Screw rotor for screw compressor and screw compressor

Abstract

The invention relates to the technical field of compressors, in particular to a screw rotor for a screw compressor and the screw compressor. The screw rotor comprises a rotating shaft, a plurality of rotor teeth and a first sealing piece, the rotor teeth are spirally arranged outside the rotating shaft, a tooth groove is formed between every two adjacent rotor teeth, and an exhaust end face is formed at one axial end of each rotor tooth; the first sealing element is convexly arranged on the exhaust end face, one end of the first sealing element extends to the tooth top of the rotor tooth, and the other end extends to the rotating shaft. The problem that gas leaks in a gap of an exhaust end face in a conventional screw compressor is solved, the volume efficiency is guaranteed, and the heat insulation efficiency and energy efficiency of working of the compressor are improved. In addition, due to the fact that the first sealing piece is made of graphite, friction of the first sealing piece on the friction contact face is obviously reduced, the abrasion degree is reduced, the sealing failure risk caused by friction heat accumulation is reduced, the reliability of the compressor cannot be affected, and efficient operation of the compressor is guaranteed.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and in particular to a screw rotor for a screw compressor and a screw compressor. Background Art

[0002] With the rapid development of science and technology and society, there are more and more large buildings, and the market share of commercial air conditioners is increasing year by year. The screw compressor is the core component of the air conditioner and is known as the heart of the air conditioner. In principle, it is a positive displacement compressor. Its core is a pile of intermeshing rotors. The inter-tooth volume is formed by the intermeshing between the tooth-shaped convex male rotor and the tooth-shaped concave female rotor. During the rotation process, the inter-tooth volume increases first and then decreases, realizing the inhalation, compression and discharge of gas.

[0003] During the operation of the compressor, there must be a gap between the moving parts (made of carbon steel, iron and other metals) to ensure the reliability of the compressor; the existence of the gap causes gas leakage during the operation of the rotor, thereby affecting the volumetric efficiency, reducing the insulation efficiency, and causing energy efficiency loss. Summary of the invention

[0004] In order to solve the above technical problems, the present application provides a screw rotor for a screw compressor and a screw compressor.

[0005] In a first aspect, an embodiment of the present application provides a screw rotor for a screw compressor, the screw rotor comprising:

[0006] Rotating shaft;

[0007] A plurality of rotor teeth are provided and are spirally arranged outside the rotating shaft, tooth grooves are formed between adjacent rotor teeth, and one axial end of the rotor teeth forms an exhaust end surface;

[0008] The first sealing member is protrudingly arranged on the exhaust end surface, wherein one end of the first sealing member extends to the tooth top of the rotor tooth, and the other end extends to the rotating shaft.

[0009] Furthermore, a plurality of the first sealing members are provided and are arranged in one-to-one correspondence with the rotor teeth.

[0010] Furthermore, a first fixing groove is formed on the exhaust end surface, and the first sealing member is fixed in the first fixing groove.

[0011] Furthermore, a second fixing groove is provided at the connection between the rotating shaft and the rotor teeth, the second fixing groove is communicated with the first fixing groove, and the first sealing member is fixed in both the first fixing groove and the second fixing groove.

[0012] Furthermore, it also includes a second sealing member, which is protrudingly arranged on the tooth top of the rotor tooth and is spirally arranged along the direction of the rotor tooth.

[0013] Furthermore, one end of the second sealing member is connected to the first sealing member.

[0014] Furthermore, the rotor teeth are divided into a high-pressure section close to the exhaust end surface and a low-pressure section away from the exhaust end surface along the axial direction of the rotating shaft, and the second sealing member is arranged at the high-pressure section of the rotor teeth.

[0015] Furthermore, along the axial direction of the rotating shaft, as gradually moving away from the exhaust end surface, the height of the first sealing member protruding from the tooth top gradually decreases.

[0016] Furthermore, a third fixing groove is formed on the tooth top of the rotor tooth, and the second sealing member is fixed in the third fixing groove.

[0017] Furthermore, the first sealing member and / or the second sealing member is graphite.

