Packing assembly for piston gas compressor

Abstract

The invention relates to a packing assembly for a piston gas compressor, belongs to the technical field of compressors, and aims at solving the problems that when an existing packing assembly for the piston gas compressor operates at high pressure for a long period, a gap is increased after a sealing ring is abraded, sealing failure is caused, shutdown replacement is needed, and accumulated heat accelerates degradation of a sealing ring material, and abrasion is aggravated. According to the technical scheme, the packing set is formed by combining a gland, a plurality of sealing pieces and a sealing end cover, and a rod body channel is formed in the packing set in a penetrating mode; the packing groove is internally provided with a sealing mechanism, the sealing mechanism comprises a three-petal type adjustable sealing ring, an abutting hoop ring with a conical groove and a wave spring, the wave spring pushes the abutting hoop ring to force sealing petals to gather towards the circle center through the conical groove, and the abrasion gap is automatically compensated; a circulating heat dissipation channel is formed in the filler group, and external circulating fluid can be introduced into the circulating heat dissipation channel for heat dissipation; according to the packing assembly, the sealing effect can be maintained under the non-stop condition, the maintenance cost is reduced, the working temperature is controlled, and the packing assembly is adaptive to the high-pressure long-period operation working condition.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more particularly to a packing assembly for a piston gas compressor. Background Technology

[0002] In key sectors such as oilfield development and natural gas transportation, compressors are widely used for pressurization in oil and gas extraction and pressurization in long-distance natural gas pipelines. In these scenarios, compressors often face harsh operating conditions of high pressure, high load, and continuous operation, placing higher demands on the sealing stability and durability of the packing assembly. Existing packing assemblies typically consist of multiple sealing rings and connecting parts. The tight fit between the sealing rings and the piston rod forms a sealing surface, blocking the leakage path of high-pressure gas inside the cylinder. However, under the aforementioned harsh operating conditions, existing packing assemblies struggle to meet the requirements for long-term stable operation, exhibiting the following problems: When a compressor operates continuously, especially under high-pressure, long-cycle conditions, continuous friction and wear occur between the sealing ring and the high-speed reciprocating piston rod. As operating time accumulates, the inner diameter of the sealing ring gradually increases due to wear, and the clearance between it and the piston rod also increases. This increased clearance directly leads to a decrease in sealing effectiveness and an increase in gas leakage. In existing designs, when wear reaches a certain level, it is usually necessary to shut down the compressor and replace the entire worn sealing ring to restore sealing performance. This process not only involves production interruption but also increases maintenance costs and spare parts consumption. On the other hand, the friction between the sealing ring and the piston rod, as well as the high-pressure gas compression process itself, will generate heat. The heat will accumulate inside the packing assembly. If it cannot be dissipated in time, it will cause the local ambient temperature of the sealing ring to rise. For sealing rings made of certain materials, continuous high temperature may accelerate the degradation of their material properties, such as a decrease in elasticity or a change in hardness. This, in turn, may further aggravate the wear process and affect the long-term stability of the seal.

[0003] To address the aforementioned problems, this invention proposes a packing assembly for a piston gas compressor. Summary of the Invention

[0004] The purpose of this invention is to address the shortcomings of existing technologies, such as the wear of the sealing ring leading to increased gaps and sealing failure during long-term high-pressure operation of traditional compressor packings, requiring shutdown for replacement, and the accelerated material degradation due to heat accumulation, which further exacerbates wear. Therefore, this invention proposes a packing assembly for piston gas compressors.

[0005] To achieve the above objectives, the present invention adopts the following technical solution: A packing assembly for a piston gas compressor, installed at one end of the compressor cylinder, for sealing the gap between the cylinder and the piston rod, comprising: A packing assembly, wherein the packing assembly is assembled by connecting multiple connectors in sequence, and each of the multiple connectors has a rod channel through which the piston rod passes; Multiple sealing mechanisms are respectively installed in the corresponding connecting parts. Each sealing mechanism includes an adjustable sealing ring and an abutment ring. The adjustable sealing ring is composed of three arc-shaped sealing petals and is sleeved on the piston rod. A conical groove is provided on one side of the abutment ring. The conical inner wall of the conical groove abuts against the inclined surface of one side of the three arc-shaped sealing petals of the adjustable sealing ring. A wave spring, located on the side of the abutment ring opposite to the adjustable sealing ring, provides axial thrust to the abutment ring. This thrust is converted into radial pressure through the tapered groove, causing the three arc-shaped sealing flaps to converge toward the piston rod to form a dynamic seal and automatically compensate for wear.

