Compressor and compression system

Abstract

The application is suitable for the compressor technical field, and provides a compressor and a compression system. The compressor comprises a shell comprising a compression cavity, a first gas inlet and a second gas inlet are arranged on the shell, and a radial exhaust port is arranged at the bottom of the shell; a rotor assembly is installed in the compression cavity, and the rotor assembly comprises a male rotor assembly and a female rotor assembly; the male rotor assembly comprises a right-handed male rotor and a left-handed male rotor which are symmetrically arranged; the female rotor assembly comprises a right-handed female rotor and a left-handed female rotor which are symmetrically arranged; an axial exhaust baffle is arranged at the middle position of the shell, and the compression cavity is divided into a first compression cavity and a second compression cavity by the axial exhaust baffle; the axial exhaust baffle is provided with an axial exhaust port which is communicated with the first compression cavity and the second compression cavity. By arranging the axial exhaust port, the gas in the two cavities is converged, and the bottom radial exhaust port is matched, so that the gas is prevented from remaining in the shell, and the exhaust resistance is reduced.

Description

Technical Field

[0001] This application relates to the field of compressor technology, and in particular to a compressor and a compression system. Background Technology

[0002] A twin-screw compressor is a positive displacement compressor that compresses a medium through the rotational motion of a pair of meshing male and female rotors. Existing twin-screw compressors have a single inlet and a single outlet. Gas enters the compression chamber from the inlet at one end, is compressed, and then exits from the outlet at the other end. This type of compressor suffers from an uneven distribution of high-pressure gas reaction forces on the male and female rotors, resulting in a short service life. Utility Model Content

[0003] The purpose of this application is to provide a compressor and compression system that can improve the above-mentioned problems.

[0004] One aspect of this application provides a compressor, the compressor comprising: a housing, a compression cavity formed within the housing, a first air inlet and a second air inlet on the housing, and a radial exhaust port at the bottom of the housing; a rotor assembly mounted in the compression cavity, the rotor assembly comprising a male rotor assembly and a female rotor assembly, the male rotor assembly comprising a right-handed male rotor and a left-handed male rotor symmetrically arranged, and the female rotor assembly comprising a right-handed female rotor and a left-handed female rotor symmetrically arranged; and an axial exhaust baffle disposed at the middle position of the housing, dividing the compression cavity into a first compression cavity and a second compression cavity, the axial exhaust baffle having an axial exhaust port communicating with the first compression cavity and the second compression cavity.

[0005] In some embodiments of this application, the male rotor assembly includes a male spindle, and the right-handed male rotor and the left-handed male rotor are mounted on the male spindle; the female rotor assembly includes a female spindle, and the left-handed female rotor and the right-handed female rotor are mounted on the female spindle; the axial exhaust baffle is installed at the intermediate step between the male spindle and the female spindle, and the axial exhaust port is a through hole structure.

[0006] In some embodiments of this application, the right-hand male rotor and the left-hand male rotor are equal-pitch structures generated based on the same end face tooth profile, and the left-hand female rotor and the right-hand female rotor are equal-pitch structures generated based on the same end face tooth profile. The right-hand male rotor and the left-hand female rotor mesh to form a first compression pair located in the first compression chamber, and the left-hand male rotor and the right-hand female rotor mesh to form a second compression pair located in the second compression chamber.

[0007] In some embodiments of this application, the axial exhaust port is formed by a first side, a second side, a third side, a fourth side, and a fifth side. When both the male rotor assembly and the female rotor assembly are in the exhaust angle position, the first side coincides with the tooth projection line of the male rotor assembly on the axial exhaust baffle, the second side coincides with the tooth root circle projection line of the male rotor assembly on the axial exhaust baffle, the third side coincides with the projection line of the meshing line of the male rotor assembly and the female rotor assembly on the axial exhaust baffle, the fourth side coincides with the tooth root circle projection line of the female rotor assembly on the axial exhaust baffle, and the fifth side coincides with the tooth projection line of the female rotor assembly on the axial exhaust baffle.

[0008] In some embodiments of this application, the first air inlet and the second air inlet are symmetrically distributed on both sides of the upper part of the housing, and the radial exhaust port is located in the middle of the bottom of the housing.

[0009] In some embodiments of this application, the axial exhaust port is connected to the radial exhaust port, and the radial exhaust port is located directly below the axial exhaust port.

[0010] In some embodiments of this application, the outline of the radial exhaust port is formed by a sixth side, a seventh side, an eighth side, and a ninth side, wherein the sixth side is configured such that, at the exhaust angle position of the left-hand female rotor, the sixth side coincides with the projection line of the tooth tip helix of the left-hand female rotor on the housing; the seventh side is configured such that, at the exhaust angle position of the right-hand female rotor, the seventh side coincides with the projection line of the tooth tip helix of the right-hand female rotor on the housing; the eighth side is configured such that, at the exhaust angle position of the right-hand male rotor, the eighth side coincides with the projection line of the tooth tip helix of the right-hand male rotor on the housing; and the ninth side is configured such that, at the exhaust angle position of the left-hand male rotor, the ninth side coincides with the projection line of the tooth tip helix of the left-hand male rotor on the housing.

