Screw rotor for screw compressor and screw compressor

Abstract

The utility model 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, technology, and society, large buildings are becoming increasingly common, and the market share of commercial air conditioners is increasing year by year. The screw compressor, a core component of air conditioners and known as the heart of the air conditioner, is a positive displacement compressor. Its core consists of a stack of intermeshing rotors. The intermeshing of the toothed male rotors (convex) and the toothed female rotors (concave) creates a volume between the teeth. During rotation, this volume increases and then decreases, achieving the intake, compression, and discharge of gas.

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

[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] shaft;

[0007] A plurality of rotor teeth are provided and are spirally arranged on the outside of 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] A first sealing member is protrudingly provided 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 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, a second sealing member is included, which is protruding from 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 face and a low-pressure section away from the exhaust end face along the axial direction of the rotating shaft, and the second seal 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 are graphite.

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

[0019] case;

[0020] An exhaust end bearing seat and an intake end bearing seat are respectively arranged at two axial ends of the housing, wherein the housing, the exhaust end bearing seat and the intake end bearing seat together form a working chamber, and a side of the exhaust end bearing seat facing the working chamber forms an exhaust end mating surface; 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 surface and the exhaust end mating surface, 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 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 in operation, the first seal will fill the gap between the exhaust end face and the fixed structure (such as the exhaust end bearing seat). The first seal made of graphite will always be in close contact with the exhaust end bearing seat, forming a strict seal at the exhaust end face of the screw rotor. This solves the problem of gas leakage in the gap at the exhaust end face in conventional screw compressors, ensures volumetric efficiency, and improves the thermal insulation efficiency and energy efficiency of the compressor. In addition, since the material of the first seal is graphite, it has excellent chemical stability, high temperature resistance and lubricity. The lubrication effect of graphite significantly reduces the friction of the first seal on the friction contact surface, which 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. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The drawings that constitute part of this application are used to provide a further understanding of this application and make other features, objects and advantages of this application more apparent. The illustrative embodiment drawings of this application and their descriptions are used to explain this application and do not constitute an improper limitation of this application. In the drawings:

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

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

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

[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 one embodiment of the present application is schematically shown;

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

[0031] Figure 7 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 one embodiment of the present application is schematically shown;

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

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

[0035] Figure 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] Figure 12 for Figure 11 A partial enlarged view of part C.

[0037] In the picture:

[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. First sealing member;

[0044] 106. 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 slot;

[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 present invention, the following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments in the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts should fall within the scope of protection of this application.

[0058] It should be noted that the terms "including" and "having" and any variations thereof in the specification and claims of this 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 are inherent to these products or devices.

[0059] In this application, terms such as "upper," "lower," "inner," "middle," and "outer" indicate positions or locations based on those shown in the accompanying drawings. These terms are intended to better describe this application and its embodiments and are not intended to limit the devices, elements, or components indicated to specific positions, or to their construction or operation in a specific position.

[0060] Furthermore, some of the above terms may be used to express other meanings besides indicating a position or location. For example, the term "on" may also be used to indicate a dependency or connection in certain circumstances. Those skilled in the art will understand the specific meanings of these terms in this application based on the specific circumstances.

[0061] Furthermore, the terms "disposed," "connected," and "fixed" should be interpreted broadly. For example, "connected" can mean a fixed connection, a removable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection, an indirect connection through an intermediary, or an internal communication between two devices, elements, or components. Those skilled in the art will understand the specific meanings of these terms in this application based on the specific circumstances.

[0062] It should be noted that, unless there is any conflict, the embodiments and features in the embodiments of this application can be combined with each other.

[0063] like Figure 1As shown, a basic structural diagram of a screw rotor 100 for a screw compressor is provided. The patent for a twin-screw compressor is used as an example for illustration, but the screw rotor 100 provided in this application can also be applied to other screw compressors. A twin-screw compressor includes a pair of meshing male rotors 100-1 and female rotors 100-2. The teeth of the male rotor 100-1 are convex, while the teeth of the female rotor 100-2 are concave. The meshing of the two rotors forms an inter-tooth volume. During rotation, the inter-tooth volume increases and then decreases, achieving gas intake, compression, and discharge. 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 provided, and the plurality of rotor teeth 102 are spirally arranged on the outside of the rotating shaft 101. Tooth grooves 103 are formed between adjacent rotor teeth 102, and one axial end of the rotor teeth 102 forms an exhaust end surface 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 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, the screw rotor 100 of the embodiment of the present application is provided with a first seal 105 , which is protrudingly provided on the exhaust end surface 104 , with one end of the first seal 105 extending to the tooth top of the rotor tooth 102 , and the other end extending to the rotating shaft 101 .

[0066] In this embodiment, reference Figure 11 and Figure 12 When the screw rotor 100 is in operation, 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 flow in the direction of the first seal. Figure 1The first seal 105 is connected to the path a in the middle, thereby solving the problem of gas leakage in the gap at the exhaust end face 104 in the conventional screw compressor, ensuring volumetric efficiency, and improving the thermal 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 lubrication effect of graphite significantly reduces the friction of the first seal 105 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, does not affect the reliability of the compressor, and ensures the efficient operation of the compressor.

