[0042] Figure 12 This is an example diagram of the linear bearing and protective structure in an embodiment of the present invention;

[0043] Figure 13 This is a structural example diagram of the compressed air chamber ring in an embodiment of the present invention. Detailed Implementation

[0044] To make the technical means, creative features, objectives and effects of this invention easier to understand, the invention will be further described below with reference to specific illustrations.

[0045] In view of the high-frequency switching operation and high-temperature working environment of the lift valve in the regenerative waste gas incinerator, the present invention provides a lift valve for the regenerative waste gas incinerator with self-adjusting high sealing performance. Compared with the existing lift valve configuration for regenerative waste gas incinerators, this lift valve has the performance characteristics of low leakage, high valve body strength, reliable operation and long service life.

[0046] Example 1

[0047] See Figure 2 The diagram shows an example of a self-adjusting high-sealing performance booster valve for a regenerative waste gas incinerator provided by the present invention.

[0048] Based on the diagram, the self-adjusting high-sealing performance lifting valve for this regenerative waste gas incinerator mainly includes the following components: inner bearing assembly 2, inner wall welded flange 3, valve seat 6, positioning bracket 9, valve plate 10, valve plate pressure plate 11, valve plate seat 12, bearing pressure plate 13, spherical bearing 14, inner valve stem 15, valve cover 17, graphite packing 20, outer bearing assembly 21, cylinder bracket 22, outer valve stem 23, and cylinder 25.

[0049] In this example, an inner wall welded flange 3 is introduced to connect the valve seat 6 to the inner wall 4 of the regenerative waste gas incinerator, avoiding direct connection between the valve seat 6 and the inner wall 4 of the furnace, thereby mitigating the impact of changes in the shape of the inner wall 4 of the furnace on the valve seat 6.

[0050] Specifically, the middle part of the inner wall welded flange 3 is embedded in the inner wall of the furnace body 4 and welded and fixed to the inner wall of the furnace body 4; while the valve seat 6 is fixed to the inner wall welded flange 3 by the first screw 5, and the valve seat 6 and the inner wall welded flange 3 are in a coaxial fixed state.

[0051] The specific structure of valve seat 6 is not limited here and can be determined according to actual needs. As an example, taking the illustrated scheme as an example, the structure of valve seat 6 given in this example is generally close to a flange. One end face is the connection end face, which is fixedly connected to the flange 3 welded to the inner wall. The other end face is the sealing end face, on which a sealing structure is formed for cooperation with valve plate 10 to form a reliable seal for the lifting seal.

[0052] Correspondingly, the valve cover 17 is directly fixed in the outer wall 16 of the furnace body of the regenerative waste gas incinerator, and the valve cover 17 and the valve seat 6 fixed in the inner wall 4 of the furnace body are concentrically arranged, that is, the valve cover 17 installed in the outer wall 16 of the furnace body and the valve seat 6 fixed in the inner wall 4 of the furnace body are coaxial and parallel.

[0053] The specific structure of the valve cover 17 is not limited here and can be determined according to actual needs. As an example, the valve cover 17 in this example adopts a one-piece molding structure. As a preferred option, an integral casting structure can be adopted, which results in a valve cover with high overall strength and precise machining dimensions; thereby ensuring the parallelism and concentricity of the lifting valve during operation.

[0054] The valve cover 17 with this structure can isolate the exhaust gas after the lifting valve is installed on the furnace body, and can also support the lifting valve exposed to the outside of the furnace body.

[0055] Combination Figure 3 As shown, for the valve seat 6 and valve cover 17 that are coaxial and parallel to each other, in this example, a positioning bracket 9 is further added to the valve seat 6 and valve cover 17. The valve seat 6 and valve cover (17) are directly connected and fixed by the positioning bracket 9 to form an integral structure. In this way, when the inner and outer walls of the furnace are deformed, the positioning bracket 9 set between the two will support and position the valve seat 6 and valve cover 17, so that the valve seat 6 and valve cover 17 can remain unchanged, thereby greatly reducing the non-parallelism between the valve seat and valve plate of the lifting valve.

[0056] Specifically, the positioning bracket 9 is a hollow cylindrical structure, with one end of its port cooperating with the connecting end face of the valve seat 6 and the other end of its port cooperating with the connecting end face of the valve cover 17. For example, the valve seat 6 and the valve cover 17 can be connected and fixed to the port of the positioning bracket 9 by corresponding screws.

[0057] The specific structure of the positioning bracket 9 is not limited here and can be determined according to actual needs. Preferably, the positioning bracket 9 adopts a lantern-type structure and is integrally cast. When the positioning bracket 9 with such structure is installed with the valve seat 6 and the valve cover 17, it can ensure the flow capacity while ensuring the parallelism and alignment of the connection between the valve seat 6 and the valve cover 17.