[0006] In one possible design, the plurality of connecting members include a gland, a plurality of seals and a sealing end cap arranged in sequence, which are connected and combined in sequence to form a packing assembly. The gland and the seals have protrusions on the side facing the cylinder, and the seals and the sealing end caps have packing grooves that slide with the protrusions on the same side. The packing grooves are used to accommodate the sealing mechanism.

[0007] In one possible design, a first side sealing ring is fixed to the side of the abutment ring near the wave spring, one end of the wave spring abuts against the adjacent protrusion, and the other end abuts against the first side sealing ring; a second side sealing ring is provided on the side of the adjustable sealing ring opposite to the abutment ring, and both the first side sealing ring and the second side sealing ring are in a sealing sliding fit with the inner wall of the packing groove.

[0008] In one possible design, a slot is provided in the packing groove, and a clamp is engaged in the slot. Three limiting protrusions are fixedly installed on the inner wall of the clamp. Guide limiting grooves are provided on the outer walls of the three sealing petals of the adjustable sealing ring. Three corresponding clearance grooves are provided on one side of the abutting ring. The guide limiting grooves and the three clearance grooves are all slidably engaged with the corresponding limiting protrusions, which are used to provide corresponding restrictions on the adjustable sealing ring to prevent it from rotating.

[0009] In one possible design, a heat dissipation mechanism is also included, comprising annular cooling channels formed inside the plurality of seals and sealing end caps. The cooling channels are annular, and each seal and sealing end cap has at least one cooling channel. Each of the plurality of seals and corresponding sealing end caps has two connecting channels, both of which are connected to the corresponding cooling channels. The connecting channel within the seal extends through both ends of the seal, and the connecting channel within the sealing end cap extends through one end of the sealing end cap. The plurality of connecting channels on the same straight line are connected to ensure liquid flow. The gland has two inlet / outlet channels inside, both of which are connected to the two connecting channels of adjacent seals. Two inlet / outlet connectors are fixedly installed on one side of the gland, each corresponding to a corresponding inlet / outlet channel, for connection to external inlet / outlet pipes to facilitate the entry and exit of circulating fluid.

[0010] In one possible design, a sealing gasket is provided between two adjacent connectors, and the sealing gasket is fitted around the outer periphery of the protrusion.

[0011] In one possible design, the inner wall of the rod channel is provided with a spiral groove, which cooperates with the outer wall of the piston rod to form a labyrinth throttling effect and generate a pumping reverse thrust effect on the leaking gas when the piston rod reciprocates.

[0012] In one possible design, the gland, the plurality of seals, and the sealing end cap are fixedly connected to bolts via through threaded holes.

[0013] In one possible design, the gland is located outside the cylinder and is fixedly connected to the cylinder by bolts.