[0011] In some embodiments of this application, the housing includes a first housing and a second housing arranged symmetrically, a first compression chamber is formed in the first housing, a second compression chamber is formed in the second housing, the axial exhaust baffle is disposed between the first housing and the second housing, the first side and the third side are located on the first housing, and the second side and the fourth side are located on the second housing.

[0012] In some embodiments of this application, when the gas is compressed to the target compression volume, the axial exhaust port and the radial exhaust port exhaust gas simultaneously.

[0013] A second aspect of this application also provides a compression system comprising the aforementioned compressor.

[0014] This application employs a symmetrical structural design. The radial and axial forces generated by the symmetrically designed female and male rotor assemblies during rotation can cancel each other out, reducing compressor vibration and wear, and extending equipment life. Simultaneously, the first and second air inlets supply gas to the first and second compression chambers, respectively. The compressed gas first collects through the axial exhaust port on the axial exhaust baffle and then exits through the radial exhaust port at the bottom of the housing. By setting the axial exhaust port, gas flow between the two chambers is achieved, and in conjunction with the bottom radial exhaust port, gas stagnation within the housing is prevented, reducing exhaust resistance. Attached Figure Description

[0015] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the description of the embodiments of this application or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0016] Figure 1 This is a first-view structural schematic diagram of the compressor shown in some embodiments of this application; Figure 2 yes Figure 1 The diagram shows the compressor from a second-view perspective. Figure 3 yes Figure 1 The diagram shows the structure of the compressor with the casing port removed. Figure 4 yes Figure 1 The diagram shows a partial casing and axial exhaust baffle structure of the compressor. Figure 5 This is a schematic diagram of the structure of the first suction end seat in some embodiments of this application; Figure 6 yes Figure 5 The intake end face of the first intake end seat; Figure 7 This is a schematic diagram of the structure of the second suction end seat in some embodiments of this application; Figure 8 yes Figure 7 The intake end face of the second intake end seat; Figure 9 This is a schematic diagram of the internal structure of the first compression chamber in some embodiments of this application; Figure 10 This is a schematic diagram of the internal structure of the second compression chamber in some embodiments of this application; Figure 11 This is a schematic diagram of the compressor structure after removing part of the housing in some embodiments of this application; Figure 12This is a schematic diagram of the male and female spindles in some embodiments of this application; Figure 13 This is a schematic diagram of the axial suction baffle in some embodiments of this application; Figure 14 This is a bottom view of the compressor section structure in some embodiments of this application; Figure 15 This is a schematic diagram of the radial exhaust port structure in some embodiments of this application; Figure 16 This is a schematic diagram of the meshing structure of the male rotor assembly and the female rotor assembly in some embodiments of this application; Figure 17 This is a force diagram of the compressor in some embodiments of this application; Figure label: 1-Shell, 11-First shell, 12-Second shell, 110-First air inlet, 120-Second air inlet, 100-Radial exhaust port, 101-First compression chamber, 102-Second compression chamber; 111-First helix, 112-Second helix, 121-Third helix, 122-Fourth helix; 2-Rotor assembly, 21-Male rotor assembly, 22-Female rotor assembly, 211-Right-hand male rotor, 212-Left-hand male rotor, 221-Left-hand female rotor, 222-Right-hand female rotor, 213-Male spindle, 223-Female spindle, 214-Male spindle intermediate step, 224-Female spindle intermediate step; 3-Axial exhaust baffle; 31-Axial exhaust port; 41-First suction end seat, 411-First suction shaft end groove, 42-Second suction end seat, 421-Second suction shaft end groove; 51 - First bearing, 52 - Second bearing; L1 - First side, L2 - Second side, L3 - Third side, L4 - Fourth side, L5 - Fifth side, L6 - Sixth side, L7 - Seventh side, L8 - Eighth side, L9 - Ninth side. Detailed Implementation

[0017] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0018] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0019] In the description of this specification, specific features, structures, materials, or characteristics may be combined in any suitable manner in one or more embodiments or examples.

[0020] A twin-screw compressor is a positive displacement compressor that compresses a medium through the rotational motion of a pair of meshing male and female rotors. During compression, the medium is compressed within the compression chamber, and the medium pressure gradually increases, generating radial and axial gas forces on the surfaces of the male and female rotors. The radial gas force acting on the male and female rotors is perpendicular to the rotor axis and acts on the rotor tooth surface. Due to the different radial pressures between each tooth, the maximum radial load is concentrated on the exhaust side, where the suction side pressure is low and the exhaust side pressure is high, forming a pressure gradient. This results in a tilting moment throughout the rotor.

[0021] The male and female rotors are subjected to axial gas force along the rotor axis, mainly generated by the high-pressure gas at the exhaust end. However, due to the high pressure near the exhaust side and the low pressure on the intake side, a pressure gradient is formed, resulting in uneven force on the bearings at both ends of the male and female rotors. In addition, existing compressor structures require thrust bearings (tapered roller bearings, angular contact bearings) to bear the axial tension to prevent axial movement of the rotor.

[0022] Therefore, in order to solve the above problems, combined with Figures 1 to 17 As shown, this application proposes a twin-screw compressor in which both the female and male rotors are split symmetrical rotors, which balances the axial forces on the compressor.