[0058] Based on this, the example scheme further provides a mutually cooperating positioning step 26 (e.g., at the connection and fit between the positioning bracket 9 and the valve seat 6) Figure 4 As shown), a matching positioning step 27 is provided at the connection between the positioning bracket 9 and the valve cover 17 (as shown). Figure 5 As shown in the figure, this further improves the concentricity between valve seat 6 and valve cover 17, and improves the assembly efficiency of the three.

[0059] Furthermore, this example also includes a matching positioning step 28 (e.g., ...) at the connection between the valve seat 6 and the inner wall welded flange 3. Figure 4 As shown in the figure, this further improves and ensures the concentricity between the positioning bracket 9, the valve seat 6, and the valve cover 17.

[0060] Based on the structure formed by the cooperation between the valve seat 6, the positioning bracket 9 and the valve cover 17, this example solution further assembles the valve stem assembly.

[0061] The valve stem assembly in this example mainly consists of an inner bearing assembly 2, an inner valve stem 15, an outer bearing assembly 21, and an outer valve stem 23.

[0062] Combination Figure 1 As shown, the inner valve stem 15 is mounted in the valve seat 6 via the inner bearing assembly 2 and is connected to the corresponding valve plate assembly.

[0063] Specifically, the inner bearing assembly 2 is integrally housed in the valve seat 6, while one end of the inner valve stem 15 passes through the inner bearing assembly 2, and the other end of the inner valve stem 15 is connected to the corresponding valve plate assembly.

[0064] Correspondingly, the outer valve stem 23 and the inner valve stem 15 in the valve stem assembly are coaxially arranged and are connected to the corresponding valve plate assembly.

[0065] Specifically, the outer valve stem 23 is mounted in a corresponding cylinder bracket 22 via a corresponding outer bearing assembly 21. The cylinder bracket 22 is fixedly mounted on the valve cover 17 corresponding to the inner valve stem 15, such that the outer valve stem 23 and the inner valve stem 15 are relatively coaxially distributed. One end of the outer valve stem 23 passes through the cylinder bracket 22 through the valve cover 17 and is connected to the corresponding valve plate assembly, while the other end extends into the cylinder bracket 22 to connect with the cylinder 25 mounted on the cylinder bracket 22. The cylinder 25 serves as a power source to drive the valve stem assembly to move.

[0066] The valve stem assembly thus formed can rotate and move back and forth along the axial direction under the drive of cylinder 25.

[0067] Based on the valve stem assembly solution, this example solution further includes a valve plate assembly.

[0068] In this example, the valve plate assembly innovatively connects and cooperates with the inner valve stem 15 and outer valve stem 23 in the valve stem assembly through a self-adjusting structure, achieving a movable distribution between the valve seat 6 and the valve cover 17, while remaining parallel to the valve seat 6. Driven by the valve stem assembly, this valve plate assembly can move back and forth at high speed between the valve seat 6 and the valve cover 17, forming a sealing structure with the valve seat 6. Simultaneously, based on the corresponding self-adjusting structure, it automatically adjusts its distribution state after contacting the valve seat 6, maintaining parallelism with it.

[0069] Further integration Figure 6 As shown, the valve plate assembly in this example mainly consists of a valve plate 10, a valve plate pressure plate 11, a valve plate seat 12, a bearing pressure plate 13, and a spherical bearing 14 that cooperate with each other.

[0070] In this example, a spherical bearing 14 is used to form the self-adjusting structure in the valve plate assembly and serves as the connecting component that directly connects the entire valve plate assembly to the valve stem assembly. This ensures the reliability and effectiveness of the self-adjustment when the entire valve plate assembly is in operation, and also ensures the stability and reliability of the connection with the valve stem assembly.

[0071] The spherical bearing 14 is connected and fixed to the inner valve stem 15 and the outer valve stem 23, which are coaxially distributed, respectively. The valve plate seat 12 is fixedly mounted on the spherical bearing 14 through the cooperation of the bearing pressure plate 13. At the same time, the valve plate 10 is fixedly mounted on the valve plate seat 12 through the corresponding valve plate pressure plate 11, thereby forming a self-adjustable parallel valve plate assembly.

[0072] Specifically, the spherical plain bearing 14 in this valve plate assembly is a spherical sliding bearing, consisting of an outer ring and an inner ring that fit together. The sliding contact surfaces of the two are an inner spherical surface and an outer spherical surface, which allows them to rotate and swing at any angle when they move relative to each other.

[0073] The resulting spherical bearing has the characteristics of high load capacity, impact resistance, corrosion resistance, wear resistance, self-aligning, and good lubrication, making it well-suited for this lift valve structure.

[0074] See further Figure 7 The valve plate seat 12 is integrally formed and includes a seat body and a valve plate support portion extending outward from the seat body. The seat body is used to cooperate with the bearing pressure plate 13 to form a locking portion that can cooperate with the spherical plain bearing 14, and has a first locking hole corresponding to the first end of the outer ring portion of the spherical plain bearing 14.