[0018] In a second aspect, an embodiment of the present application provides a screw compressor, the screw compressor comprising:

[0019] case;

[0020] The exhaust end bearing seat and the suction end bearing seat are respectively arranged at two ends of the shell in the axial direction, the shell, the exhaust end bearing seat and the suction end bearing seat together form a working chamber, and the exhaust end bearing seat forms an exhaust end mating surface on one side facing the working chamber; and

[0021] The screw rotor provided in the first aspect of the present application has two ends of the rotating shaft respectively passing through the exhaust end bearing seat and the intake end bearing seat, the rotor teeth are located in the working chamber, a first gap is formed between the exhaust end face and the exhaust end mating face, and the first seal is filled in the first gap.

[0022] Furthermore, the screw rotor also includes a second seal, which is protruding from the tooth top of the rotor tooth and is spirally arranged along the direction of the rotor tooth; a second gap is formed between the tooth top of the rotor tooth and the inner wall of the shell, and the second seal is filled in the second gap.

[0023] When the screw compressor using the screw rotor provided by the present application is working, the first seal will fill the gap between the exhaust end face and the fixed structure (such as the exhaust end bearing seat), and the first seal made of graphite will be in close contact with the exhaust end bearing seat at all times, forming a strict seal at the exhaust end face of the screw rotor. The problem of gas leakage in the gap at the exhaust end face in conventional screw compressors is solved, the volumetric efficiency is guaranteed, and the insulation efficiency and energy efficiency of the compressor are improved; in addition, since the material of the first seal is graphite, it has excellent chemical stability, high temperature resistance and lubricity. Through the lubrication of graphite, the friction of the first seal on the friction contact surface is significantly reduced, which not only reduces the degree of wear, but also reduces the risk of seal failure caused by friction heat accumulation, does not affect the reliability of the compressor, and ensures the efficient operation of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The drawings constituting a part of this application are used to provide a further understanding of this application, so that other features, purposes and advantages of this application become more obvious. The schematic embodiment drawings and their descriptions of this application are used to explain this application and do not constitute an improper limitation on this application. In the drawings:

[0025] Figure 1 A three-dimensional structure diagram of a male rotor and a female rotor meshing and connecting in the related art is schematically given;

[0026] Figure 2 A partial three-dimensional structural diagram of a screw rotor provided in an embodiment of the present application is schematically provided;

[0027] Figure 3 A three-dimensional structural diagram of a screw rotor provided in an embodiment of the present application is schematically provided;

[0028] Figure 4 for Figure 3 A partial enlarged view of part A;

[0029] Figure 5 A three-dimensional structural diagram of a screw rotor provided in an embodiment of the present application is schematically provided;

[0030] Figure 6 A three-dimensional structural diagram of a screw rotor provided in an embodiment of the present application is schematically provided;

[0031] Figure 7 It is schematically given Figure 6 An axial orthographic view of the screw rotor shown;

[0032] Figure 8 A three-dimensional structural diagram of a screw rotor provided in an embodiment of the present application is schematically provided;

[0033] Fig. 9A cross-sectional view perpendicular to the axis of the screw compressor provided in an embodiment of the present application is schematically shown;

[0034] Fig.10 for Fig. 9 A partial enlarged view of part B;

[0035] Fig.11 A portion of a cross-sectional view parallel to the axis of a screw compressor provided in an embodiment of the present application is schematically shown;

[0036] Fig.12 for Fig.11 A partial enlarged view of part C.

[0037] In the figure:

[0038] 100, screw rotor; 100-1, male rotor; 100-2, female rotor;

[0039] 101, shaft;

[0040] 102, rotor teeth;

[0041] 103, tooth groove;

[0042] 104, exhaust end face;

[0043] 105. a first sealing member;

[0044] 106. a first fixing groove;

[0045] 107, second fixing groove;

[0046] 108. Second sealing member;

[0047] 109. High-voltage section;

[0048] 110, low pressure section;

[0049] 111, third fixing groove;

[0050] 200, housing;

[0051] 300, exhaust end bearing seat;

[0052] 301, exhaust end mating surface;

[0053] 400, suction end bearing seat;

[0054] 500, working chamber;

[0055] 501, first gap;

[0056] 502. The second gap. DETAILED DESCRIPTION

[0057] In order to enable those skilled in the art to better understand the solution of the present application, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work should fall within the scope of protection of the present application.

[0058] It should be noted that the terms "including" and "having" and any variations thereof in the specification and claims of the present application and the above-mentioned drawings are intended to cover non-exclusive inclusions. For example, a system, product or device comprising a series of units is not necessarily limited to those units explicitly listed, but may include units that are not explicitly listed or inherent to these products or devices.