[0014] In this application, during use, the packing assembly is slidably inserted into one end of the cylinder, ensuring that the piston rod passes through the rod channel and maintains a sliding fit with the inner wall of the channel. Then, the gland is fixed to the cylinder with bolts to complete the overall installation of the packing assembly. Inside the packing assembly, the wave spring is in a pre-compressed state, which can continuously apply axial thrust to the abutment ring. The abutment ring generates radial pressure on the three arc-shaped sealing petals of the adjustable sealing ring through the conical inner wall of the conical groove, thereby allowing the three sealing petals to tightly fit against the outer wall of the piston rod. In conjunction with the first side sealing ring and the second side sealing ring, a seal can be provided for the gap between the compressor cylinder and the corresponding piston rod. As operating time increases, multiple sealing rings are prone to wear due to continuous friction, and the gap between them and the piston rod will gradually increase. During this process, the wave spring will gradually release the preload, thereby pushing the abutment ring to move axially towards the adjustable sealing ring. The conical inner wall of the conical groove will increase the squeezing effect on the three arc-shaped sealing petals, forcing the three sealing petals to converge towards the center. This can automatically compensate for the gap caused by wear, enabling it to maintain a tight fit with the outer wall of the piston rod and maintain a stable sealing effect. The clamp is fixed in the packing groove by the clamp groove. The limiting protrusion on its inner wall is embedded in the guide limiting groove of the adjustable sealing ring sealing petal, and at the same time slides with the relief groove of the abutting clamp ring. During the process of the adjustable sealing ring moving back and forth with the piston rod and the wear compensation and gathering, the multiple limiting protrusions can limit the rotation of the adjustable sealing ring, thereby ensuring that its sealing petal is always in the correct working position and avoiding sealing failure due to rotation. During operation, the friction between multiple sealing rings and the piston rod generates heat, and the compression of high-pressure gas also transfers some heat to the packing assembly. At this time, the external circulating fluid can be connected through pipes and inlet / outlet connectors, enters the connecting flow channel of adjacent seals through the inlet / outlet channels in the gland, and then flows into the annular cooling flow channel in each seal and sealing end cap through the connected flow channel. When the circulating fluid flows in the cooling flow channel, it can fully absorb the heat generated by the packing assembly, and then flows out from the corresponding inlet / outlet connector along another set of connecting flow channels and inlet / outlet channels, realizing continuous heat dissipation of the packing assembly and avoiding the sealing failure of the packing assembly due to excessive temperature. The spiral grooves on the inner wall of the rod channel can cooperate with the outer wall of the piston rod to form a labyrinth throttling effect when the piston rod reciprocates. At the same time, the pumping effect can push back a small amount of gas that may leak, further improving the reliability of the compressor.

[0015] Beneficial effects: In this invention, the packing assembly for a piston gas compressor employs a three-lobe adjustable sealing ring in conjunction with a retaining ring with a conical groove and a wave spring. The wave spring continuously applies axial thrust to the retaining ring, which is converted into radial pressure through the conical inner wall of the conical groove. This forces the three arc-shaped sealing lobes to tightly adhere to the outer wall of the piston rod, forming a reliable seal. When the adjustable sealing ring wears due to friction, the wave spring releases its preload, pushing the retaining ring to move axially, enhancing the squeezing effect on the arc-shaped sealing lobes, causing them to converge towards the center, automatically compensating for wear gaps. This maintains stable sealing performance without stopping the machine, significantly reducing the frequency of sealing ring replacement, lowering maintenance costs and downtime losses. In this invention, the packing assembly for a piston gas compressor has a heat dissipation mechanism that opens a circulating heat dissipation channel inside the packing assembly. External circulating fluid can enter the annular cooling channel of each seal and sealing end cover through the inlet / outlet liquid connector, inlet / outlet liquid channel, and connecting flow channel, and fully exchange heat with the packing assembly. The circulating fluid can quickly remove the heat generated by sealing friction and the heat transferred by high-pressure gas, effectively control the working temperature of the packing assembly, avoid carbonization and aging of the sealing ring due to high temperature, ensure long-term stable sealing performance, and further extend the overall service life of the packing assembly. In this invention, a packing assembly for a piston gas compressor has a clamp fixed in the packing groove by a clamping groove. The limiting protrusion on its inner wall is embedded in the guide limiting groove of the adjustable sealing ring and slides in cooperation with the relief groove of the abutting ring. This structure can effectively limit the circumferential rotation of the adjustable sealing ring during reciprocating movement and wear compensation, ensuring that the sealing petal is always in the correct working position, avoiding damage to the sealing surface due to misalignment of the sealing petal, and structurally ensuring the stability of the sealing effect. In this invention, the packing assembly for a piston gas compressor has a spiral groove on the inner wall of the rod channel that engages with the outer wall of the piston rod. This creates a labyrinthine throttling effect as the piston rod reciprocates, increasing the flow resistance of leaking gas. Simultaneously, the pumping effect pushes back any small amount of potentially leaking gas, further blocking the gas leakage path. Combined with the sealing rings on the first and second sides and the sealing gasket between the connectors, multiple layers of sealing protection are formed, significantly improving the overall sealing performance and ensuring the compressor's operating efficiency. In this invention, the packing assembly for a piston gas compressor includes a gland, a seal, and a sealing end cap, which are fixed by a combination of threaded holes and screws. The protrusion slides against the inner wall of the adjacent packing groove to achieve precise positioning, ensuring the assembly accuracy of each component. The sealing gasket is fitted onto the outer wall of the protrusion, and through holes are opened corresponding to the threaded holes and the connecting flow channels. This ensures the sealing performance between the connecting components, preventing gas or cooling fluid leakage, and also allows the packing assembly to maintain structural stability under compressor vibration and high-pressure conditions. The relative positions of each component do not shift, ensuring the continuous and effective performance of sealing and heat dissipation functions. In this invention, the packing assembly can automatically compensate for wear caused by the sealing ring. Through the cooperation of the three-lobed sealing ring structure, the conical abutment ring and the wave spring, the seal can be maintained without stopping the machine, reducing replacement costs and downtime losses. The circulating heat dissipation channel can quickly cool down and prevent seal failure. The clamp limiting structure can prevent the sealing ring from rotating and ensure the stability of the seal. The spiral groove and multiple sealing structure enhance the sealing effect. The components are precisely positioned and the seal is reliable. It can still operate stably under vibration and high pressure, which can comprehensively improve the performance and service life of the compressor. Attached Figure Description