[0067] In some embodiments, as Figure 2 As shown in FIG7 , a plurality of first seals 105 are provided and are arranged in one-to-one correspondence with the rotor teeth 102. A 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 of the corresponding rotor tooth 102 and the fixed structure 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 for gas leakage at the exhaust end face 104, and avoids the influence of pressure fluctuations of the gas between the tooth grooves 103. For example Figure 1 and 7 The number of rotor teeth 102 and tooth grooves 103 is 5, so a total of 5 first seals 105 are provided, and 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, as Figure 3 and 4 As shown, a first fixing groove 106 is defined on the exhaust end surface 104, and the first sealing member 105 is fixed in the first fixing groove 106. Specifically, the exhaust end surface 104 may be provided with multiple first fixing grooves 106, with the number and position of the first fixing grooves 106 corresponding 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 positioned on 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 to ensure that the seal has reliable fixation and sealing effect in a 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 teeth 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, as Figure 3 and 4 As shown, a second fixing groove 107 is provided at the connection between the rotating shaft 101 and the rotor teeth 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 .

[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, allowing the first seal 105 to be fixed within a wider range. Specifically, during installation, the first seal 105 is simultaneously fixed within the first fixing groove 106 and the second fixing groove 107, forming a dual-groove fixing structure that spans the rotor teeth 102 and the rotating shaft 101. The first fixing groove 106 and the second fixing groove 107 extend in perpendicular directions, allowing the first seal 105 to be fixed in multiple degrees of freedom. This dual-groove fixing method significantly improves the firmness of the first seal 105 under high-speed rotation and high-pressure environments, avoids the problem of loosening or displacement of the seal during high-speed rotation, and improves the durability of the sealing system.

[0072] Furthermore, because the first seal 105 spans the rotor teeth 102 and the shaft 101, it not only forms a stable barrier between the tooth grooves 103 but also provides an additional sealing effect at the intersection of the shaft 101 and the rotor teeth 102, preventing gas leakage along the gap between the shaft 101 and the first seal 105. The design of the first seal 105 within the first and second fixing grooves 106 and 107 creates a more stringent sealing system, reducing the gas leakage path on both sides of the rotor teeth 102, thereby further improving 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 need to be sealed as much as possible to form a closed compression space in the tooth grooves 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, such as Figure 5-8 As shown, the screw rotor 100 for the screw compressor further includes a second seal 108 . The second seal 108 is protruding from the tooth top of the rotor teeth 102 and is spirally arranged along the direction of the rotor teeth 102 . The material of the second seal 108 is also graphite.

[0075] The addition of a second seal 108 to the top of the rotor teeth 102 of the screw rotor 100 further improves the sealing performance of the screw compressor and reduces the risk of gas leakage. Specifically, the second seal 108 protrudes from the top of the rotor teeth 102 and is arranged spirally along the direction of the rotor teeth 102. During operation, the second seal 108 fills the gap between the top of the rotor teeth 102 and the fixed components of the compressor (such as the inner wall of the housing 200), helping to form an effective sealing barrier, preventing high-pressure gas from leaking from one tooth groove 103 around the tooth top to the adjacent tooth groove 103. Because the second seal 108 is arranged in a spiral shape along the tooth top, its sealing effect is enhanced. The long-distance coverage along the tooth top creates a continuous sealing surface during the screw rotation, effectively preventing gas leakage between the tooth grooves 103. This design further improves the volumetric efficiency of the screw compressor, reduces the problem of gas leakage caused by tooth tip clearance, and improves the thermal 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 lubricating effect 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, as Figure 5-8As shown, there are multiple second seals 108 and they are arranged one-to-one with the rotor teeth 102. Multiple second seals 108 are respectively installed on the tooth tops of each rotor tooth 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 of the corresponding rotor tooth 102 and the fixed structure 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 slots 103 is 5, so a total of 5 second seals 108 are provided, and each rotor tooth 102 is provided with a second seal 108, so that no gas leakage occurs at the tooth top between the 5 tooth slots 103.

[0078] In some embodiments, as 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, forming a continuous and complete sealing path. This design allows the first and second seals 105, 108 to work together to form an integrated sealing structure at the exhaust end face 104 and the tooth top, effectively improving the sealing effect. When the screw compressor is operating, because 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 not only prevents high-pressure gas from leaking from the exhaust end face 104, but also prevents 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, improving the energy efficiency of the compressor.

[0079] In some embodiments, as Figure 8As shown, the rotor teeth 102 are divided axially along the shaft 101 into a high-pressure section 109 near the exhaust end face 104 and a low-pressure section 110 away from the exhaust end face 104. The second seal 108 is disposed within the high-pressure section 109 of the rotor tooth 102. During operation, the gas pressure within the tooth slots 103 in the low-pressure section 110 is relatively low, resulting in a lower risk of leakage. Conventional oil seals can effectively seal the tooth tip clearances in the low-pressure section 110. However, the gas pressure within the tooth slots 103 in the high-pressure section 109 is high, making it difficult for conventional oil seals to achieve effective sealing. The targeted placement of the second seal 108 in the high-pressure section 109 effectively enhances the sealing effect of the high-pressure section 109 and prevents gas leakage from the high-pressure section 109 to adjacent tooth slots 103. This design effectively manages pressure differences between different regions, ensuring efficient gas transmission during the compression process and reducing energy loss caused by leakage. It also avoids the reliability issues and costs associated with installing the second seal 108 in the low-pressure section 110, thereby improving the overall operating efficiency and stability of the compressor.