[0059] In this application, the directions or positional relationships indicated by the terms "upper", "lower", "inner", "middle", "outer", etc. are based on the directions or positional relationships shown in the drawings. These terms are mainly used to better describe the present application and its embodiments, and are not used to limit the indicated devices, elements or components to have a specific direction, or to be constructed and operated in a specific direction.

[0060] In addition, some of the above terms may be used to express other meanings in addition to indicating orientation or positional relationship. For example, the term "on" may also be used to express a certain dependency or connection relationship in some cases. For those of ordinary skill in the art, the specific meanings of these terms in this application can be understood according to specific circumstances.

[0061] In addition, the terms "disposed", "connected", and "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0062] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application may be combined with each other.

[0063] like Figure 1As shown, a basic structural diagram of a screw rotor 100 for a screw compressor is given. Here, the patent of a twin-screw compressor is used as an example for explanation, but the screw rotor 100 provided in this application can also be applied to other screw compressors. The twin-screw compressor includes a pair of mutually meshing male rotors 100-1 and female rotors 100-2. The tooth shape of the male rotor 100-1 is convex, and the tooth shape of the female rotor 100-2 is concave. The two mesh with each other to form an inter-tooth volume. During the rotation process, the inter-tooth volume undergoes a process of first increasing and then decreasing, thereby realizing the suction, compression and discharge of gas. Taking the screw rotor 100 as the male rotor 100-1 as an example, the screw rotor 100 includes a rotating shaft 101 and rotor teeth 102, wherein a plurality of rotor teeth 102 are arranged, and the plurality of rotor teeth 102 are spirally arranged outside the rotating shaft 101, and tooth grooves 103 are formed between adjacent rotor teeth 102, and one axial end of the rotor teeth 102 forms an exhaust end face 104.

[0064] When the screw rotor 100 is applied to a screw compressor, during operation, the exhaust end face 104 of the screw rotor 100 and the fixed parts of the compressor need to be sealed as much as possible to form a closed compression space in the tooth groove 103. However, during operation, the screw rotor 100 is a rotating moving part, and a gap is often required between the exhaust end face 104 and the fixed parts of the compressor to ensure the reliability of the compressor. The existence of the gap causes the gas in one tooth groove 103 to leak from the gap at the exhaust end face 104 to the adjacent tooth groove 103 during the operation of the rotor, such as Figure 1 In the path a, since different tooth grooves 103 are in different compression conditions, gas leakage will affect the volumetric efficiency, resulting in a decrease in adiabatic efficiency and a loss of energy efficiency.

[0065] Based on this, Figure 2 As shown, a first seal 105 is provided on the screw rotor 100 of the embodiment of the present application. The first seal 105 is protrudingly provided on the exhaust end surface 104 , and one end of the first seal 105 extends to the tooth top of the rotor tooth 102 , and the other end extends to the rotating shaft 101 .

[0066] In this embodiment, reference Fig.11 and Fig.12 When the screw rotor 100 is working, the first seal 105 will fill the gap between the exhaust end face 104 and the fixed structure (such as the exhaust end bearing seat 300). The graphite first seal 105 will always be in close contact with the exhaust end bearing seat 300, forming a strict seal at the exhaust end face 104 of the screw rotor 100. First, because one end of the first seal 105 extends to the tooth top of the rotor tooth 102, and the other end extends to the shaft 101, the gas in the adjacent tooth grooves 103 on both sides of the first seal 105 can no longer follow the Figure 1The first seal 105 is connected with the path a in the middle, which solves the problem of gas leakage in the gap at the exhaust end face 104 in the conventional screw compressor, ensures the volumetric efficiency, and improves the insulation efficiency and energy efficiency of the compressor. In addition, since the first seal 105 is made of graphite, which has excellent chemical stability, high temperature resistance and lubricity, the friction of the first seal 105 on the friction contact surface is significantly reduced through the lubrication of graphite. This low friction characteristic is very important in the high-speed rotating screw compressor. It not only reduces the degree of wear, but also reduces the risk of sealing failure caused by friction heat accumulation, does not affect the reliability of the compressor, and ensures the efficient operation of the compressor.