[0016] Figure 1This is a three-dimensional structural schematic diagram of a packing assembly for a piston gas compressor proposed in this invention; Figure 2 This is a schematic diagram of the internal structure of a packing assembly for a piston gas compressor proposed in this invention; Figure 3 This is a schematic diagram of the disassembled packing assembly of a packing component for a piston gas compressor proposed in this invention; Figure 4 This is a cross-sectional view of the packing assembly of a packing component for a piston gas compressor proposed in this invention.

[0017] Figure 5 This is a schematic diagram showing the disassembled structure of the sealing mechanism of a packing assembly for a piston gas compressor according to the present invention; Figure 6 This is a partially enlarged cross-sectional view of the sealing mechanism of a packing assembly for a piston gas compressor proposed in this invention.

[0018] In the diagram: 1. Cylinder; 2. Packing assembly; 3. Piston head; 4. Piston rod; 5. Gland; 6. Seal; 7. Sealing end cap; 8. Rod body channel; 9. Packing groove; 10. Protrusion; 11. Sealing gasket; 12. Threaded hole; 13. Spiral groove; 14. Cooling channel; 15. Connecting channel; 16. Inlet / outlet channel; 17. Inlet / outlet connector; 18. Wave spring; 19. First side sealing ring; 20. Second side sealing ring; 21. Clamp; 22. Limiting protrusion; 23. Slot; 24. Adjustable sealing ring; 25. Guide limiting groove; 26. Abutment ring; 27. Relief groove; 28. Conical groove. Detailed Implementation

[0019] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0020] In one embodiment: Refer to Figure 1-6 A packing assembly, installed at one end of a compressor cylinder 1, whose core function is to provide a dynamic seal for the annular gap between the cylinder 1 and the piston rod 4 reciprocating therein, ensuring that the piston head 3 effectively compresses the gas within the cylinder 1, comprising: In this embodiment, the main body of the packing assembly is the packing group 2. The packing group 2 is composed of multiple independent connectors arranged sequentially along the axial direction and combined with external fasteners. These connectors include an outermost gland 5, multiple seals 6 arranged along the axial direction, and an innermost sealing end cap 7. The same side end face (facing the gland 5) of the seals 6 and the sealing end cap 7 are machined with circular packing grooves 9. The side end face of the gland 5 and the seals 6 facing the inside of the cylinder 1 is integrally formed with an annular protrusion 10. During assembly, the protrusion 10 of the corresponding connector is precisely inserted into the packing groove 9 of the adjacent connector to achieve radial positioning between adjacent components. After all the connectors are combined, their centers together form a through rod channel 8. The piston rod 4 passes through this channel, and its outer surface maintains a precise sliding fit with the inner wall of the rod channel 8, allowing the piston rod 4 to reciprocate stably.

