Compressor and compression system

Abstract

The application belongs to the technical field of compressors and provides a compressor and a compression system.The compressor comprises a shell containing a compression cavity, the shell comprises a first shell provided with a first air inlet and a second shell provided with a second air inlet, the shell is provided with a radial exhaust port, the radial exhaust port is communicated with the compression cavity, a rotor assembly is installed in the compression cavity, 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, the right-handed male rotor and the left-handed female rotor are engaged to form a first compression pair, and the left-handed male rotor and the right-handed female rotor are engaged to form a second compression pair.The symmetric structure design eliminates a single high-pressure area, the gas forces generated by the two compression pairs are offset to each other, the vibration and wear are reduced, and the operation stability and reliability of the compressor are improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors, in particular to a compressor and a compression system. BACKGROUND

[0002] A double screw compressor is a positive displacement compressor, which realizes compression of medium through the rotary motion of a pair of intermeshing male and female rotors. In the compression process, the medium is compressed in the compression chamber, and the medium pressure gradually rises, generating radial and axial gas forces on the surface of the male and female rotors. The axial gas force is along the axis of the male and female rotors, mainly generated by the high-pressure gas at the discharge end, and the pressure is high near the discharge side and low at the suction side, forming a pressure gradient, so that the bearings at both ends of the male and female rotors are unevenly stressed. SUMMARY

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

[0004] One aspect of the present application provides a compressor, comprising: a housing, a compression chamber is formed in the housing, the housing comprises a first housing and a second housing arranged symmetrically, a first gas inlet is formed on the first housing, a second gas inlet is formed on the second housing, a radial discharge port is provided on the housing, and the radial discharge port communicates with the compression chamber;

[0005] A rotor assembly is installed in the compression chamber, 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 arranged symmetrically, the female rotor assembly comprises a right-handed female rotor and a left-handed female rotor arranged symmetrically, the right-handed male rotor and the left-handed female rotor mesh to form a first compression pair, and the left-handed male rotor and the right-handed female rotor mesh to form a second compression pair.

[0006] In some embodiments of the present application, a first suction end seat is provided on the first housing, the first suction end seat comprises a first suction shaft end groove, and the first suction shaft end groove communicates with the first gas inlet; a second suction end seat is provided on the second housing, the second suction end seat comprises a second suction shaft end groove, and the second suction shaft end groove communicates with the second gas inlet.

[0007] In some embodiments of the present application, the profile of the first suction shaft end recess is formed by a left-handed female rotor dedendum circle, a left-handed female rotor tooth profile projection at a suction angle position, a right-handed male rotor dedendum circle, a right-handed male rotor tooth profile projection at a suction angle position, and a suction volume outer circle; and the profile of the second suction shaft end recess is formed by a left-handed male rotor dedendum circle, a left-handed male rotor tooth profile projection at a suction angle position, a right-handed female rotor dedendum circle, a right-handed female rotor tooth profile projection at a suction angle position, and a suction volume outer circle.

[0008] In some embodiments of the present application, the compressor further comprises an axial exhaust baffle arranged at an intermediate position of the housing, the axial exhaust baffle separating the compression cavity into a first compression cavity and a second compression cavity, the first compression pair being arranged in the first compression cavity, and the second compression pair being arranged in the second compression cavity.

[0009] In some embodiments of the present application, the male rotor assembly further comprises a male main shaft, the right-handed male rotor and the left-handed male rotor being assembled on the male main shaft; the female rotor assembly further comprises a female main shaft, the left-handed female rotor and the right-handed female rotor being assembled on the female main shaft; and the axial exhaust baffle is installed at an intermediate step of the male main shaft and the female main shaft.

[0010] In some embodiments of the present application, the right-handed male rotor and the left-handed male rotor are equal-pitch structures generated based on the same end face tooth profile, and the left-handed female rotor and the right-handed female rotor are equal-pitch structures generated based on the same end face tooth profile.

[0011] In some embodiments of the present application, the male tooth short side of the right-handed male rotor is aligned with the male tooth short side of the left-handed male rotor, and the male tooth long side of the right-handed male rotor is aligned with the male tooth long side of the left-handed male rotor; and the female tooth short side of the left-handed female rotor is aligned with the female tooth short side of the right-handed female rotor, and the female tooth long side of the left-handed female rotor is aligned with the female tooth long side of the right-handed female rotor.