[0075] Correspondingly, the bearing pressure plate 13 and the seat portion of the valve plate seat 12 are arranged in a relative distribution and fit together, and can be fixed to the valve plate seat 12 as a whole by a fastener. At the same time, the bearing pressure plate 13 has a second snap-fit ​​hole corresponding to the other end of the outer ring portion of the spherical bearing 14.

[0076] Thus, when the seat portion of the valve plate seat 12 is pressed into the bearing pressure plate 13, for example, the seat portion of the valve plate seat 12 and the bearing pressure plate 13 are respectively assembled onto the outer ring portion of the spherical plain bearing 14 from both ends. The two are mated together and can be connected and fixed along the circumference of the mating portion by corresponding fixing screws. At the same time, the first snap-fit ​​hole in the seat portion of the valve plate seat 12 mates with the second snap-fit ​​hole on the bearing pressure plate 13 to form a snap-fit ​​portion corresponding to the outer ring portion of the spherical plain bearing 14. The two ends of the snap-fit ​​portion formed in this way are clamped to the ends of the outer ring portion of the spherical plain bearing 14 by elastic sealing rings 29, thereby fixing the valve plate seat 12 as a whole onto the outer ring portion of the spherical plain bearing 14. Here, the bearing pressure plate 13 and the valve plate seat 12 are clamped and fixed to the spherical plain bearing 14 by the elastic sealing rings 29, which can ensure both the sealing performance of the overall structure and the reliability of the clamping and fixing structure.

[0077] See Figure 7 The valve plate support in the valve plate seat 12 is used to install the corresponding valve plate 10. In order to adapt to the high-frequency operation of the valve plate assembly in the lift valve, the valve plate 10 here is cooperated with the valve plate support in the valve plate seat 12 through the valve plate pressure plate 11 to achieve stable and reliable fixation of the valve plate 10.

[0078] Furthermore, as a further preferred option, in this example, the valve plate support portion in the valve plate seat 12 is designed as a bowl shape with an arc-shaped cross section, which can effectively improve the load-bearing capacity of the valve plate seat 12 and reduce the amount of deformation.

[0079] In this valve plate assembly, the valve plate 10 serves as a sealing element, used to cooperate with the valve seat 6 to form a corresponding hard seal structure. The valve plate 10 is fixed to the valve plate seat 12 by a corresponding valve plate pressure plate 11 and remains parallel to the valve seat 6.

[0080] In this valve plate assembly, the valve plate 10 is a preferred embodiment, which is made of a smooth stainless steel plate by laser cutting in one go. This can greatly improve the strength of the entire valve plate 10 and keep it flat, thereby improving the reliability of the sealing fit between the valve plate 10 and the valve seat 6.

[0081] The valve plate assembly formed based on the aforementioned scheme can be self-adjustingly mounted on the valve stem assembly and can move back and forth at high speed between the valve seat 6 and the valve cover 17 under the drive of the valve stem assembly. When the valve plate assembly moves towards the valve seat 6, when the valve plate 10 in the valve plate assembly contacts the sealing end face of the valve seat 6, the valve seat 6 is pressed by the driving force of the valve stem assembly to form a hard sealing structure distributed circumferentially along the sealing end face of the valve seat 6.

[0082] If the coaxiality of the valve stem assembly relative to the valve seat 6 changes, such as Figure 6As described above, a deviation angle a° is formed. At this time, the valve stem assembly will drive the valve plate assembly to move relative to the valve seat 6 at the deviation angle a°. When the valve plate 10 in the valve plate assembly contacts the sealing end face of the valve seat 6, based on the driving force of the valve stem assembly and the hard contact between the valve plate 10 and the valve seat 6, the valve plate 10 will drive the valve plate seat 12 to automatically adjust parallel movement around the spherical bearing 14 until the valve plate 10 is parallel to the sealing end face of the valve seat 6. At that time, the valve plate 10 will synchronously press the sealing end face of the valve seat 6 to form a hard sealing structure distributed circumferentially along the sealing end face of the valve seat 6.

[0083] The resulting lift valve design innovatively incorporates a positioning bracket (9) to directly connect and fix the valve seat 6 and valve cover 17 into a single unit. This significantly reduces the non-parallelism between the valve seat 6 and valve plate 10 when the inner or outer walls of the furnace deform. Furthermore, the self-adjusting structure formed by the introduced spherical bearing (14) automatically adjusts the valve plate 10 to parallel position after contact with the valve seat 6. Therefore, this design greatly improves the stability and reliability of the lift valve's sealing performance, effectively overcoming the problem in existing lift valve designs where furnace deformation due to temperature changes during equipment operation leads to loss of parallelism between the valve seat and valve plate assembly, resulting in leakage at the sealing surface.

[0084] Example 2

[0085] Based on the example solution in Example 1, this example presents a further optimization scheme to further improve the performance of the entire lift valve.