[0023] In some embodiments of this application, such as Figures 1 to 4 As shown, the compressor includes: a housing 1, within which a compression chamber is formed. The housing 1 includes a first housing 11 and a second housing 12 symmetrically arranged. A first air inlet 110 is formed on the first housing 11, and a second air inlet 120 is formed on the second housing 12. The housing is symmetrically composed of the first housing 11 and the second housing 12, and the symmetrical dual air inlet design enables the compressor to achieve bidirectional air intake, resulting in a more uniform airflow distribution, reduced intake resistance, improved intake efficiency, and increased volumetric efficiency. Simultaneously, it balances the axial force during rotor operation and reduces bearing load.

[0024] The housing 1 is provided with a radial exhaust port 100, which is connected to the compression chamber. This design shortens the exhaust path, reduces exhaust resistance, and helps to improve the high-speed performance of the compressor, while making the exhaust direction easier to arrange in the pipeline.

[0025] Rotor assembly 2 is installed in the compression chamber. Rotor assembly 2 includes a male rotor assembly 21 and a female rotor assembly 22. The male rotor assembly 21 includes a right-handed male rotor 211 and a left-handed male rotor 212 arranged symmetrically. The female rotor assembly 22 includes a right-handed female rotor 222 and a left-handed female rotor 221 arranged symmetrically. The right-handed male rotor 211 and the left-handed female rotor 221 mesh to form a first compression pair. The left-handed male rotor 212 and the right-handed female rotor 222 mesh to form a second compression pair.

[0026] When the compressor is working, gas enters the compression chamber through the first inlet 110 and the second inlet 120 respectively. In the compression chamber in the first housing 11 region, the right-hand male rotor 211 meshes and rotates with the left-hand female rotor 221, compressing the gas from low pressure to high pressure. At the same time, in the compression chamber in the second housing 12 region, the left-hand male rotor 212 meshes and rotates with the right-hand female rotor 222, also compressing the gas from low pressure to high pressure. The compressed high-pressure gas is discharged through the radial exhaust port 100.

[0027] Thanks to its symmetrical structural design, the high-pressure zone at one end is eliminated, and the gas forces generated by the two compression pairs cancel each other out. This symmetrical design balances the axial forces on the male rotor assembly 21 and the female rotor assembly 22, reducing vibration and wear, significantly minimizing the impact of the axial forces generated by the gas on the bearings, extending bearing life, and improving the operational stability and reliability of the compressor. The simultaneous operation of the two compression pairs is equivalent to two compressors in parallel, almost doubling the discharge capacity while maintaining the same external dimensions, significantly improving space utilization.

[0028] In some embodiments of this application, such as Figure 3 , Figure 4 As shown, the compressor also includes an axial exhaust baffle 3, which is disposed in the middle of the housing 1. The axial exhaust baffle 3 divides the compression chamber into a first compression chamber 101 and a second compression chamber 102. The first compression pair is located in the first compression chamber 101, and the second compression pair is located in the second compression chamber 102. This separation allows the first compression pair and the second compression pair to work in their respective independent spaces, avoiding mutual interference of airflow. The two separated compression chambers can maintain a more uniform temperature distribution, avoiding heat accumulation in a single chamber, which is beneficial to improving the thermal efficiency and working stability of the compressor.

[0029] Meanwhile, the axial exhaust baffle 3 not only serves as a physical separator, but also optimizes the exhaust flow path. By rationally designing the shape and size of the baffle, the exhaust flow direction can be controlled, reducing eddies and pressure loss during the exhaust process and improving isentropic efficiency.

[0030] In addition, the axial exhaust baffle 3 is centrally located and serves as the core carrier for force balance. The gas reaction force in the first compression chamber 101 and the gas reaction force in the second compression chamber 102 are equal in magnitude and opposite in direction, and the axial resultant force is zero. This allows the axial forces of the compressor to be balanced during operation, which greatly reduces the impact of axial forces on the bearings and improves the operating stability and reliability of the compressor. This design can also increase the compression ratio, thereby obtaining a higher pressure ratio.

[0031] In some embodiments of this application, such as Figure 3 , Figure 11 , Figure 12 As shown, the male rotor assembly 21 includes a male spindle 213, a right-hand male rotor 211, and a left-hand male rotor 212. Optionally, the male spindle 213 is an integral structure, and a male spindle intermediate step 214 is provided in the axial middle part of the male spindle 213. The right-hand male rotor 211 and the left-hand male rotor 212 are relatively fixedly installed on both sides of the male spindle intermediate step 214 of the male spindle 213. This design integrates two symmetrical male rotors on a single spindle, ensuring the coaxiality and phase consistency of the two rotors and reducing assembly errors.

[0032] In some embodiments of this application, such as Figure 3 , Figure 11 , Figure 12 As shown, the female rotor assembly 22 includes a female spindle 223, a left-handed female rotor 221, and a right-handed female rotor 222. Optionally, the female spindle 223 is a one-piece structure, with a central step 224 at its axial midpoint. The left-handed female rotor 221 and the right-handed female rotor 222 are fixedly mounted on either side of the central step 224 of the female spindle 223. This design integrates two symmetrical female rotors onto a single spindle, ensuring coaxiality and phase consistency between the two rotors and reducing assembly errors.

[0033] Of course, it is understood that the right-handed male rotor 211 and the left-handed male rotor 212 can be press-fitted onto the male spindle 213, or can be fixed onto the male spindle 213 in other ways. The left-handed female rotor 221 and the right-handed female rotor 222 can be press-fitted onto the female spindle 223, or can be fixed onto the female spindle 223 in other ways. No limitation is made here.