[0067] In some embodiments, Figure 2 As shown in FIG. 7 , a plurality of first seals 105 are provided and are arranged one-to-one with the rotor teeth 102. The plurality of first seals 105 are respectively installed on the exhaust end face 104 of each rotor tooth 102, so that each rotor tooth 102 has an independent sealing protection function. During operation, each first seal 105 is respectively filled in the gap between the exhaust end face 104 and the fixed structure of the corresponding rotor tooth 102 to form a separate sealing barrier, so that the gas in the tooth groove 103 on both sides of any rotor tooth 102 cannot form a connection at the exhaust end face 104. Specifically, the two ends of each first seal 105 extend to the tooth top of the rotor tooth 102 and the rotating shaft 101, respectively, and fit accurately between the exhaust end face 104 and the fixed structure. This design greatly reduces the possibility of gas flowing along the gap of the exhaust end face 104 through circumferentially evenly distributed partitions and seals, blocks the path of gas leakage at the exhaust end face 104, and avoids the influence of pressure fluctuations of gas between the tooth grooves 103. For example Figure 1 and 7 The number of rotor teeth 102 and tooth grooves 103 is 5, and a total of 5 first seals 105 are provided. Each rotor tooth 102 is provided with a first seal 105, so that no gas leakage occurs at the exhaust end surface 104 between the 5 tooth grooves 103.

[0068] In some embodiments, Figure 3 and 4 As shown, a first fixing groove 106 is provided on the exhaust end surface 104, and the first sealing member 105 is fixed in the first fixing groove 106. Specifically, a plurality of first fixing grooves 106 may be provided on the exhaust end surface 104, and the number and position of the first fixing grooves 106 correspond to the number and arrangement of the first sealing members 105. The first sealing members 105 are fixed in the first fixing grooves 106, so that each first sealing member 105 is independently and stably located at the exhaust end surface 104 of the corresponding rotor tooth 102.

[0069] Preferably, the first seal 105 is formed by graphite die-casting in the first fixed groove 106, ensuring that the seal has reliable fixation and sealing effect under high temperature and high pressure environment. By fixing the first seal 105 by die-casting, not only the sealing stability of the first seal 105 is improved, but also the bonding degree between the seal and the rotor tooth 102 is ensured. During operation, the first seal 105 is firmly die-cast in the first fixed groove 106, so that it can more effectively withstand the pressure impact of the gas in the tooth groove 103, and remain without displacement under high-speed rotation, thereby maintaining the integrity of the sealing structure and the stability of performance, which helps to achieve efficient and long-term operation of the compressor.

[0070] In some embodiments, Figure 3 and 4 As shown, a second fixing groove 107 is provided at the connection between the rotating shaft 101 and the rotor tooth 102 . The second fixing groove 107 is connected to the first fixing groove 106 . The first sealing member 105 is fixed in both the first fixing groove 106 and the second fixing groove 107 .

[0071] The second fixing groove 107 provided at the connection between the rotating shaft 101 and the rotor teeth 102 is connected to the first fixing groove 106, so that the first seal 105 can be fixed in a larger range. Specifically, the first seal 105 is fixed in the first fixing groove 106 and the second fixing groove 107 at the same time during installation, forming a double-groove fixing structure spanning the rotor teeth 102 and the rotating shaft 101, and the extension directions of the first fixing groove 106 and the second fixing groove 107 are perpendicular to each other, so that the first seal 105 can be fixed in multiple degrees of freedom. Through this double-groove fixing method, the firmness of the first seal 105 in high-speed rotation and high-pressure environment is significantly improved, avoiding the problem of loosening or displacement of the seal in high-speed rotation, and improving the durability of the sealing system.

[0072] In addition, since the first seal 105 spans the rotor teeth 102 and the shaft 101, the seal can not only form a stable partition between the tooth grooves 103, but also provide an additional sealing effect at the intersection of the shaft 101 and the rotor teeth 102, preventing gas from leaking along the gap between the shaft 101 and the first seal 105. The design of the first seal 105 being located in the first fixed groove 106 and the second fixed groove 107 forms a more rigorous sealing system, reduces the leakage path of gas on both sides of the rotor teeth 102, and further improves the volumetric efficiency and thermal insulation efficiency.