[0086] In the lift valve solution presented in Example 1, the corresponding seal is based on the hard seal formed between the valve plate 10 and the valve seat 6 in the valve plate assembly. Considering the working state and environment of the lift valve, this example solution preferably uses cobalt-tungsten alloy overlay welding on the sealing surface of the valve seat 6, so that the hardness of the sealing surface of the valve seat 6 reaches 45HRC, thereby greatly improving the wear resistance of the valve seat. Since there is a certain hardness difference between the valve seat and the valve plate, cold welding will not occur.

[0087] Meanwhile, based on the characteristic that the valve plate 10 can generate elastic deformation, this lift valve design further forms two sets of sealing structures on the end face where the valve seat 6 and the valve plate 10 mate. These structures can respectively mate with the valve plate in its normal state and the valve plate in its elastic deformation state, thereby forming two sets of seals between the valve seat 6 and the valve plate 10, further improving the reliability of the overall lift valve sealing performance.

[0088] Specifically, in this example, two stepped hard sealing rings are formed on the sealing surface of the valve seat 6 to seal with the sealing surface of the valve plate 10, forming a double hard sealing structure, which greatly improves the reliability of the sealing structure formed between the valve seat and the valve plate.

[0089] As a preferred option, the two stepped hard sealing rings are concentrically distributed on the sealing surface of the valve seat 6.

[0090] See Figure 8 In this scheme, a first sealing structure 30 is provided on the sealing surface of the valve seat 6. The first sealing structure 30 is used to seal with the valve plate 10 surface in normal state, forming a first sealing line structure between the two.

[0091] Specifically, the first sealing structure 30 is an overall first hard sealing ring structure, so as to form a first sealing line structure on the sealing surface of the valve seat 6.

[0092] Preferably, the first sealing structure 30 of this hard sealing ring structure is formed by depositing a layer of hard alloy on the corresponding peripheral area of ​​the sealing surface of the valve seat 6 in a ring shape. The overall hardness of the first sealing structure 30 thus formed reaches 45HRC, thereby greatly improving the wear resistance of the valve seat.

[0093] The first sealing structure has a certain hardness difference with the valve plate, preventing cold welding. Furthermore, the first sealing structure adopts a rounded transition, which not only increases its adaptability to the valve plate but also improves its impact resistance.

[0094] The first sealing structure 30 formed by this scheme can directly cooperate with the valve plate 10 in its normal state to form a first sealing line structure when the valve seat 6 and the valve plate 10 make initial hard contact.

[0095] Meanwhile, this solution further provides a second sealing structure 31 on the sealing surface of the valve seat 6. This second sealing structure 31 corresponds to the deformable part of the valve plate 10 and is located on the deformation stroke where the valve plate 10 deforms after contacting the valve seat 6. This second sealing structure 31 is used to seal the deformable part of the valve plate 10, forming a second sealing line structure between them.

[0096] Specifically, the second sealing structure 31 is an overall second hard sealing ring structure, forming a second sealing structure on the sealing surface of the valve seat 6. Simultaneously, the second sealing structure 31 is located inside the first sealing structure 30, thus forming a second sealing line structure distributed inside the first sealing line structure on the sealing surface of the valve seat 6. Furthermore, the height of the second sealing structure 31 (relative to the sealing surface of the valve seat 6) is lower than the height of the first sealing structure 30 (relative to the sealing surface of the valve seat 6). Therefore, the second sealing structure 31 and the first sealing structure 30 cooperate to form two stepped hard sealing rings on the sealing surface of the valve seat 6, sealing against the sealing surface of the valve plate 10, thus forming two hard sealing structures and ensuring a sealing effect.

[0097] Preferably, the second sealing structure 31 of this hard sealing ring structure is formed by depositing a layer of hard alloy in a ring-shaped arrangement on the sealing surface of the valve seat 6 within the area inside the first sealing structure 30. The height of this hard alloy layer is lower than that of the hard alloy layer forming the first sealing structure 30, thus creating two stepped hard sealing rings on the sealing surface of the valve seat 6. The resulting second sealing structure 31 achieves an overall hardness of 45 HRC, significantly improving the wear resistance of the valve seat.

[0098] The second sealing structure 31 has a certain hardness difference with the valve plate, preventing cold welding. Furthermore, the second sealing structure 31 adopts a rounded transition, which not only increases its adaptability to the valve plate but also improves its impact resistance.

[0099] The second sealing structure 31 formed by this scheme is distributed inside the first sealing structure 30 and its height is lower than that of the first sealing structure 30. In this way, after the valve seat 6 and the valve plate 10 make initial hard contact, the second sealing structure 31 will make hard sealing cooperation with the deformed part on the valve plate 10, forming a second sealing line structure between the two.