[0021] Multiple threaded holes 12 are evenly distributed circumferentially on one side of each connector. The threaded holes 12 inside the seal 6 and the sealing end cap 7 are through-holes, while the threaded holes 12 inside the pressure cap 5 are only through-holes on one side of the pressure cap 5. The multiple threaded holes 12 cooperate with external bolts to lock and fix the pressure cap 5, multiple seals 6 and sealing end cap 7. In this embodiment, an annular sealing gasket 11 is also provided between the contact end faces of two adjacent connectors. The sealing gasket 11 is sleeved on the outer periphery of the protrusion 10 and is made of high-temperature resistant fluororubber. The sealing gasket 11 has through holes that align with the threaded holes 12. When the bolts are tightened, the sealing gasket 11 is compressed, filling the microscopic unevenness between the end faces of the connectors, achieving static sealing between the connectors and preventing gas leakage from these joints.

[0022] In this embodiment, an independent sealing mechanism is provided inside the packing groove 9 of each seal 6 and sealing end cap 7. The core of this sealing mechanism is an adjustable sealing ring 24 and an abutment ring 26. The adjustable sealing ring 24 adopts a three-part split design, that is, it is composed of three independent arc-shaped sealing petals spliced ​​in the circumferential direction. The inner working surface of these three sealing petals directly contacts the outer wall of the piston rod 4 and forms a sliding seal. The abutment ring 26 is located on the axial side of the adjustable sealing ring 24 (facing away from the cylinder pressure side). A conical groove 28 is machined on its end face facing the adjustable sealing ring 24. The conical angle of the conical groove 28 is between 15° and 30°, for example, it can be 18°, 22° or 28° (the specific angle can be set according to actual needs). One side of the arc-shaped edge of each of the three arc-shaped sealing petals is provided with a bevel. The three arc-shaped sealing petals abut against the conical inner wall of the conical groove 28 through the bevel.

[0023] In this embodiment, in order to apply a continuous axial thrust to the abutment ring 26, a wave spring 18 is installed in the packing groove 9 on the side of the abutment ring 26 away from the adjustable sealing ring 24. The wave spring 18 is in a pre-compressed state, with one side abutting against the end face of the protrusion 10 of the adjacent connector, and the other side abutting against a first side sealing ring 19. The first side sealing ring 19 is fixedly installed on the end face of the abutment ring 26 and forms a sealing sliding fit with the inner wall of the packing groove 9 together with the abutment ring 26. The pre-tightening of the wave spring 18... The force is transmitted to the abutment ring 26 through the first side sealing ring 19, pushing it axially against the adjustable sealing ring 24. Due to the fit between the tapered groove 28 and the inclined surface of the sealing flap, this axial thrust is converted into a radial force that forces the three sealing flaps to converge toward the center (i.e., the piston rod axis), thereby making the inner working surface of the sealing flap tightly fit against the piston rod 4. On the other side of the adjustable sealing ring 24 (facing the cylinder pressure side), a second side sealing ring 20 is also provided, which also seals with the inner wall of the packing groove 9, mainly playing the role of auxiliary sealing and filling abutment.

[0024] In this embodiment, a wave spring 18 is used instead of a regular helical spring to provide preload force, based on engineering considerations of actual assembly space and force stability. The axial space of the packing groove 9 is limited, and the wave spring 18 requires a smaller axial installation height to provide the same elastic force. If the wave spring 18 is not provided and the sealing mechanism is fixed solely by the bolt preload force during installation, the tiny gaps caused by wear of the internal parts of the mechanism cannot be automatically compensated after long-term operation, and the sealing force will rapidly decrease.