[0012] In some embodiments of the present application, the inner circumferential surface of the first shell is provided with a first spiral line and a second spiral line, when the right-handed male rotor is at the right-handed male rotor suction angle position, the first spiral line coincides with the projection line of the tooth top of the right-handed male rotor on the first shell; when the left-handed female rotor is at the left-handed female rotor suction angle position, the second spiral line coincides with the projection line of the tooth top of the left-handed female rotor on the first shell; the inner circumferential surface of the second shell is provided with a third spiral line and a fourth spiral line, when the left-handed male rotor is at the left-handed male rotor suction angle position, the third spiral line coincides with the projection line of the tooth top of the left-handed male rotor on the second shell; when the right-handed female rotor is at the right-handed female rotor suction angle position, the fourth spiral line coincides with the projection line of the tooth top of the right-handed female rotor on the fourth shell.

[0013] In some embodiments of the present application, a first bearing is arranged on the first suction end seat, and a second bearing is arranged on the second suction end seat, and the rotor assembly is mounted on the first suction end seat through the first bearing and mounted on the second suction end seat through the second bearing.

[0014] The second aspect of the present application also provides a compression system comprising the foregoing compressor.

[0015] The present application adopts a symmetrical structure design, eliminates a single-end high-pressure area, and the gas forces generated by the two compression pairs cancel each other out. This symmetrical design balances the axial forces of the male rotor assembly and the female rotor assembly, reduces vibration and wear, greatly reduces the influence of the axial force generated by the gas on the bearing, prolongs the service life of the bearing, and improves the operation stability and reliability of the compressor. Two compression pairs work at the same time, which is equivalent to two parallel compressors, almost doubles the exhaust volume, while maintaining the same external dimensions, significantly improving the space utilization. BRIEF DESCRIPTION OF DRAWINGS

[0016] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the following will briefly introduce the drawings needed to be used in the embodiments of the present application or the prior art description. Obviously, the drawings described below are only some embodiments of the present application, and other drawings can also be obtained by those skilled in the art without creative labor on the basis of these drawings.

[0017] Figure 1 is a structural schematic diagram of the first view angle of the compressor shown in some embodiments of the present application;

[0018] Figure 2 is Figure 1 a structural schematic diagram of the second view angle of the compressor shown in some embodiments of the present application;

[0019] Figure 3 is Figure 1 the structure diagram of the compressor removing the shell mouth;

[0020] Figure 4 is Figure 1 the structure diagram of the compressor part shell and axial exhaust baffle;

[0021] Figure 5 is the structure diagram of the first suction end seat in some embodiments of the present application;

[0022] Figure 6 is Figure 5 the suction end face of the first suction end seat in some embodiments of the present application;

[0023] Figure 7 is the structure diagram of the second suction end seat in some embodiments of the present application;

[0024] Figure 8 is Figure 7 the suction end face of the second suction end seat in some embodiments of the present application;

[0025] Figure 9 is the structure diagram of the first compression cavity in some embodiments of the present application;

[0026] Figure 10 is the structure diagram of the second compression cavity in some embodiments of the present application;

[0027] Figure 11 is the structure diagram of the compressor removing part of the shell in some embodiments of the present application;

[0028] Figure 12 is the structure diagram of the male spindle and the female spindle in some embodiments of the present application;

[0029] Figure 13 is the structure diagram of the axial suction baffle in some embodiments of the present application;

[0030] Figure 14 is the bottom view of the part structure of the compressor in some embodiments of the present application;

[0031] Figure 15 is the structure diagram of the radial exhaust port in some embodiments of the present application;

[0032] Figure 16 is the structure diagram of the male rotor assembly and the female rotor assembly meshing in some embodiments of the present application;

[0033] Figure 17 is the force diagram of the compressor in some embodiments of the present application;

[0034] Reference signs:

[0035] 1 - housing, 11 - first housing, 12 - second housing, 110 - first air inlet, 120 - second air inlet, 100 - radial exhaust port, 101 - first compression chamber, 102 - second compression chamber; 111 - first spiral line, 112 - second spiral line, 121 - third spiral line, 122 - fourth spiral line;

