Shaft seal arrangement structure applied to high pressure
By adding carbon rings and dynamic sealing components to the high-pressure screw compressor, the problems of gas leakage and external contamination of single-end shaft seals are solved, achieving low-cost and high-efficiency sealing, extending the service life of the shaft seal and simplifying the structure.
Patent Information
- Application Number
- CN202520136892.1
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-01-21
- Publication Date
- 2025-12-19
- Estimated Expiration
- 2035-01-21
AI Technical Summary
Existing single-end shaft seals in high-pressure screw compressors suffer from excessive gas leakage and intrusion of external contaminants, while double-end shaft seals are costly, difficult to install, and have a complex structure.
A carbon ring seal is added between the intake end cover and the male rotor, and a dynamic sealing assembly is provided, including a dynamic ring, a stationary ring and a metal bellows. The high-pressure gas leaking from the sealing pair flows back into the container through the leak port through the carbon ring assisted sealing. The dynamic ring and the stationary ring are tightly sealed by the elastic force of the metal bellows.
It effectively reduces gas leakage, prevents external contaminants from entering, extends the service life of the shaft seal, reduces costs and simplifies the structure, avoids bellows fatigue failure, and improves sealing performance.
Smart Images
Figure CN223689939U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model relates to a kind of shaft seal arrangement structure applied to high pressure, it is related to open type high pressure screw compressor field. BACKGROUND
[0002] Open type screw compressor is realized by a pair of intermeshing female and male rotors rotation to gas compression.Electric motor as the power source of compressor, through shaft coupling and male rotor shaft extension end are connected, drive male rotor rotation.High pressure screw compressor does not allow internal gas mass leakage, while equipment application environment has the characteristics of strong corrosion, high temperature and high humidity.Therefore, it is important to install suitable shaft seal on male rotor shaft extension end for the normal operation and prolong service life of compressor.
[0003] Single end face shaft seal is the most widely used shaft seal mode in open type screw compressor, and the sealing pair formed by the friction of a pair of dynamic and static ring end faces, and the compensation function of corrugated pipe is cooperated to ensure that the sealing end face is well fitted, and then the compressor gas is blocked inside the body.However, the current single end face shaft seal only relies on a pair of friction pair sealing and cooperates wool felt auxiliary sealing, in the open type screw compressor application of high pressure working medium, there are problems of too large gas leakage and external pollutants intrusion.Double end face shaft seal can effectively prevent gas leakage, but there are problems of high use and maintenance cost, large installation difficulty and complex structure. SUMMARY
[0004] In view of the deficiencies of the prior art, the technical problem to be solved by the utility model is to provide a kind of shaft seal arrangement structure applied to high pressure, solve the problem of poor high pressure working condition applicability and limited external pollution sealing in the existing single end face shaft seal arrangement scheme.
[0005] To solve the above technical problems, the technical scheme of the utility model is: a kind of shaft seal arrangement structure applied to high pressure, including gas inlet end cover, the male rotor is installed on the gas inlet end cover, the leakage port is provided on the gas inlet end cover, the gas inlet end cover is sealed between the male rotor on the one side of leakage port by carbon ring, and dynamic sealing assembly is arranged between the gas inlet end cover and the male rotor on the other side of leakage port, to facilitate gas sealing.
[0006] Preferably, wave spring is arranged between the inner side of carbon ring and the end of gas inlet end cover, and shaft end baffle ring is arranged between the outer side of carbon ring and the end of gas inlet end cover.
[0007] Preferably, the dynamic sealing assembly comprises a dynamic ring, a static ring and a metal bellows arranged axially in sequence towards the leakage port direction, the dynamic ring is fixedly connected on the male rotor for synchronous rotation with the male rotor, one end of the metal bellows is fixedly connected on the gas inlet end cover, the other end is integrated with the static ring, and the end face between the static ring and the dynamic ring is tightly attached under the elastic force of the metal bellows.
[0008] Preferably, the metal bellows and the gas inlet end cover are connected and fastened through a set screw.
[0009] Preferably, an O-shaped sealing ring is arranged on the joint seam between the metal bellows and the gas inlet end cover.
[0010] Preferably, the metal bellows and the static ring are integrally provided.
[0011] Preferably, a guide sleeve is arranged between the dynamic ring and the male rotor.
[0012] Preferably, the dynamic ring and the guide sleeve are connected and fastened through a set screw, and an O-shaped sealing ring is arranged on the joint seam between the dynamic ring and the guide sleeve.
[0013] Preferably, the guide sleeve and the male rotor are connected and fastened through a set screw.
[0014] Preferably, an O-shaped sealing ring is arranged on the joint seam between the guide sleeve and the male rotor.