[0073] When the screw rotor 100 is applied to a screw compressor, during operation, the tooth tops of the rotor teeth 102 of the screw rotor 100 and the fixed parts of the compressor also need to be sealed as much as possible to form a closed compression space in the tooth groove 103. However, during operation, the screw rotor 100 is a rotating moving part, and a gap is often required between the tooth tops of the rotor teeth 102 and the fixed parts of the compressor to ensure the reliability of the compressor. The existence of the gap causes the gas in one tooth groove 103 to leak from the tooth top of the rotor tooth 102 to the adjacent tooth groove 103 during the operation of the rotor, such as Figure 1 In the path b, since different tooth grooves 103 are in different compression conditions, gas leakage will affect the volumetric efficiency, resulting in a decrease in adiabatic efficiency and a loss of energy efficiency.

[0074] Based on this, in some embodiments, Figure 5-8 As shown, the screw rotor 100 for the screw compressor further includes a second seal 108 , which is protrudingly disposed on the tooth top of the rotor tooth 102 and is spirally disposed along the direction of the rotor tooth 102 . The material of the second seal 108 is also graphite.

[0075] The screw rotor 100 adds a second seal 108 at the tooth top of its rotor teeth 102, which can further improve the sealing performance of the screw compressor and reduce the risk of gas leakage. Specifically, the second seal 108 is protruding from the tooth top of the rotor tooth 102 and is arranged spirally along the direction of the rotor tooth 102. The second seal 108 can fill the gap between the tooth top of the rotor tooth 102 and the fixed part of the compressor (such as the inner wall of the housing 200) during operation, which helps to form an effective sealing barrier to prevent high-pressure gas from leaking from one tooth groove 103 to the adjacent tooth groove 103 bypassing the tooth top. Since the second seal 108 is arranged in a spiral shape along the tooth top, its sealing effect is enhanced, and it covers a long distance along the direction of the tooth top, and a continuous sealing surface is generated during the rotation of the screw, which effectively blocks the gas leakage between the tooth grooves 103. This design further improves the volumetric efficiency of the screw compressor, reduces the gas leakage problem caused by the tooth top gap, and improves the insulation efficiency and energy efficiency during the compression process.

[0076] In addition, since the material of the second seal 108 is also graphite, which has excellent chemical stability, high temperature resistance and lubricity, the lubrication of graphite significantly reduces the friction of the second seal 108 on the friction contact surface. This low friction characteristic is crucial in high-speed rotating screw compressors. It not only reduces the degree of wear, but also reduces the risk of seal failure caused by frictional heat accumulation. It will not affect the reliability of the compressor and ensures the efficient operation of the compressor.

[0077] In some embodiments, Figure 5-8As shown, the second seal 108 is provided in plurality and is arranged one-to-one with the rotor teeth 102. The plurality of second seals 108 are respectively installed on the tooth tops of the rotor teeth 102, so that each rotor tooth 102 has an independent sealing protection function. During operation, each second seal 108 is respectively filled in the gap between the tooth top and the fixed structure of the corresponding rotor tooth 102 to form a separate sealing structure, so that the gas in the tooth grooves 103 on both sides of any rotor tooth 102 cannot form a connection at the tooth top. For example Figure 5 and 6 The number of rotor teeth 102 and tooth grooves 103 is 5, and a total of 5 second seals 108 are provided. A second seal 108 is provided on each rotor tooth 102, so that no gas leakage occurs at the tooth top between the 5 tooth grooves 103.

[0078] In some embodiments, Figure 6 and 7 As shown, one end of the second seal 108 is connected to the first seal 105. One end of the second seal 108 is connected to the first seal 105, thereby forming a continuous and complete sealing path. This design enables the first seal 105 and the second seal 108 to work together to form an integrated sealing structure at the exhaust end face 104 and the tooth top position, effectively improving the sealing effect. When the screw compressor is running, since the first seal 105 fills the gap between the exhaust end face 104 and the fixed component, and the second seal 108 is located at the tooth top and connected to the first seal 105, a closed sealing path is achieved around the entire rotor tooth 102 structure. This sealing path can not only prevent high-pressure gas from leaking from the exhaust end face 104, but also prevent gas from leaking from the tooth top to the adjacent tooth groove 103. By connecting the first seal 105 and the second seal 108, the stability of the entire sealing system is further enhanced, and the energy efficiency performance of the compressor is improved.