[0025] In this embodiment, the packing assembly 2 also integrates a heat dissipation mechanism. The core of this heat dissipation mechanism is a circulating heat dissipation channel machined inside the bodies of multiple seals 6 and sealing end caps 7. Specifically, at least one annular cooling channel 14 is machined around the rod channel 8 inside each seal 6 and sealing end cap 7. Two connecting channels 15 are also machined in each connector. These two connecting channels 15 are located on both sides of the rod channel 8 and are connected to the annular cooling channels 14. For the seal 6, its two connecting channels 15 are straight holes penetrating its two end faces. For the sealing end cap 7... Cover 7 has two blind holes 15 connecting channels 15 that lead to only one end. When multiple connectors are stacked, the multiple connecting channels 15 on the same straight line are connected to each other to form two independent axial channels. Two liquid inlet and outlet channels 16 are machined inside the outermost cover 5. These two liquid inlet and outlet channels 16 are respectively connected to the two connecting channels 15 of the adjacent first seal 6. Two liquid inlet and outlet connectors 17 are fixedly installed on the outer side of the cover 5 and are respectively connected to the two liquid inlet and outlet channels 16. The pipeline of the external coolant circulation system can be connected to these two liquid inlet and outlet connectors 17.

[0026] In this embodiment, the cooling channel 14 adopts an annular rather than a straight design because the seal 6 is a rotating part. The annular channel has better manufacturability and allows the coolant to flow more evenly around the heat-generating area. If no active cooling channel is provided and the heat dissipation relies solely on the natural heat dissipation of the metal casing, the temperature inside the packing assembly 2, especially the seal 6 near the cylinder side, may exceed 150°C during continuous high-load operation of the compressor. This would accelerate the aging process of the sealing ring material.

[0027] This application can be used in the field of compressor technology, or in other fields applicable to this application.

[0028] In another embodiment: Reference Figure 3 , 5 A packing assembly for a piston gas compressor, which is applied in the field of compressor technology; the structure of this embodiment is basically the same as that of the aforementioned embodiments, the difference being: In this embodiment, to prevent the three sealing petals of the adjustable sealing ring 24 from rotating circumferentially or misaligning under the reciprocating motion of the piston rod 4, an annular groove 23 is provided at the bottom of the packing groove 9, and a clamp 21 is engaged in the groove 23. Three radially inward limiting protrusions 22 are uniformly fixed on the inner circumferential surface of the clamp 21. Correspondingly, an axially extending guide limiting groove 25 is provided on the outer circumferential surface of each of the three sealing petals of the adjustable sealing ring 24, and three axial clearance grooves 27 are correspondingly provided on the circumferential surface of the abutting ring 26. During assembly, the three limiting protrusions 22 are simultaneously embedded in the guide limiting grooves 25 of the corresponding sealing petals and the clearance grooves 27 of the abutting ring 26. In this way, no matter how the sealing petals of the adjustable sealing ring 24 move during radial compensation, their circumferential position is constrained by the limiting protrusions 22, avoiding uneven wear of the sealing surface or sealing failure caused by rotation.

[0029] As an alternative, the inner wall of the rod channel 8 can also be machined with a shallow spiral groove 13. When the piston rod 4 reciprocates, a tiny labyrinthine throttling gap is formed between the spiral groove 13 and the outer surface of the piston rod 4, which generates a certain pumping and reverse thrust effect on the trace amount of gas that may leak along the gap, which helps to further reduce the leakage rate. This solution is more advantageous in situations where the gas leakage control requirements are extremely strict, but its processing cost is relatively higher, and the requirements for the surface quality and straightness of the piston rod are also more stringent.