[0015] Compared with the prior art, the utility model has the following beneficial effects:
[0016] The carbon ring is arranged between the gas inlet end cover and the male rotor to realize auxiliary sealing, the problems of easy erosion of the felt seal by gas and liquid and poor high-temperature and high-pressure protection effect are overcome, the gas-liquid-solid three-phase pollutants are effectively blocked outside the compressor body, the erosion of the external pollutants on the shaft seal is reduced, and the service life of the shaft seal is prolonged. In addition, the high-pressure gas leaked from the sealing pair is blocked by the carbon ring and flows back to the container through the leakage port, effectively solving the problem of excessive gas leakage caused by only one pair of sealing pair when the single-end face shaft seal is applied to the high-pressure gas seal. Compared with the expensive double-end face shaft seal, the carbon ring auxiliary seal has the advantages of low cost, compact structure and simple layout in the case of allowing a small amount of leakage of the compressor gas.
[0017] The utility model will be explained in further detail in connection with the drawings and specific embodiments. BRIEF DESCRIPTION OF DRAWINGS
[0018] Figure 1 The utility model embodiment is a structure schematic view.
[0019] In the diagram: 1. Inlet end cover; 2. Male rotor; 3. Leakage port; 4. Carbon ring; 5. Wave spring; 6. Shaft end retaining ring; 7. Dynamic ring; 8. Static ring; 9. Metal bellows; 10. Set screw; 11. O-ring seal; 12. Guide sleeve. Detailed Implementation
[0020] The present invention will be further described below with reference to the accompanying drawings and embodiments.
[0021] It should be noted that the following detailed descriptions are exemplary and intended to provide further explanation of this application. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.
[0022] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.
[0023] like Figure 1 As shown, this embodiment provides a shaft seal arrangement structure for high pressure, including an air inlet end cover 1, a male rotor 2 mounted on the air inlet end cover, a leakage port 3 provided on the air inlet end cover, a carbon ring 4 sealing the air inlet end cover and the male rotor on one side of the leakage port, and a sealing pair of a dynamic sealing assembly provided between the air inlet end cover and the male rotor on the other side of the leakage port to facilitate gas sealing.
[0024] Adding a carbon ring between the intake end cover and the male rotor for auxiliary sealing prevents high-pressure gas leaking from the sealing pair from entering the shaft seal and exiting it into the container through the leak, thus achieving sealing and protection within a limited space.
[0025] In this embodiment of the present invention, a wave spring 5 is provided between the inner side of the carbon ring and the end of the air intake end cover, and a shaft end retaining ring 6 is provided between the outer side of the carbon ring and the end of the air intake end cover. The shaft end retaining ring is an elastic retaining ring.
[0026] The carbon ring is fixed between the intake end cover and the male rotor by a wave spring and a shaft end retaining ring. When the compressor is working, a gas film is formed between the carbon ring and the male rotor to prevent high-pressure gas leakage and external impurities from entering the shaft seal.
[0027] In the embodiment of the utility model, the dynamic sealing assembly comprises dynamic ring 7, static ring 8 and metal bellows 9 which are sequentially and axially arranged towards the leakage port, the dynamic ring is fixedly connected to the male rotor and rotates synchronously with the male rotor, one end of the metal bellows is fixedly connected to the air inlet end cover, the other end is integrated with the static ring, and the end faces between the static ring and the dynamic ring are tightly attached under the elastic force of the metal bellows, and the tightly attached end faces of the static ring and the dynamic ring are smooth and flat.
[0028] In the embodiment of the utility model, the metal bellows and the air inlet end cover are connected and fastened through the set screw 10.
[0029] In the embodiment of the utility model, the O-shaped sealing ring 11 is arranged on the joint seam between the metal bellows and the air inlet end cover, and the auxiliary static sealing effect is achieved.
[0030] In the embodiment of the utility model, the metal bellows and the static ring are integrally arranged.
[0031] The metal bellows is arranged on one side of the static ring for centralized installation, which not only reduces the requirement for the worker's proficiency in shaft seal installation, but also greatly improves the fatigue life and installation precision of the bellows.
[0032] In the embodiment of the utility model, the guide sleeve 12 is arranged between the dynamic ring and the male rotor.
[0033] In the embodiment of the utility model, the dynamic ring and the guide sleeve are connected and fastened through the set screw, and the O-shaped sealing ring is arranged on the joint seam between the dynamic ring and the guide sleeve, and the auxiliary static sealing effect is achieved.
[0034] In the embodiment of the utility model, the guide sleeve and the male rotor are connected and fastened through the set screw.
[0035] In the embodiment of the utility model, the O-shaped sealing ring is arranged on the joint seam between the guide sleeve and the male rotor, and the auxiliary static sealing effect is achieved.
[0036] The static ring and the metal bellows are designed as an integrated type, are installed on the air inlet end cover of the compressor shell through the set screw, the static ring is tightly attached to the end face of the dynamic ring by the elastic force of the metal bellows, and the initial sealing closing force is generated. The dynamic ring is installed on the guide sleeve through the set screw, the guide sleeve is installed on the male rotor through the set screw to follow the movement. When the male rotor rotates, the guide sleeve drives the dynamic ring to rotate, the end face of the dynamic ring rubs against the end face of the static ring to generate the closing force, and the gas sealing is realized.