[0034] The axial exhaust baffle 3 is installed at the intermediate steps 214 and 224 of the male main shaft 213 and the female main shaft 223, respectively. The axial exhaust baffle 3 is tolerantly fitted with the intermediate steps 214 and 224 of the male main shaft to control the axial exhaust clearance of the rotor. The tolerance fit between the axial exhaust baffle 3 and the steps can also ensure the sealing of the compressor at high temperatures and avoid thermal expansion jamming.

[0035] In addition, by installing axial exhaust baffles 3 at the intermediate steps 214 and 224 of the male spindle 213 and female spindle 223, additional intermediate support can be provided for the male rotor assembly 21 and female rotor assembly 22, effectively reducing the deflection deformation of the female spindle 223 and male spindle 213 and improving the dynamic running stability of the rotor. This design enhances the rigidity of the male rotor assembly 21 and the female rotor assembly 22, especially in the case of long span, it can reduce shaft deflection during high-speed rotation and prevent the rotor assembly 2 from contacting the housing 1.

[0036] In some embodiments of this application, such as Figure 3 As shown, the right-hand male rotor 211 and the left-hand male rotor 212 are equal pitch structures generated based on the same end face tooth profile. That is, the end face tooth profiles of the right-hand male rotor 211 and the left-hand male rotor 212 are exactly the same, only the helical directions are opposite. The two are symmetrical mirror structures. This design ensures the strict symmetry of the rotor geometric parameters, simplifies the processing technology, and improves the interchangeability of the rotor pairs.

[0037] In some embodiments of this application, such as Figure 3 As shown, the left-hand female rotor 221 and the right-hand female rotor 222 are equal-pitch structures generated based on the same end-face tooth profile. That is, the end-face tooth profiles of the left-hand female rotor 221 and the right-hand female rotor 222 are exactly the same, only the helical directions are opposite, and the two are symmetrical mirror structures. This design ensures strict symmetry of the rotor geometric parameters, simplifies the manufacturing process, and improves the interchangeability of the rotor pairs.

[0038] In some embodiments of this application, during assembly, the left-hand female rotor 221 and the right-hand female rotor 222 are respectively pressed onto the female spindle 223, and their rotation angle is limited during assembly, so that the short side of the female tooth of the right-hand female rotor 222 is aligned with the short side of the female tooth of the left-hand female rotor 221, and the long side of the female tooth of the right-hand female rotor 222 is aligned with the long side of the female tooth of the left-hand female rotor 221.

[0039] In some embodiments of this application, the right-hand male rotor 211 and the left-hand male rotor 212 are respectively press-fitted onto the male spindle 213, and their rotation angles are limited by assembly, so that the short side of the male teeth of the right-hand male rotor 211 is aligned with the short side of the male teeth of the left-hand male rotor 212, and the long side of the male teeth of the right-hand male rotor 211 is aligned with the long side of the male teeth of the left-hand male rotor 212.

[0040] The short side of the male tooth of the right-hand male rotor 211 is aligned with the short side of the male tooth of the left-hand male rotor 212, and the long side of the male tooth of the right-hand male rotor 211 is aligned with the long side of the male tooth of the left-hand male rotor 212; the short side of the female tooth of the left-hand female rotor 221 is aligned with the short side of the female tooth of the right-hand female rotor 222, and the long side of the female tooth of the left-hand female rotor 221 is aligned with the long side of the female tooth of the right-hand female rotor 222. This precise tooth alignment relationship ensures the mechanical symmetry of the two male rotors and the mechanical symmetry of the two female rotors, so that the radial forces acting on the male main shaft 213 and the female main shaft 223 are completely balanced.

[0041] The operating rotation directions of the female rotor assembly 22 and the male rotor assembly 21 are as follows: Figure 16 As shown, when the short side of the female rotor assembly 22 (left-handed female rotor 221 or right-handed female rotor 222) is about to encroach on the tooth inter-tooth area A1 of the male rotor assembly 21 (right-handed male rotor 211 or left-handed male rotor 212), that is, when the long side of the female rotor assembly 22 is tangent to the tooth tip circle of the male rotor assembly 21 at position A, the angle between this tangent point A and the line connecting the centers of the female rotor and the male rotor is the encroachment angle α of the male rotor assembly being invaded by the short side of the tooth profile of the female rotor assembly. The design of the encroachment angle α optimizes the geometric relationship of the rotors so that when the short side of the female rotor (left-handed female rotor 221 or right-handed female rotor 222) encroaches on the tooth inter-tooth area of ​​the male rotor (right-handed male rotor 211 or left-handed male rotor 212), a high-pressure volume is formed axially, which further improves the compression ratio and pressure.

[0042] In some embodiments of this application, such as Figures 5-8As shown, the first housing 11 side is provided with a first suction end seat 41, which includes a first suction shaft end groove 411, and the first suction shaft end groove 411 communicates with the first air inlet 110; the second housing 12 side is provided with a second suction end seat 42, which includes a second suction shaft end groove 421, and the second suction shaft end groove 421 communicates with the second air inlet 120. This double-sided arrangement of suction end seats matches the dual air inlet structure, ensuring that the two compression chambers can independently obtain sufficient air source and avoiding air intake competition. At the same time, the first suction shaft end groove 411 and the second suction shaft end groove 421 allow the gas to expand moderately before entering the compression chamber, reducing the gas temperature and the intake heating effect, thereby increasing the actual intake density and mass flow rate; the design of the first suction shaft end groove 411 and the second suction shaft end groove 421 can effectively increase the axial suction volume, and the symmetrical design of the double-sided grooves ensures the uniformity of air intake in the two compression chambers.