[0100] Accordingly, two stepped hard sealing rings will be formed on the sealing surface of the valve seat 6. When the valve seat 6 initially contacts the valve plate 10, the first sealing structure 30, located in the outer region and with a higher height on the valve seat 6, will first make hard contact with the valve plate 10 in its normal state, forming a first sealing line structure. Subsequently, the valve plate 10 further presses against the valve seat 6, and the valve plate 10 and the first sealing structure 30 on the valve seat 6 continue to maintain a seal. Simultaneously, based on its own elasticity, the valve plate 10 will undergo a certain deformation. The deformed portion will make hard contact with the second sealing structure 31, located inside the first sealing structure 30 and with a lower height on the valve seat 6, forming a second sealing line structure 31. At this time, the valve plate 10 and the first sealing structure 30 on the valve seat 6 continue to maintain a seal. Thus, when the valve plate 10 and the valve seat 6 are stably fitted, two sets of sealing line structures will be formed simultaneously between the valve plate 10 and the valve seat 6, thereby further improving the stability and reliability of the sealing fit between the valve plate 10 and the valve seat 6.

[0101] Building upon this, the present solution further introduces a compressed air isolation band structure 32 into the valve seat 6. This structure is used to introduce compressed gas 34 from the outside and form a compressed air isolation band 33 between the two sets of sealing line structures between the valve seat 6 and the valve plate 10. This further improves the stability and reliability of the sealing fit between the valve plate 10 and the valve seat 6. Here, the pressure of the compressed air is higher than the flue gas pressure.

[0102] Combination Figure 1 and Figure 8As shown, the compressed air isolation belt structure 32 is mainly composed of an air chamber 32-1 located in the valve seat 6, an air inlet channel 32-2, an air outlet channel 32-3, and an isolation air channel 32-4 located on the sealing surface of the valve seat 6.

[0103] The air chamber 32-1 here is located inside the valve seat 6 and is used to store compressed air 34. Its specific structural shape depends on the actual needs and will not be described in detail here.

[0104] The air intake channel 32-2 is located in the valve seat 6 and connects the air chamber 32-1 in the valve seat 6 to an external compressed air source, so as to introduce external compressed air into the air chamber 32-1 in the valve body 6.

[0105] An air outlet passage 32-3 is provided in the valve seat 6 and connects the air chamber 32-1 in the valve seat 6 with the isolation air passage 32-4 on the sealing surface of the valve seat 6, so as to lead the compressed air in the air chamber 32-1 in the valve body 6 to the sealing structure between the valve seat 6 and the valve plate 10, so as to form a corresponding compressed air isolation zone between the two.

[0106] The isolation air passages 32-4 are distributed on the sealing surface of the valve body 6 and are located between the first sealing structure 30 and the second sealing structure 31. They are used to form a compressed air isolation band 33 between the two sets of sealing line structures between the valve seat 6 and the valve plate 10 when the valve seat 6 and the valve plate 10 are sealed together, so as to further improve the stability and reliability of the sealing fit between the valve plate 10 and the valve seat 6.

[0107] The specific structure of the isolation airway 32-4 is not limited here and can be determined according to actual needs.

[0108] As an alternative, the compressed air isolation band structure 32 may not have an isolation air passage 32-4. Instead, compressed air can be directly drawn out through the outlet passage 32-3. The outlet of the outlet passage 32-3 is located on the sealing surface of the valve body 6 and between the first sealing structure 30 and the second sealing structure 31. In this way, the area between the valve seat 6 and the valve plate 10, located between the two sets of sealing line structures, can be used as the isolation air passage. Compressed gas can be drawn out through the outlet passage 32-3, thereby forming a compressed air isolation band 33 between the two sets of sealing line structures between the valve seat 6 and the valve plate 10. This further improves the stability and reliability of the sealing fit between the valve plate 10 and the valve seat 6.

[0109] As an example, in order to effectively introduce compressed air, this solution uses stainless steel air pipes 8, right-angle pipe joints 7, tee pipe joints 18, and straight pipe joints 19 to form multiple air passages, so as to quickly and stably introduce compressed air.

[0110] by Figure 1Taking the illustrated scheme as an example, in the valve seat 6, its air intake channels 32-2 are distributed on the side wall of the valve seat 6. The inlet of each air intake channel 32-2 is connected to one end of the corresponding stainless steel air pipe 8 through a right-angle pipe joint 7. The other end of the stainless steel air pipe 8 is connected to a three-way pipe joint 18. The three-way pipe joint 18 is connected to a straight pipe joint 19 installed on the valve cover 17. The straight pipe joint 19 is connected to the compressed air source through the stainless steel air pipe 8. This forms multiple air passages to introduce compressed air synchronously, quickly and stably in a multi-path manner.

[0111] Based on the aforementioned optimization scheme, when the valve seat 6 and valve plate 10 are in sealing contact, two sets of sealing line structures can be formed simultaneously between them, and a compressed air isolation zone can be formed synchronously between the two sets of sealing line structures. The synchronous sealing of the two sets of sealing line structures effectively improves the sealing effect and performance. Furthermore, the compressed air in the isolation zone between the two sets of sealing line structures has a pressure higher than the flue gas pressure, which can further effectively expel the flue gas, making it more difficult for the medium to pass through the sealing surface, thus further promoting sealing. This effectively overcomes the problem in existing lift valve designs where high frequency of use easily leads to severe collisions between the valve seat and valve plate, causing scratches, dents, and fatigue on the sealing surface, thereby affecting the sealing performance and service life of the lift valve.