[0030] The working principle and usage process of this technical solution are as follows: During use, the packing assembly 2 is slidably inserted into one end of the cylinder 1, ensuring that the piston rod 4 passes through the rod channel 8 and the piston rod 4 maintains a sliding fit with the inner wall of the channel. Then, the pressure cap 5 is fixed to the cylinder 1 with bolts to complete the overall installation of the packing assembly 2. Inside the packing assembly 2, the wave spring 18 is in a pre-compressed state, which can continuously apply axial thrust to the abutment ring 26. The abutment ring 26 generates radial pressure on the three arc-shaped sealing petals of the adjustable sealing ring 24 through the conical inner wall of the conical groove 28, thereby making the three sealing petals tightly fit against the outer wall of the piston rod 4. With the cooperation of the first side sealing ring 19 and the second side sealing ring 20, the gap between the compressor cylinder 1 and the corresponding piston rod 4 can be sealed. As the running time increases, multiple sealing rings are prone to wear due to continuous friction, and the gap between them and the piston rod 4 will gradually increase. During this process, the wave spring 18 will gradually release the preload, thereby pushing the abutment ring 26 to move axially towards the adjustable sealing ring 24. The conical inner wall of the conical groove 28 will increase the squeezing effect on the three arc-shaped sealing petals, forcing the three sealing petals to converge towards the center. This can automatically compensate for the gap caused by wear, enabling them to maintain a tight fit with the outer wall of the piston rod 4 and maintain a stable sealing effect. The clamp 21 is fixed in the packing groove 9 through the clamp groove 23. The limiting protrusion 22 on its inner wall is embedded in the guide limiting groove 25 of the sealing petal of the adjustable sealing ring 24, and simultaneously slides with the relief groove 27 of the abutting clamp ring 26. During the reciprocating movement of the adjustable sealing ring 24 with the piston rod 4 and the wear compensation and convergence process, the multiple limiting protrusions 22 can limit the rotation of the adjustable sealing ring 24, thereby ensuring that its sealing petal is always in the correct working position and avoiding sealing failure due to rotation. During operation, the friction between multiple sealing rings and piston rod 4 generates heat, and the compression of high-pressure gas also transfers some heat to the packing assembly 2. At this time, the external circulating fluid can be connected through the pipe and the inlet / outlet connector 17, enter the connecting flow channel 15 of the adjacent seal 6 through the inlet / outlet channel 16 in the gland 5, and then flow into the annular cooling flow channel 14 in each seal 6 and the sealing end cap 7 through the connected flow channel 15. When the circulating fluid flows in the cooling flow channel 14, it can fully absorb the heat generated by the packing assembly 2, and then flow out from the corresponding inlet / outlet connector 17 along another set of connecting flow channels 15 and inlet / outlet channels 16, so as to realize the continuous heat dissipation of the packing assembly 2 and avoid the sealing failure of the packing assembly 2 due to excessive temperature. The spiral groove 13 on the inner wall of the rod channel 8 can cooperate with the outer wall of the piston rod 4 to form a labyrinth throttling effect when the piston rod 4 reciprocates. At the same time, it can push back a small amount of gas that may leak by means of the pumping effect, further improving the working reliability of the compressor.

[0031] The packing assembly can be maintained periodically according to the existing compressor maintenance specifications. The maintenance includes: checking the elasticity of the wave spring 18 and replacing it in time if fatigue deformation occurs; cleaning the impurities deposited in the circulating heat dissipation channel to ensure smooth fluid flow; adding supplementary lubricating oil to the inner wall of the rod channel 8 and the mating surface of the adjustable sealing ring 24 and the piston rod 4 to reduce friction and wear; and checking the wear of multiple sealing components and replacing them in time if aging or damage occurs.

[0032] The accompanying drawings in this application are for illustrative purposes only. The dimensions and shapes of the components shown are not actual limitations but are merely schematic representations. In actual implementation, the components can be reasonably configured and adjusted according to specific needs and actual conditions.

[0033] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A packing assembly for a piston gas compressor, installed at one end of a compressor cylinder (1) for sealing the gap between the cylinder (1) and the piston rod (4), characterized in that, include: The packing assembly (2) is assembled by connecting multiple connectors in sequence, and each connector has a rod channel (8) through which the piston rod (4) passes. Multiple sealing mechanisms are respectively set in the corresponding connecting parts. The sealing mechanism includes an adjustable sealing ring (24) and an abutment ring (26). The adjustable sealing ring (24) is composed of three arc-shaped sealing petals and is sleeved on the piston rod (4). A conical groove (28) is opened on one side of the abutment ring (26). The conical inner wall of the conical groove (28) abuts against the inclined surface of one side of the three arc-shaped sealing petals of the adjustable sealing ring (24). A wave spring (18) is disposed on the side of the abutment ring (26) facing away from the adjustable sealing ring (24) to provide axial thrust to the abutment ring (26), which is converted into radial pressure through the tapered groove (28), causing the three arc-shaped sealing flaps to converge toward the piston rod (4) to form a dynamic seal and automatically compensate for wear.