[0043] In some embodiments of this application, such as Figure 6 As shown, based on the rotor characteristics, the suction angle positions of the right-hand male rotor 211 and the left-hand female rotor 221 are calculated on the suction end face of the first suction end seat 41. The outline of the first suction shaft end groove 411 is formed by the tooth root circle of the left-hand female rotor 221, the tooth projection line of the left-hand female rotor 221 at the suction angle position, the tooth root circle of the right-hand male rotor 211, the tooth projection line of the right-hand male rotor 211 at the suction angle position (male axis suction closed line), and the outer circle of the suction volume. like Figure 8 As shown, based on the rotor characteristics, the suction angle positions of the left-hand male rotor 212 and the right-hand female rotor 222 are calculated on the suction end face of the second suction end seat 42. The outline of the second suction shaft end groove 421 is formed by the tooth root circle of the left-hand male rotor, the tooth projection line of the left-hand male rotor 212 at the suction angle position (the suction closure line of the female rotor), the tooth root circle of the right-hand female rotor, the tooth projection line of the right-hand female rotor 222 at the suction angle position, and the outer circle of the suction volume.

[0044] By precisely matching the shapes of the first intake shaft end groove 411 and the second intake shaft end groove 421 to the rotor geometry, perfect synchronization between the intake process and rotor movement is ensured, minimizing intake turbulence and pressure loss. Compared to traditional screw compressors, this intake shaft end groove, which precisely matches the rotor tooth profile, allows the compressor to maintain high volumetric efficiency even at high speeds.

[0045] In some embodiments of this application, such as Figure 9As shown, for the first housing 11, the intake angle of the right-hand male rotor 211 and the intake angle of the left-hand female rotor 221 are calculated. The inner circumferential surface of the first housing 11 is provided with a first helix 111 and a second helix 112. When the right-hand male rotor 211 is at the intake angle position, the first helix 111 coincides with the projection line of the tooth tip of the right-hand male rotor 211 on the first housing 11, that is, the helical projection line of the tooth tip of the right-hand male rotor 211. The first helix 111 is the radial intake closed line of the right-hand male rotor 211. When the left-hand female rotor 221 is at the intake angle position, the second helix 112 coincides with the projection line of the tooth tip of the left-hand female rotor 221 on the first housing 11, that is, the helical projection line of the tooth tip of the left-hand female rotor 221. The second helix 112 is the radial intake closed line of the left-hand female rotor 221. Similarly, such as Figure 10 As shown, for the second housing 12, the intake angle of the left-hand male rotor 212 and the intake angle of the right-hand female rotor 222 are calculated. The inner circumferential surface of the second housing 12 is provided with a third spiral line 121 and a fourth spiral line 122. When the left-hand male rotor 212 is at the intake angle position, the third spiral line 121 coincides with the projection line of the tooth tip of the left-hand male rotor 212 on the second housing 12, that is, the spiral projection line of the tooth tip of the left-hand male rotor 212. The third spiral line 121 is the radial intake closed line of the left-hand male rotor 212. When the right-hand female rotor 222 is at the intake angle position, the fourth spiral line 122 coincides with the projection line of the tooth tip of the right-hand female rotor 222 on the second housing, that is, the spiral projection line of the tooth tip of the right-hand female rotor 222. The fourth spiral line 122 is the radial intake closed line of the right-hand female rotor 222.

[0046] The first helix 111, the second helix 112, the third helix 121 and the fourth helix 122 coincide with the corresponding rotor tooth tip projection lines, which means that the shape of the housing precisely matches the movement trajectory of the rotor, minimizing the area of ​​the leakage channel while maintaining the necessary clearance.

[0047] In some embodiments of this application, a first bearing 51 is disposed on the first suction end seat 41, and a second bearing 52 is disposed on the second suction end seat 42. The rotor assembly 2 is mounted on the first suction end seat 41 via the first bearing 51 and on the second suction end seat 42 via the second bearing 52. Optionally, the first bearing 51 and the second bearing 52 may be angular contact ball bearings or cylindrical roller bearings, which can simultaneously withstand radial force and a certain axial force. For large or high-speed compressors, tilting pad bearings may also be used to provide better damping characteristics and stability.

[0048] In the above scheme, such as Figure 17 As shown, since both the female rotor assembly 22 and the male rotor assembly 21 adopt a symmetrical structure, and the high-pressure gas is located in the middle of the female rotor assembly 22 and the male rotor assembly 21, the axial gas forces F1 and F2 exerted by the high-pressure gas on the left and right parts of the female rotor assembly 22 and the male rotor assembly 21 are equal in magnitude and opposite in direction. Therefore, the resultant force of the axial gas reaction force is zero, achieving axial force balance between the female rotor assembly 22 and the male rotor assembly 21 during compressor operation. Traditional twin-screw compressors require thrust bearings (such as tapered roller bearings or angular contact bearings) to bear the tension and prevent rotor slippage due to the uneven axial force on the rotors. The compressor described in this application eliminates the need for thrust bearings.