[0112] Example 3

[0113] Based on the example scheme in Example 1, this example presents an optimized design scheme for the cylinder bracket 22 in Example 1, thereby further improving the performance of the lifting valve.

[0114] See Figure 9 The cylinder bracket 22 given in this example mainly includes two parts: the bracket body 22-1 and the stuffing box 22-2. The stuffing box 22-2 is integrally formed at the front end of the bracket body 22-1, and the stuffing box 22-2 and the bracket body 22-1 are coaxially distributed.

[0115] The stuffing box 22-2 can accommodate the corresponding outer valve stem 23 through which it passes, and the stuffing box 22-2 is filled with corresponding packing to form a dynamic seal on the outer valve stem 23.

[0116] This integrated design of the stuffing box 22-2 and the bracket allows for a more precise and stable valve stem movement trajectory. The packing inside the stuffing box 22-2 has a very high degree of concentricity with the valve stem, preventing severe wear in certain parts of the packing and ensuring that the loss is basically consistent.

[0117] As a further preferred option, in this example, the cylinder bracket 22 is designed with a symmetrical top and bottom, which can distribute the force evenly and further ensure the reliability of the lifting valve.

[0118] This cylinder support design effectively overcomes the problem in the existing lift valve design where the cylinder bracket is installed on the outer furnace body and below the neutral line of the lift valve. This causes the cylinder to sink when the valve is closed, resulting in the packing being tight at the top and loose at the bottom, which can easily lead to packing leakage.

[0119] See Figure 10 As a further preferred option, the cylinder bracket 22 in this example is directly fixed on the valve cover 17 during assembly; at the same time, a positioning step 35 is provided at the connection and mating point between the cylinder bracket 22 and the valve cover 17 to further improve and ensure the concentricity between the cylinder bracket 22, the valve seat 6 and the valve cover 17, thereby ensuring the stability of the valve stem assembly operation.

[0120] As a further preferred embodiment, in this example, when connecting the cylinder 25 to the cylinder bracket 22, the cylinder 25 is coaxially positioned at the mounting end of the cylinder bracket 22. Simultaneously, the extension rod of the cylinder 25 is connected to the outer valve stem 23 using a self-adjusting floating joint 24. This allows for a certain degree of form and position error between the cylinder and the valve stem. This effectively overcomes the problems of existing lift valves where the valve stem assembly and cylinder use a threaded connection, requiring extremely high relative positioning; and where significant changes in concentricity after wear and tear lead to greater wear and reduced service life of the cylinder.

[0121] Example 4

[0122] Based on the example scheme in Example 3, this example presents an optimized design scheme for the stuffing box in Example 3, thereby further improving the performance of the lift valve.

[0123] See Figure 11 In this example, graphite packing 36 is installed in the stuffing box 22-2 as sealing packing to form a dynamic seal between the stuffing box and the outer valve stem.

[0124] As a further optimization, this example also provides a compressed air chamber ring 37 in the graphite packing 36 of the stuffing box to introduce compressed air to form a corresponding isolation zone, so as to play an auxiliary sealing role when the packing is severely damaged.

[0125] See Figure 13 In this example, the compressed air chamber ring 37 is a circular structure, specifically including a circular body 37-1 of a certain length and thickness, and a number of ventilation holes 37-2 are opened on the side wall of the circular body 37-1 along the circumferential direction.

[0126] The annular body 37-1 is a metal annular body, and its overall structure is compatible with the internal structure of the stuffing box 22-2; the hollow inner cavity 37-4 of the annular body 37-1 is used to introduce compressed gas and form a high-pressure gas isolation zone inside it.

[0127] Specifically, an annular air inlet groove 37-3 is formed circumferentially on the outer wall of the annular body 37-1, and several vent holes 37-2 communicating with the inner cavity of the annular body 37-1 are evenly opened at the bottom of the annular air inlet groove 37-3. The annular air inlet groove 37-3 provides initial buffering for the introduced compressed airflow, forming a stable high-pressure air ring within the annular air inlet groove, which is then synchronously introduced into the annular body 37-1 through the several vent holes 37-2, ensuring the stability of the high-pressure gas isolation zone.

[0128] Based on this, a concave annular outlet groove 37-5 is formed circumferentially on the inner wall of the annular body 37-1, corresponding to the position of the annular inlet groove 37-3 on the outer wall. The outlets of several vent holes 37-2 are located within the annular outlet groove 37-5. The annular outlet groove 37-5 rapidly guides the high-pressure gas introduced through the vent holes 37-2, quickly forming a stable high-pressure gas isolation zone within the inner cavity of the annular body 37-1. The dispersed guidance of the annular outlet groove 37-5 allows the gas pressure within the annular body 37-1 to quickly stabilize, preventing pressure fluctuations in certain areas and ensuring the stability of the high-pressure gas isolation zone. Simultaneously, because the annular outlet groove 37-5 is concave, and the outlets of the vent holes 37-2 are located within the annular outlet groove 37-5, the unobstructed flow of each vent hole 37-2 is ensured, preventing blockage.