[0079] In some embodiments, Figure 8As shown, the rotor teeth 102 are divided into a high-pressure section 109 close to the exhaust end face 104 and a low-pressure section 110 away from the exhaust end face 104 along the axial direction of the rotating shaft 101, and the second seal 108 is arranged in the high-pressure section 109 area of ​​the rotor teeth 102. Since the pressure of the gas in the tooth groove 103 of the low-pressure section 110 is relatively small during operation, the risk of leakage is low, and the traditional oil seal can effectively achieve the sealing at the tooth top gap of the low-pressure section 110, while the pressure of the gas in the tooth groove 103 of the high-pressure section 109 is very high, and the traditional oil seal is difficult to achieve effective sealing. The second seal 108 is specifically arranged in the high-pressure section 109, which can effectively enhance the sealing effect of the high-pressure section 109 and prevent the gas from leaking to the adjacent tooth groove 103 at the high-pressure section 109. This design can effectively manage the pressure difference in different areas, ensure the efficient transmission of gas during the compression process, reduce the energy loss caused by leakage, and avoid the reliability problems and costs caused by the second seal 108 being arranged in the low-pressure section 110, thereby improving the overall operating efficiency and stability of the compressor.

[0080] In some embodiments, along the axis direction of the rotating shaft 101, as the distance from the exhaust end face 104 gradually increases, the height of the first seal 105 protruding from the tooth top gradually decreases. This design is based on the consideration that the gas pressure in the area close to the exhaust end face 104 is relatively high, and the risk of leakage is relatively large. In this area, the protruding height of the seal is designed to be high to ensure that it can effectively fill the gap between the exhaust end face 104 and the fixed component, thereby preventing gas leakage and maintaining the sealing and efficiency inside the compressor. As the distance from the exhaust end face 104 increases, the working gas pressure in the tooth groove 103 gradually decreases, and the protruding height of the seal can also be reduced accordingly. There is no need to completely close the gap at the tooth top, and the remaining gap can be sealed with the help of an oil seal. This gradual height design has multiple advantages. First, the reduced height reduces the friction between the seal and the fixed component, reduces the heat generated by friction, thereby reducing the wear and fatigue of the second seal 108 and extending its service life. In addition, in the high-pressure section 109, the height of the second seal 108 is relatively high, which compensates for the problem of oil seal failure and can effectively resist high-pressure gas leakage. In the low-pressure section 110, the reduction in the height of the seal can ensure that in a lower air pressure environment, the second seal 108 with a reduced protruding height and the oil seal can still achieve effective sealing through cooperation.

[0081] It should be noted that the height of the second seal 108 above the tooth top of the rotor tooth 102 should not be too long, as too long will increase the friction resistance, and too short will not achieve an ideal sealing state. Preferably, when the diameter D of the rotor tooth 102 is ≤ 200 mm, the height of the protruding tooth top of the second seal 108 in the area close to the exhaust end face 104 is preferably 0.2 mm; when the diameter D of the rotor tooth 102 is greater than 200 mm, the height of the protruding tooth top of the second seal 108 in the area close to the exhaust end face 104 is preferably 0.3 mm to 0.4 mm.

[0082] In addition, the cross-sectional shapes of the first sealing member 105 and the second sealing member 108 include but are not limited to rectangular, trapezoidal, circular and the like.

[0083] In some embodiments, Figure 3 and 4 As shown, a third fixing groove 111 is provided on the tooth top of the rotor tooth 102, and the second seal 108 is fixed in the third fixing groove 111. The second seal 108 is fixed in the third fixing groove 111 so that it can be firmly integrated with the rotor tooth 102. In this way, during the rotation of the rotor, the seal can maintain a stable position to avoid displacement of the seal due to rotor movement, thereby improving the reliability of the seal. The provision of the third fixing groove 111 makes the installation position of the second seal 108 more precise and effectively controls the height of the protruding tooth top.

[0084] Preferably, the second seal 108 made of graphite is fixed in the third fixed groove 111 by a die-casting process, which can ensure that it will not fall off due to vibration or friction during operation. This fixing method not only improves the manufacturing accuracy, but also effectively reduces the production cost and time, that is, the simplified production process of die-casting graphite in the third fixed groove 111 helps to improve production efficiency. The setting of the die-cast second seal 108 in the third fixed groove 111 not only improves the sealing effect, but also enhances the overall structural strength of the screw rotor 100, thereby improving the reliability and durability of the screw compressor under high-pressure working environment.