[0037] In the embodiment of the utility model, the shaft seal principle of the shaft seal arrangement structure applied to high pressure is as follows:
[0038] 1. The carbon ring is added between the gas inlet end cover and the male rotor to assist in sealing, the high-pressure gas leaked from the sealing pair is blocked in the shaft seal and discharged from the leakage port, and the sealing and protection effects can be achieved in the limited space.
[0039] 2. When the male rotor rotates, the guide sleeve drives the dynamic ring to rotate, the end face of the dynamic ring is frictional with the end face of the static ring to generate a closing force, and the gas sealing is realized.
[0040] The following can be realized:
[0041] 1. The carbon ring is added between the gas inlet end cover and the male rotor to assist in sealing, the problems that the felt sealing is easy to be eroded by gas and liquid and the high-temperature and high-pressure protection effect is poor are overcome, the gas-liquid-solid three-phase pollutants are effectively blocked outside the compressor body, the erosion of the external pollutants on the shaft seal is reduced, and the service life of the shaft seal is prolonged. In addition, the high-pressure gas leaked from the sealing pair is blocked by the carbon ring and flows back to the container through the leakage port, and the problem that the gas leakage amount is too large due to only one pair of sealing pair when the single-end-face shaft seal is applied to the high-pressure gas sealing is effectively solved. Compared with the expensive double-end-face shaft seal, the carbon ring auxiliary sealing has the advantages of low cost, compact structure and simple layout in the case of allowing a small amount of leakage of the compressor gas.
[0042] 2. In the prior art, the bellows bears large periodic alternating load and friction with the dynamic ring during high-speed rotation under high-pressure working conditions, the elasticity of the bellows is gradually weakened, and fatigue failure is prone to occur. The metal bellows of the utility model is installed on the static ring side, the problem that the periodic alternating load and impact borne by the bellows and the dynamic ring are too large under high-pressure gas working conditions is effectively avoided, the risk of fatigue failure of the metal bellows is reduced, and the service life of the shaft seal is greatly improved. In addition, the metal bellows and the static ring are processed into an integrated whole before leaving the factory, the on-site installation is convenient, the sealing surface matching error caused by human operation is reduced, and the sealing effect of the shaft seal is ensured.
[0043] The above is only a preferred embodiment of the utility model, and does not limit other forms of the utility model, and any person skilled in the art can change or modify the above disclosed technical content into equivalent embodiments with equivalent changes. However, any simple modification, equivalent change and modification made on the above embodiments according to the technical essence of the utility model without departing from the technical scheme content of the utility model still belongs to the protection scope of the technical scheme of the utility model.
Claims
1. A seal arrangement for high pressure applications comprising an inlet end cover having a male rotor mounted thereon, characterised in that: The air inlet end cover is provided with a leakage port, the air inlet end cover on one side of the leakage port is sealed with the male rotor via a carbon ring, and the air inlet end cover on the other side of the leakage port is provided with a dynamic sealing assembly to facilitate gas sealing.
2. A seal arrangement for high pressures according to claim 1, characterized in that: A wave spring is arranged between the inner side of the carbon ring and the end of the air inlet end cover, and an axle end retainer ring is arranged between the outer side of the carbon ring and the end of the air inlet end cover.
3. A seal arrangement for high pressures according to claim 1, characterized in that: The dynamic sealing assembly comprises, in sequence from the direction of the leakage port, a dynamic ring, a static ring and a metal bellows, the dynamic ring is fixedly connected to the male rotor to rotate synchronously with the male rotor, one end of the metal bellows is fixedly connected to the air inlet end cover, the other end is integrated with the static ring, and the end faces of the static ring and the dynamic ring are tightly attached under the elastic force of the metal bellows.
4. A seal arrangement for high pressures according to claim 3, characterised in that: The metal bellows and the air inlet end cover are connected and fastened via a clamping screw.
5. A seal arrangement for high pressures according to claim 3, characterised in that: An O-shaped sealing ring is arranged on the joint seam between the metal bellows and the air inlet end cover.
6. A seal arrangement for high pressures according to claim 3, characterised in that: The metal bellows and the static ring are integrated.
7. A seal arrangement for high pressures according to claim 3, characterised in that: A guide sleeve is arranged between the dynamic ring and the male rotor.
8. A seal arrangement for high pressures according to claim 7, characterised in that: The dynamic ring and the guide sleeve are connected and fastened via a clamping screw, and an O-shaped sealing ring is arranged on the joint seam between the dynamic ring and the guide sleeve.
9. A seal arrangement for high pressure according to claim 7, characterized in that: The guide sleeve and the male rotor are connected and fastened via a clamping screw.
10. A seal arrangement for high pressure as claimed in claim 7, characterized in that: An O-shaped sealing ring is arranged on the joint seam between the guide sleeve and the male rotor.