[0080] In some embodiments, along the axial 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 takes into account that the gas pressure in the area close to the exhaust end face 104 is higher and the risk of leakage is relatively greater. In this area, the protruding height of the seal is designed to be higher 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 air pressure in the tooth groove 103 gradually decreases. At this time, the protruding height of the seal can also be reduced accordingly. There is no need to completely close the gap at the tooth top. 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, and thus reduces the wear and fatigue of the second seal 108, extending its service life. In addition, in the high-pressure section 109, the height of the second seal 108 is higher, 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.

[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 frictional 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, as Figure 3 and 4 As shown, a third fixing groove 111 is defined on the tooth tip of the rotor tooth 102, and the second seal 108 is secured within this third fixing groove 111. Securing the second seal 108 within the third fixing groove 111 secures it to the rotor tooth 102. This allows the seal to maintain a stable position during rotor rotation, preventing seal displacement due to rotor movement and improving sealing reliability. The provision of the third fixing groove 111 allows for more precise installation of the second seal 108, effectively controlling the height of the protruding tooth tip.

[0084] The second seal 108 made of graphite is preferably fixed in the third fixing groove 111 through a die-casting process to ensure that it will not fall off due to vibration or friction during operation. This fixing method not only improves manufacturing accuracy, but also effectively reduces production costs and time. In other words, the simplified production process of die-casting graphite in the third fixing groove 111 helps to improve production efficiency. The arrangement of the die-cast second seal 108 in the third fixing 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 in a 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 graphite material provided above 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 in the direction perpendicular to its layered structure very small, while the expansion coefficient in the direction parallel to its layered structure is larger. 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 the 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 expanding excessively along the direction of the groove depth, effectively preventing the first seal 105 and the second seal 108 from being excessively squeezed between the fixed structure after a large radial deformation 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 axial ends 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, and 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 in accordance with the aforementioned embodiment of the present application, namely, the screw rotor 100 includes a rotating shaft 101, rotor teeth 102, and a first seal 105. A plurality of rotor teeth 102 are provided, spirally arranged on the exterior of the rotating shaft 101, with tooth grooves 103 formed between adjacent rotor teeth 102. An exhaust end surface 104 is formed at one axial end of the rotor teeth 102. A first seal 105 protrudes from the exhaust end surface 104, with one end of the first seal 105 extending to the tooth top of the rotor teeth 102 and the other end extending to the rotating shaft 101. The ends of the rotating shaft 101 respectively extend through the exhaust end bearing seat 300 and the intake end bearing seat 400. The rotor teeth 102 are located within the working chamber 500. A first gap 501 is formed between the exhaust end surface 104 and the exhaust end mating surface 301. The first seal 105 fills the first gap 501.

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

[0089] In some embodiments, the screw rotor 100 further includes a second seal 108, which protrudes from the tooth tips of the rotor teeth 102 and is arranged in a spiral pattern along the direction of the rotor teeth 102. A second gap 502 is formed between the tooth tips of the rotor teeth 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 tips of the rotor teeth 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, gas does not flow unnecessarily between the different tooth slots 103, further improving the overall sealing effect.

[0090] Since the screw compressor disclosed in the embodiments of this application includes the screw rotor provided in the aforementioned embodiments, the screw compressor including this screw rotor also has all the aforementioned technical effects, which will not be described in detail here. Specifically, both the male and female rotors in the screw compressor can employ the screw rotors in the aforementioned embodiments. The other structures, principles, and connection relationships of the screw compressor are known to those skilled in the art 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 are merely specific embodiments of the present application to enable those skilled in the art to 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 may 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 rather is intended to conform to the widest scope consistent with the principles and novel features of the present application.

Claims

1. A screw rotor for a screw compressor, characterized in that: include: Rotating shaft (101); A plurality of rotor teeth (102) are provided and are spirally arranged on the outside of 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, wherein A plurality of 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, wherein 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).

4. The screw rotor for a screw compressor according to claim 3, wherein A second fixing groove (107) is provided at the connection between the rotating shaft (101) and the rotor teeth (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, wherein The invention also includes a second sealing member (108), which is protruding from the tooth top of the rotor tooth (102) and spirally arranged along the direction of the rotor tooth (102). 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, wherein 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, wherein 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, wherein 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); An exhaust end bearing seat (300) and an intake 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 intake end bearing seat (400) together form a working chamber (500); and a side of the exhaust end bearing seat (300) facing the working chamber (500) forms an exhaust end mating surface (301); According to the screw rotor (100) according to 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 includes a second seal (108), which is protruding from the tooth top of the rotor tooth (102) and is 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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