2. The packing assembly for a piston gas compressor according to claim 1, characterized in that, The plurality of connecting parts include a gland (5), a plurality of seals (6) and a sealing end cap (7) arranged in sequence, which are connected and combined to form a packing group (2). The gland (5) and the seals (6) are provided with protrusions (10) on the side facing the cylinder (1). The seals (6) and the sealing end cap (7) are provided with a packing groove (9) that slides with the protrusions (10) on the same side. The packing groove (9) is used to accommodate the sealing mechanism.

3. The packing assembly for a piston gas compressor according to claim 2, characterized in that, The abutment ring (26) is fixed with a first side sealing ring (19) on the side near the wave spring (18). One end of the wave spring (18) abuts against the adjacent protrusion (10), and the other end abuts against the first side sealing ring (19). The adjustable sealing ring (24) is provided with a second side sealing ring (20) on the side away from the abutment ring (26). Both the first side sealing ring (19) and the second side sealing ring (20) are in a sealing sliding fit with the inner wall of the packing groove (9).

4. A packing assembly for a piston gas compressor according to claim 3, characterized in that, The filling groove (9) is provided with a slot (23), and a clamp (21) is engaged in the slot (23). Three limiting protrusions (22) are fixedly installed on the inner wall of the clamp (21). The outer walls of the three sealing petals of the adjustable sealing ring (24) are provided with guide limiting grooves (25). Three corresponding relief grooves (27) are provided on one side of the abutting ring (26). The guide limiting grooves (25) and the three relief grooves (27) are all slidably engaged with the corresponding limiting protrusions (22), which are used to provide corresponding restrictions on the adjustable sealing ring (24) to prevent it from rotating.

5. A packing assembly for a piston gas compressor according to any one of claims 2-4, characterized in that, It also includes a heat dissipation mechanism, which includes an annular cooling channel (14) formed inside the plurality of seals (6) and the sealing end cap (7). The cooling channel (14) is annular, and at least one cooling channel (14) is formed inside each seal (6) and sealing end cap (7). Two connecting channels (15) are formed inside each of the plurality of seals (6) and the corresponding sealing end cap (7). The two connecting channels (15) are connected to the corresponding cooling channels (14). The connecting channel (15) located inside the seal (6) passes through both ends of the seal (6) and is located inside the sealing end cap (7). The connecting flow channel (15) inside the sealing end cap (7) passes through one end of the sealing end cap (7), and multiple connecting flow channels (15) on the same straight line are connected to ensure the flow of liquid; the inside of the pressure cap (5) is provided with two inlet and outlet liquid channels (16), and the two inlet and outlet liquid channels (16) are connected to the two connecting flow channels (15) of the adjacent sealing element (6), and two inlet and outlet liquid connectors (17) are fixedly installed on one side of the pressure cap (5), and the two inlet and outlet liquid connectors (17) are corresponding to the corresponding inlet and outlet liquid channels (16), which are used to connect with external inlet and outlet liquid pipes to complete the inlet and outlet of circulating fluid.

6. A packing assembly for a piston gas compressor according to claim 5, characterized in that, A sealing gasket (11) is provided between two adjacent connectors, and the sealing gasket (11) is fitted around the outer periphery of the protrusion (10).

7. A packing assembly for a piston gas compressor according to claim 1, characterized in that, The inner wall of the rod channel (8) is provided with a spiral groove (13), which cooperates with the outer wall of the piston rod (4) to form a labyrinth throttling effect and generate a pumping reverse thrust effect on the leaked gas when the piston rod (4) reciprocates.

8. A packing assembly for a piston gas compressor according to claim 2, characterized in that, The gland (5), the plurality of seals (6) and the sealing end cap (7) are fixedly connected to bolts through threaded holes (12).

9. A packing assembly for a piston gas compressor according to claim 2, characterized in that, The pressure cap (5) is located outside the cylinder (1) and is fixedly connected to the cylinder (1) by bolts.

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