[0129] In addition, the dimensions and structure of the compressed air chamber ring 37 (such as length, sidewall thickness, etc.) are not limited here, and can be determined according to actual needs.

[0130] Concurrently, in this example, corresponding vent holes 22-3 are provided on the side wall of the stuffing box 22-2. These vent holes 22-3 correspond to the annular air inlet grooves 37-3 on the compressed air chamber ring 37, and these vent holes are connected to corresponding compressed air sources through corresponding connectors and air pipes 39. The pressure of the compressed air introduced here is greater than that of the medium and atmospheric pressure.

[0131] Specifically, in this example, when the compressed air chamber ring 37 is configured to cooperate with the stuffing box 22-2 and the corresponding graphite packing 36, the compressed air chamber ring 37 is located entirely within the inner cavity of the stuffing box 22-2, with its annular air inlet groove 37-3 corresponding to the vent hole 22-3 on the stuffing box 22-2. Since the overall structure of the compressed air chamber ring 37 is fitted with the inner wall of the stuffing box 22-2, the outer wall of the compressed air chamber ring 37 will fit snugly against the inner wall of the stuffing box 22-2. Thus, an annular air inlet chamber is formed between the annular air inlet groove 37-3 on the compressed air chamber ring 37 and the inner wall of the stuffing box 22-2, and is connected to an external compressed air source through the vent hole 22-3, and is connected to the inner cavity of the compressed air chamber ring 37 through the vent hole 37-2. Based on this, graphite packing 36 is then installed at both ends of the compressed air chamber ring 37. The graphite packing 36 distributed at both ends seals both ends of the compressed air chamber ring 37, thereby forming a high-pressure gas isolation chamber within the compressed air chamber ring 37.

[0132] In a preferred embodiment, a corresponding compressed air chamber ring 37 is provided in the middle of the graphite packing 36, that is, the graphite packing 36 on both sides clamps the compressed air chamber ring 37 in the middle.

[0133] Based on this, compressed air with a pressure greater than that of the medium and atmospheric pressure is further introduced. At this time, the compressed air enters at high speed through the vent holes 22-3 on the stuffing box 22-2 into the annular air intake chamber formed between the compressed air chamber ring 37 and the inner wall of the stuffing box 22-2. The annular air intake chamber buffers the incoming high-speed, high-pressure gas, stabilizes the air pressure and flow rate, and forms a stable high-pressure air ring. Then, it is simultaneously introduced through several vent holes 37-2 into the high-pressure gas isolation chamber formed by the inner cavity 37-4 of the compressed air chamber ring 37 and the graphite packing 36 on both sides.

[0134] At the same time, the compressed air entering the high-pressure gas isolation chamber will fill the high-pressure gas isolation chamber and form a high-pressure gas isolation zone inside the high-pressure gas isolation chamber to separate the graphite packing distributed on both sides of the high-pressure gas isolation chamber. This will play an auxiliary sealing role when the packing is severely damaged, and improve the stability and reliability of the seal between the stuffing box and the outer valve stem.

[0135] Example 5

[0136] Based on the example scheme in Example 1, this example presents an optimized design scheme for the inner bearing assembly 2 and the outer bearing assembly 21 in Example 1, thereby further improving the performance of the lift valve.

[0137] See Figure 12 In this example, the inner bearing assembly 2 and the outer bearing assembly 21 are constructed using corresponding inner linear bearings and outer linear bearings, respectively, which are used to cooperate with the inner valve stem 15 and the outer valve stem 23.

[0138] This design uses internal and external linear bearings to replace the rolling bearing adjustment assembly in existing lift valve solutions, resulting in stable overall operation, precise dimensions, and a compact size. Furthermore, the contact area between the linear bearing and the valve stem is larger than that of the rolling bearing, thus reducing the surface load on the valve stem.

[0139] The specific structure of the linear bearing is not limited here and can be determined according to actual needs.

[0140] As a further optimization, this example provides a protective cover 38 and a sealing ring 37 around the inner linear bearing 2 to protect the inner linear bearing 2.

[0141] Specifically, in this example, a sealing ring 37 is provided at the outer end of the inner linear bearing 2 facing the outer bearing assembly 21, and a protective cover 38 is fitted on the inner end of the inner linear bearing 2 extending into the inner wall of the furnace body, so as to achieve simultaneous protection of both ends of the inner linear bearing 2.

[0142] Since the lifting valve operates in an environment containing oil, the protective cover 38 sets are installed to protect the inner linear bearing 2, thereby preventing oil from entering the linear bearing and accumulating and clogging it, which could cause the valve to jam or even become stuck and unable to operate. This effectively improves the reliability of the entire lifting valve operation.