[0085] In some embodiments, preferably, the layered structure of the graphite material in the first fixed groove 106 and the third fixed groove 111 is substantially perpendicular to the direction of the groove depth. In terms of crystal structure, graphite is composed of a layered structure, and each layer is a hexagonal grid formed by six carbon atoms connected by covalent bonds. This structure determines that the above-mentioned graphite material can obtain the best lubrication and friction reduction effect on the contact surface. On the other hand, the above-mentioned crystal structure makes the expansion coefficient of the graphite material perpendicular to its layered structure direction very small, and the expansion coefficient in the direction parallel to its layered structure is large. Through this design, when the first seal 105 and the second seal 108 are heated in a high-temperature working environment, they can produce a large amount of expansion in a direction perpendicular to the groove depth, forming an interference fit connected to the first fixed groove 106 and the third fixed groove 111, so that the first seal 105 and the second seal 108 are firmly fixed in the groove to prevent loosening and leakage. Due to the above-mentioned characteristics of graphite, the first seal 105 and the second seal 108 can be prevented from generating excessive expansion along the direction of the groove depth, which effectively prevents the first seal 105 and the second seal 108 from being excessively squeezed between the fixed structure after a large deformation in the radial direction of the screw rotor 100, thereby reducing friction and ensuring the reliability and long-term stable operation of the equipment.

[0086] like Figure 9-12 As shown, the screw compressor provided in the embodiment of the present application mainly includes a shell 200, an exhaust end bearing seat 300, an intake end bearing seat 400 and a screw rotor 100. The exhaust end bearing seat 300 and the intake end bearing seat 400 are respectively arranged at the two ends of the axial direction of the shell 200. The shell 200, the exhaust end bearing seat 300 and the intake end bearing seat 400 together form a working chamber 500. The exhaust end bearing seat 300 forms an exhaust end mating surface 301 on the side facing the working chamber 500.

[0087] The screw rotor 100 is provided for the aforementioned embodiment of the present application, that is, the screw rotor 100 includes a rotating shaft 101, a rotor tooth 102 and a first seal 105, wherein a plurality of rotor teeth 102 are provided, and the plurality of rotor teeth 102 are spirally arranged outside the rotating shaft 101, and a tooth groove 103 is formed between adjacent rotor teeth 102, and an exhaust end face 104 is formed at one axial end of the rotor tooth 102, and a first seal 105 is protrudingly arranged on the exhaust end face 104, and one end of the first seal 105 extends to the tooth top of the rotor tooth 102, and the other end extends to the rotating shaft 101. The two ends of the rotating shaft 101 respectively penetrate the exhaust end bearing seat 300 and the suction end bearing seat 400, the rotor tooth 102 is located in the working chamber 500, a first gap 501 is formed between the exhaust end face 104 and the exhaust end mating surface 301, and the first seal 105 is filled in the first gap 501.

[0088] The screw compressor effectively fills the first gap 501 between the exhaust end face 104 and the exhaust end mating face 301 by providing the first seal 105, and improves the sealing performance between adjacent tooth grooves 103 at the first gap 501. The improved sealing performance reduces the leakage of gas between different tooth grooves 103 through the first gap 501, thereby reducing the pressure loss, so that the compressor can more effectively maintain the overall energy efficiency during operation. And by blocking the exhaust leakage in the first gap 501, the flow path of the gas in the rotor becomes more stable, so that the compressed gas is discharged from the screw compressor through the exhaust port, thereby improving the operating state of the compressor and the gas discharge efficiency.

[0089] In some embodiments, the screw rotor 100 further includes a second seal 108, which is protrudingly disposed on the tooth top of the rotor tooth 102 and is disposed in a spiral shape along the direction of the rotor tooth 102; a second gap 502 is formed between the tooth top of the rotor tooth 102 and the inner wall of the housing 200, and the second seal 108 fills the second gap 502. The second seal 108 fills the second gap 502 between the tooth top of the rotor tooth 102 and the inner wall of the housing 200, effectively preventing gas leakage through the second gap 502. This sealing design ensures that during the compression process, the gas does not flow unnecessarily between different tooth grooves 103, further improving the overall sealing effect.

[0090] Since the screw compressor disclosed in the embodiment of the present application includes the screw rotor provided in the above embodiment, the screw compressor having the screw rotor also has all the above technical effects, which will not be described one by one here. Specifically, the male rotor and the female rotor in the screw compressor can both adopt the screw rotor in the above embodiment. The other structures, principles and connection relationships of the screw compressor are known to ordinary technicians in the field and will not be described in detail here.