[0049] In the above scheme, such as Figure 17 As shown, since both the female rotor assembly 22 and the male rotor assembly 21 adopt a symmetrical structure, the center of mass of the female rotor assembly 22 and the male rotor assembly 21 are on the same straight line as the radial high-pressure gas reaction force F3 of the exhaust port. The radial high-pressure gas reaction force F3 is opposite to the direction of the gravity G of the female rotor assembly 22 and the male rotor assembly 21, thereby reducing the radial loads M1 and M2 on the first bearing 51 and the second bearing 52 at both ends of the compressor.

[0050] In some embodiments of this application, such as Figure 1 , Figure 13 As shown, this application also provides a compressor, the compressor comprising: a housing 1, a compression cavity formed within the housing 1, a first air inlet 110 and a second air inlet 120 provided on the housing 1, and a radial exhaust port 100 provided at the bottom of the housing 1; a rotor assembly 2, installed in the compression cavity, the rotor assembly 2 comprising a male rotor assembly 21 and a female rotor assembly 22, the male rotor assembly 21 comprising a right-handed male rotor 211 and a left-handed male rotor 212 symmetrically arranged, the female rotor assembly 22 comprising a right-handed female rotor 222 and a left-handed female rotor 221 symmetrically arranged; and an axial exhaust baffle 3, disposed in the middle of the housing 1, dividing the compression cavity into a first compression cavity 101 and a second compression cavity 102, the axial exhaust baffle 3 comprising an axial exhaust port 31 communicating with the first compression cavity 101 and the second compression cavity 102.

[0051] In the above scheme, the radial and axial forces generated by the symmetrically designed female rotor assembly 22 and male rotor assembly 21 during rotation can cancel each other out, significantly reducing the load on the first bearing 51 and the second bearing 52, reducing compressor vibration and wear, and extending equipment life. Simultaneously, the first air inlet 110 and the second air inlet 120 supply gas to the first compression chamber 101 and the second compression chamber 102 respectively. The compressed gas first collects through the axial exhaust port 31 on the axial exhaust baffle 3, and then exits through the radial exhaust port 100 at the bottom of the housing 1. By setting the axial exhaust port 31, the gas from the two chambers converges, and in conjunction with the bottom radial exhaust port 100, gas stagnation within the housing is avoided, reducing exhaust resistance.

[0052] The exhaust angle is a critical point in the compression process. When the female rotor assembly 22 and the male rotor assembly 21 rotate to the exhaust angle position, the closed volume reaches its minimum, compression is complete, and it needs to connect with the axial exhaust port 31 for exhaust. If the profile of the axial exhaust port 31 is larger than the rotor projection, it will lead to premature exhaust (i.e., exhaust before the target pressure is reached). If the profile of the axial exhaust port 31 is smaller than the rotor projection, it will lead to delayed exhaust (i.e., the compressed volume has passed the minimum point but exhaust has not yet occurred, and the gas is backflushed).

[0053] In some embodiments of this application, such as Figure 13As shown, the axial exhaust baffle 3 adopts a mirror structure design, and the side of the axial exhaust baffle 3 near the first compression chamber 101 is completely symmetrical to the side of the axial exhaust baffle 3 near the second compression chamber 102. The axial exhaust port 31 is formed by a first side L1, a second side L2, a third side L3, a fourth side L4, and a fifth side L5. When both the male rotor assembly 21 and the female rotor assembly 22 are in the exhaust angle position, on the side of the axial exhaust baffle 3 near the first compression chamber 101, the first side L1 coincides with the tooth projection line of the right-hand male rotor assembly 211 on the axial exhaust baffle 3; the second side L2 coincides with the tooth root circle projection line of the right-hand male rotor 211 on the axial exhaust baffle 3; the third side L3 coincides with the projection line of the meshing line between the right-hand male rotor 211 and the left-hand female rotor 221 on the axial exhaust baffle 3; and the fourth side L4 coincides with the tooth root circle projection line of the left-hand female rotor 221 on the axial exhaust baffle 3. The projection lines coincide, and the fifth side L5 coincides with the tooth projection line of the left-hand female rotor 221 on the axial exhaust baffle 3; since the axial exhaust baffle is a mirror structure, the first side L1 also coincides with the tooth projection line of the left-hand male rotor 212 on the axial exhaust baffle 3, the second side L2 also coincides with the tooth root circle projection line of the left-hand male rotor 212 on the axial exhaust baffle 3, the third side L3 also coincides with the projection line of the meshing line of the left-hand male rotor 212 and the right-hand female rotor 222 on the axial exhaust baffle 3, the fourth side L4 also coincides with the tooth root circle projection line of the right-hand female rotor 222 on the axial exhaust baffle 3, and the fifth side L5 also coincides with the tooth projection line of the right-hand female rotor 222 on the axial exhaust baffle 3.