[0143] Finally, it should be noted that, based on the aforementioned example solutions, the inner wall welded flange, positioning bracket, valve cover, and cylinder bracket can be cast in specific applications. This results in high machining accuracy and eliminates the need for the adjustment structure required in the original lift valve solution. At the same time, multiple parts can be combined to form a single casting, resulting in lower weight and fewer fasteners required for the same structure. This facilitates standardization and reduces product costs and improves efficiency.

[0144] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of the invention. Various changes and modifications can be made to the invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the present invention as claimed. The scope of protection of this invention is defined by the appended claims and their equivalents.

Claims

1. A self-adjusting high sealing performance lifting valve for regenerative waste gas incinerator, comprising an inner bearing assembly, a valve stem assembly, an outer bearing assembly, a cylinder, a valve seat, a valve cover, a valve plate assembly, a cylinder support; characterized in that It also includes an inner wall welded flange and a positioning support; The valve seat is arranged in the inner wall of the furnace body of the regenerative waste gas incinerator through the inner wall welded flange; The valve cover is fixedly arranged in the outer wall of the furnace body of the regenerative waste gas incinerator in a concentric manner corresponding to the valve seat; the valve seat and the valve cover are directly connected and fixed through the positioning support; The inner valve stem part of the valve stem assembly is arranged in the valve seat through the inner bearing assembly at one end, and is connected with the valve plate assembly at the other end; the outer valve stem part of the valve stem assembly is coaxially arranged corresponding to the inner valve stem part, is arranged in the cylinder support through the outer bearing assembly at one end, and is connected with the valve plate assembly at the other end; the cylinder support is fixedly arranged on the valve cover; the cylinder is arranged on the cylinder support and drives the outer valve stem part in the valve stem assembly; The cylinder support comprises a support body and a stuffing box, the stuffing box is integrally formed at the front end of the support body, and the outer valve stem passes through the stuffing box; graphite packing is used between the stuffing box and the outer valve stem; the stuffing box is provided with a compressed air cavity ring at the middle position of the graphite packing; The compressed air cavity ring is in the form of a whole annular structure, an annular air inlet groove is formed on the outer side wall of the annular body in the circumferential direction, a plurality of air holes communicating with the inner cavity of the annular body are uniformly arranged at the bottom of the annular air inlet groove, and an inner concave annular air outlet groove is formed on the inner side wall of the annular body in the circumferential direction corresponding to the position of the annular air inlet groove on the outer side wall, and the outlets of the plurality of air holes are located in the annular air outlet groove; The valve plate assembly is connected and matched with the inner valve stem part and the outer valve stem part in the valve stem assembly through a self-adjusting structure, can form a sealing structure with the valve seat under the drive of the valve stem assembly, and can automatically adjust to keep parallel with the valve seat after contacting with the valve seat; The valve plate of the valve stem assembly can be elastically deformed, and two groups of sealing structures are formed on the cooperating end surfaces, can be matched with the valve plate in the normal state and the elastically deformed valve plate respectively, so that two groups of seals are formed between the valve seat and the valve plate, and two stepped hard sealing rings are formed on the sealing surface of the valve seat, The first hard sealing ring structure can form a first sealing line structure by being matched with the valve plate in the normal state when the valve seat and the valve plate are preliminarily in hard contact; The second hard sealing ring structure arranged on the sealing surface of the valve seat is located on the inner side of the first hard sealing ring structure, corresponds to the deformable part of the valve plate, and is located on the deformation stroke of the deformed valve plate and valve seat after contacting, and is used for sealing and matching the deformed part of the valve plate to form a second sealing line structure between them; When the valve plate and the valve seat are stably matched, two groups of sealing line structures will be formed between the valve plate and the valve seat.

2. The self-adjusting high sealing performance enhancing poppet valve for a regenerative exhaust gas incinerator according to claim 1, characterized in that, The positioning support is provided with a positioning step connected with the valve seat or / and the valve cover.

3. The self-adjusting high sealing performance enhancing poppet valve for a regenerative exhaust gas incinerator according to claim 1, characterized in that, The valve plate assembly comprises a valve plate, a valve plate seat, a bearing pressing plate, and a joint bearing; the joint bearing is connected with the inner valve rod part and the outer valve rod part in the valve rod assembly; the valve plate seat is fixedly arranged on the joint bearing through the bearing pressing plate; and the valve plate is arranged on the valve plate seat.

4. The self-adjusting high sealing performance enhancing poppet valve for a regenerative exhaust gas incinerator according to claim 1, characterized in that, The valve seat is subjected to hardfacing cobalt tungsten alloy treatment corresponding to the sealing surface of the valve plate assembly.

5. The self-adjusting high sealing performance enhancing poppet valve for a regenerative exhaust gas incinerator according to claim 1, characterized in that, The valve seat is provided with a compressed air isolation belt structure.

6. The self-adjusting high sealing performance enhancing poppet valve for a regenerative exhaust gas incinerator according to claim 1, wherein The inner bearing assembly is provided with a protective cover and a sealing ring around the periphery.

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