[0091] Some embodiments in this specification are described in a progressive or parallel manner. Each embodiment focuses on the differences from other embodiments, and the same or similar parts between the embodiments can be referenced to each other.

[0092] The above is only a specific implementation of the present application, so that those skilled in the art can understand or implement the present application. Various modifications to these embodiments will be apparent to those skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application will not be limited to the embodiments shown herein, but will conform to the widest range consistent with the principles and novel features applied for herein.

Claims

1. A screw rotor for a screw compressor, characterized in that: include: A rotating shaft (101); A plurality of rotor teeth (102) are provided and are spirally arranged outside the rotating shaft (101), tooth grooves (103) are formed between adjacent rotor teeth (102), and an axial end of the rotor tooth (102) forms an exhaust end surface (104); A first sealing member (105) is protrudingly arranged on the exhaust end surface (104), one end of the first sealing member (105) extends to the tooth top of the rotor tooth (102), and the other end extends to the rotating shaft (101), and the material of the first sealing member (105) is graphite.

2. The screw rotor for a screw compressor according to claim 1, characterized in that: A plurality of the first sealing members (105) are provided and are arranged in one-to-one correspondence with the rotor teeth (102).

3. The screw rotor for a screw compressor according to claim 1, characterized in that: The exhaust end surface (104) is provided with a first fixing groove (106), and the first sealing member (105) is fixed in the first fixing groove (106).

4. The screw rotor for a screw compressor according to claim 3, characterized in that: A second fixing groove (107) is provided at the connection between the rotating shaft (101) and the rotor tooth (102); the second fixing groove (107) is connected to the first fixing groove (106); and the first sealing member (105) is fixed in both the first fixing groove (106) and the second fixing groove (107).

5. The screw rotor for a screw compressor according to claim 1, characterized in that: The invention also comprises a second sealing member (108), wherein the second sealing member (108) is protrudingly arranged on the tooth top of the rotor tooth (102) and is spirally arranged along the direction of the rotor tooth (102), and the material of the second sealing member (108) is graphite.

6. The screw rotor for a screw compressor according to claim 5, characterized in that: One end of the second sealing member (108) is connected to the first sealing member (105).

7. The screw rotor for a screw compressor according to claim 5, characterized in that: The rotor tooth (102) is divided into a high-pressure section (109) close to the exhaust end surface (104) and a low-pressure section (110) away from the exhaust end surface (104) along the axial direction of the rotating shaft (101), and the second sealing member (108) is arranged in the high-pressure section (109) of the rotor tooth (102).

8. The screw rotor for a screw compressor according to claim 5, characterized in that: Along the axial direction of the rotating shaft (101), as the distance from the exhaust end surface (104) gradually increases, the height of the first sealing member (105) protruding from the tooth top gradually decreases.

9. The screw rotor for a screw compressor according to claim 5, characterized in that: A third fixing groove (111) is provided on the tooth top of the rotor tooth (102), and the second sealing member (108) is fixed in the third fixing groove (111).

10. A screw compressor, characterized in that: include: Housing (200); The exhaust end bearing seat (300) and the suction end bearing seat (400) are respectively arranged at two axial ends of the housing (200); the housing (200), the exhaust end bearing seat (300) and the suction end bearing seat (400) together form a working chamber (500); and the exhaust end bearing seat (300) forms an exhaust end mating surface (301) on one side facing the working chamber (500); According to the screw rotor (100) as described in any one of claims 1 to 9, both ends of the rotating shaft (101) respectively pass through the exhaust end bearing seat (300) and the suction end bearing seat (400), the rotor teeth (102) are located in the working chamber (500), a first gap (501) is formed between the exhaust end surface (104) and the exhaust end mating surface (301), and the first sealing member (105) is filled in the first gap (501).

11. The screw compressor according to claim 10, characterized in that: The screw rotor (100) further comprises a second seal (108), the second seal (108) being protrudingly arranged on the tooth top of the rotor tooth (102) and being spirally arranged along the direction of the rotor tooth (102); a second gap (502) is formed between the tooth top of the rotor tooth (102) and the inner wall of the housing (200), and the second seal (108) is filled in the second gap (502).

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