[0054] It is understood that when both the male rotor assembly 21 and the female rotor assembly 22 are in the exhaust angle position, the tooth projection line of the right-hand male rotor 211 on the axial exhaust baffle 3 is the right-hand male axial exhaust opening line, the tooth projection line of the left-hand male rotor 212 on the axial exhaust baffle 3 is the left-hand male axial exhaust opening line, the tooth projection line of the right-hand female rotor 222 on the axial exhaust baffle 3 is the right-hand female axial exhaust opening line, and the tooth projection line of the left-hand female rotor 221 on the axial exhaust baffle 3 is the left-hand female axial exhaust opening line. The calculation method for the exhaust angle of the male rotor assembly 21 and the female rotor assembly 22 is existing technology and will not be elaborated here.

[0055] When both the male rotor assembly 21 and the female rotor assembly 22 are in the exhaust angle position, the above scheme can ensure that the radial exhaust port 100 is fully open and has no overlap or gap with the contours of the female rotor assembly 22 and the male rotor assembly 21, avoiding premature / delayed exhaust, and preventing the high-pressure gas after compression from rushing back into the compression chamber, ensuring stable exhaust pressure; and the fitted contour allows the gas to flow smoothly from the closed volume into the exhaust port, reducing airflow separation and eddies, reducing exhaust resistance loss, thereby improving compression efficiency.

[0056] In some embodiments of this application, such as Figure 1 , Figure 14 As shown, the housing 1 includes a first housing 11 and a second housing 12 symmetrically arranged. A first compression chamber 101 is formed in the first housing 11, and a second compression chamber 102 is formed in the second housing 12. The axial exhaust baffle 3 is disposed between the first housing 11 and the second housing 12. The first air inlet 110 and the second air inlet 120 are symmetrically distributed on both sides of the upper part of the housing 1, and the radial exhaust port 100 is located at the middle position of the bottom of the housing. The first air inlet 110 is located on the first housing 11, and the second air inlet 120 is located on the second housing 12. The symmetrical arrangement of the first air inlet 110 and the second air inlet 120 ensures that the intake volume and intake velocity of the first compression chamber 101 and the second compression chamber 102 are completely consistent, avoiding the compression ratio difference caused by uneven intake and making the overall structure of the compressor more compact. Simultaneously, gas is supplied to the first compression chamber 101 and the second compression chamber 102 through the first air inlet 110 and the second air inlet 120 respectively. The compressed gas is discharged synchronously through the radial exhaust port 100 at the bottom of the housing, eliminating the single-end high-pressure area. During the operation of the compressor, the axial forces can be balanced, which greatly reduces the impact of the axial force generated by the gas on the bearing, extends the bearing life, and improves the operating stability and reliability of the compressor.

[0057] In some embodiments of this application, the axial exhaust port 31 is connected to the radial exhaust port 100, and the radial exhaust port 100 is located directly below the axial exhaust port 31. This arrangement allows the compressed high-pressure gas, after converging from the first compression chamber 101 and the second compression chamber 102 through the axial exhaust port 31, to flow directly into the radial exhaust port 100 for discharge, without needing to bend or split, thus minimizing friction loss and local losses in the gas flow.

[0058] In some embodiments of this application, such as Figure 14 , Figure 15As shown, the outline of the radial exhaust port 100 is formed by the sixth side L6, the seventh side L7, the eighth side L8, and the ninth side L9. The sixth side L6 is configured such that, at the exhaust angle position of the left-hand female rotor 221, the sixth side L6 coincides with the projection line of the tooth tip helix of the left-hand female rotor 221 onto the housing 1. The seventh side L7 is configured such that, at the exhaust angle position of the right-hand female rotor 222, the seventh side L7 coincides with the projection line of the tooth tip helix of the right-hand female rotor 222 onto the housing 1. The eighth side L8 is configured such that, at the exhaust angle position of the right-hand male rotor 211, the eighth side L8 coincides with the projection line of the tooth tip helix of the right-hand male rotor 211 onto the housing 1. The ninth side L9 is configured such that, at the exhaust angle position of the left-hand male rotor 212, the ninth side L9 coincides with the projection line of the tooth tip helix of the left-hand male rotor 212 onto the housing 1.

[0059] It is understood that when both the male rotor assembly 21 and the female rotor assembly 22 are in the exhaust angle position, the projection line of the tooth tip helix of the left-hand female rotor 221 on the housing 1 is the left-hand female radial exhaust opening line, the projection line of the tooth tip helix of the right-hand female rotor 222 on the housing 1 is the right-hand female radial exhaust opening line, the projection line of the tooth tip helix of the right-hand male rotor 211 on the housing 1 is the right-hand male radial exhaust opening line, and the projection line of the tooth tip helix of the left-hand male rotor 212 on the housing 1 is the left-hand male radial exhaust opening line.

[0060] In some embodiments of this application, when the gas is compressed to the target compression volume, the radial exhaust vent line and the axial exhaust vent line exhaust simultaneously, thereby improving the compression efficiency.

[0061] This application also provides a compression system including the aforementioned compressor. When the compressor is operating, gas enters the compression chamber through a first inlet 110 and a second inlet 120. In the compression chamber of the first housing 11 region, a right-handed male rotor 211 meshes and rotates with a left-handed female rotor 221, compressing the gas from low pressure to high pressure. Simultaneously, in the compression chamber of the second housing 12 region, a left-handed male rotor 212 meshes and rotates with a right-handed female rotor 222, also compressing the gas from low pressure to high pressure. The compressed high-pressure gas is discharged through a radial exhaust port 100. Due to the symmetrical structural design, the single-end high-pressure zone is eliminated, and the axial forces of the compressor can be balanced during operation, significantly reducing the impact of the axial force generated by the gas on the bearings, extending bearing life, and improving the operating stability and reliability of the compressor.

[0062] Those skilled in the art will understand that the above embodiments are specific implementations of this application, and in practical applications, various changes can be made in form and detail without departing from the spirit and scope of this application.

Claims

1. A compressor, characterized in that, include: The housing (1) has a compression cavity inside, and the housing (1) has a first air inlet (110) and a second air inlet (120) on it. The bottom of the housing (1) has a radial exhaust port (100). Rotor assembly (2) is installed in the compression chamber. The rotor assembly (2) includes a male rotor assembly (21) and a female rotor assembly (22). The male rotor assembly (21) includes a right-handed male rotor (211) and a left-handed male rotor (212) arranged symmetrically. The female rotor assembly (22) includes a right-handed female rotor (222) and a left-handed female rotor (221) arranged symmetrically. An axial exhaust baffle (3) is disposed in the middle of the housing (1) and divides the compression chamber into a first compression chamber (101) and a second compression chamber (102). The axial exhaust baffle (3) is provided with an axial exhaust port (31), which is connected to the first compression chamber (101) and the second compression chamber (102).

2. The compressor as described in claim 1, characterized in that, The male rotor assembly (21) includes a male spindle (213), and the right-handed male rotor (211) and the left-handed male rotor (212) are mounted on the male spindle (213); the female rotor assembly (22) includes a female spindle (223), and the left-handed female rotor (221) and the right-handed female rotor (222) are mounted on the female spindle (223); the axial exhaust baffle (3) is installed at the intermediate step of the male spindle (213) and the female spindle (223), and the axial exhaust port (31) is a through hole structure.

3. The compressor as described in claim 2, characterized in that, The right-hand male rotor (211) and the left-hand male rotor (212) are equal pitch structures generated based on the same end face tooth shape. The left-hand female rotor (221) and the right-hand female rotor (222) are equal pitch structures generated based on the same end face tooth shape. The right-hand male rotor (211) and the left-hand female rotor (221) mesh to form a first compression pair, located in the first compression chamber (101). The left-hand male rotor (212) and the right-hand female rotor (222) mesh to form a second compression pair, located in the second compression chamber (102).

4. The compressor as described in claim 2, characterized in that, The axial exhaust port (31) is formed by the first side (L1), the second side (L2), the third side (L3), the fourth side (L4), and the fifth side (L5), wherein, when both the male rotor assembly (21) and the female rotor assembly (22) are in the exhaust angle position, The first side (L1) coincides with the tooth projection line of the male rotor assembly (21) on the axial exhaust baffle (3), the second side (L2) coincides with the tooth root circle projection line of the male rotor assembly (21) on the axial exhaust baffle (3), the third side (L3) coincides with the projection line of the meshing line of the male rotor assembly (21) and the female rotor assembly (22) on the axial exhaust baffle (3), the fourth side (L4) coincides with the tooth root circle projection line of the female rotor assembly (22) on the axial exhaust baffle (3), and the fifth side (L5) coincides with the tooth projection line of the female rotor assembly (22) on the axial exhaust baffle (3).

5. The compressor as described in claim 4, characterized in that, The first air inlet (110) and the second air inlet (120) are symmetrically distributed on both sides of the upper part of the housing (1), and the radial exhaust port (100) is located in the middle of the bottom of the housing (1).

6. The compressor as described in claim 5, characterized in that, The axial exhaust port (31) is connected to the radial exhaust port (100), and the radial exhaust port (100) is located directly below the axial exhaust port (31).

7. The compressor as described in claim 5, characterized in that, The outline of the radial exhaust port (100) is formed by the sixth side (L6), the seventh side (L7), the eighth side (L8), and the ninth side (L9), wherein, At the exhaust angle position of the left-handed female rotor (221), the sixth side (L6) coincides with the projection line of the tooth tip helix of the left-handed female rotor (221) on the housing (1); At the exhaust angle position of the right-handed female rotor (222), the seventh side (L7) coincides with the projection line of the tooth tip helix of the right-handed female rotor (222) on the housing (1); At the exhaust angle position of the right-hand rotating male rotor (211), the eighth side (L8) coincides with the projection line of the tooth tip helix of the right-hand rotating male rotor (211) on the housing (1); At the exhaust angle position of the left-hand rotating male rotor (212), the ninth side (L9) coincides with the projection line of the tooth tip helix of the left-hand rotating male rotor (212) on the housing (1).

8. The compressor as claimed in claim 7, characterized in that, The housing (1) includes a first housing (11) and a second housing (12) arranged symmetrically. A first compression chamber (101) is formed in the first housing (11), and a second compression chamber (102) is formed in the second housing (12). The axial exhaust baffle (3) is disposed between the first housing (11) and the second housing (12). The first side (L1) and the third side (L3) are located on the first housing (11), and the second side (L2) and the fourth side (L4) are located on the second housing (12).

9. The compressor as described in claim 3, characterized in that, When the gas is compressed to the target compression volume, the axial exhaust port (31) and the radial exhaust port (100) exhaust gas simultaneously.

10. A compression system, characterized in that, Includes the compressor described in any one of claims 1-9.

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