[0036] 2 - rotor assembly, 21 - male rotor assembly, 22 - female rotor assembly, 211 - right-handed male rotor, 212 - left-handed male rotor, 221 - left-handed female rotor, 222 - right-handed female rotor, 213 - male main shaft, 223 - female main shaft, 214 - male main shaft middle step, 224 - female main shaft middle step;

[0037] 3 - axial exhaust baffle; 31 - axial exhaust port;

[0038] 41 - first suction end seat, 411 - first suction shaft end groove, 42 - second suction end seat, 421 - second suction shaft end groove;

[0039] 51 - first bearing, 52 - second bearing;

[0040] 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 DESCRIPTION

[0041] The technical solutions in the embodiments of the present application will be described clearly and completely below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0042] The terms "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, unless otherwise specified, the meaning of "multiple" is two or more.

[0043] In the description of the present application, specific features, structures, materials or characteristics can be combined in any one or more embodiments or examples in a suitable manner.

[0044] 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.

[0045] 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.

[0046] 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.

[0047] 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.

[0048] 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.

[0049] A rotor assembly 2 is installed in the compression cavity, 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, the right-handed male rotor 211 and the left-handed female rotor 221 engage to form a first compression pair, and the left-handed male rotor 212 and the right-handed female rotor 222 engage to form a second compression pair.

[0050] When the compressor is working, the gas enters the compression cavity through the first gas inlet 110 and the second gas inlet 120, in the compression cavity in the first shell 11 region, the right-handed male rotor 211 and the left-handed female rotor 221 engage to rotate and compress the gas from low pressure to high pressure, at the same time, in the compression cavity in the second shell 12 region, the left-handed male rotor 212 and the right-handed female rotor 222 engage to rotate and also compress the gas from low pressure to high pressure, and the compressed high-pressure gas is discharged through the radial gas outlet 100.

[0051] Due to the adoption of the symmetric structure design, the single-end high-pressure area is eliminated, the gas forces generated by the two compression pairs are offset, the symmetric design balances the axial forces of the male rotor assembly 21 and the female rotor assembly 22, reduces the vibration and wear, greatly reduces the influence of the axial force generated by the gas on the bearing, prolongs the service life of the bearing, and improves the operation stability and reliability of the compressor. The two compression pairs work simultaneously, which is equivalent to two parallel compressors, so that the exhaust volume is almost doubled, while the same external dimensions are maintained, and the space utilization is significantly improved.

[0052] In some embodiments of the present application, as shown in Figure 3 , Figure 4 The compressor further includes an axial gas discharge baffle 3, the axial gas discharge baffle 3 is arranged at the middle position of the shell 1, the axial gas discharge baffle 3 divides the compression cavity into a first compression cavity 101 and a second compression cavity 102, the first compression pair is located in the first compression cavity 101, and the second compression pair is located in the second compression cavity 102, and the division enables the first compression pair and the second compression pair to work in independent spaces, avoiding interference between the gas flows; the two compression cavities after the division can maintain a more uniform temperature distribution, avoiding heat accumulation in a single cavity, which is conducive to improving the thermal efficiency and working stability of the compressor.

[0053] At the same time, the axial gas discharge baffle 3 not only plays a physical separation role, but also optimizes the gas discharge flow path, by reasonably designing the shape and size of the baffle, the gas flow direction can be controlled, the vortex and pressure loss in the gas discharge process can be reduced, and the isentropic efficiency can be improved.

[0054] In addition, the axial exhaust baffle 3 is arranged in the middle as a force balance core carrier, the gas reaction force in the first compression cavity 101 and the gas reaction force in the second compression cavity 102 are equal and opposite, the axial resultant force is zero, so that the axial forces of the compressor can be balanced in the working process, the influence of the axial force on the bearing is greatly reduced, the operation stability and reliability of the compressor are improved, and the compression ratio is also improved, so that a higher pressure ratio is obtained.

[0055] In some embodiments of the present application, as shown in Figure 3 、 Figure 11 、 Figure 12 The male rotor assembly 21 includes a male main shaft 213, a right-handed male rotor 211 and a left-handed male rotor 212. Optionally, the male main shaft 213 is a one-piece structure, the axial middle part of the male main shaft 213 is provided with a male main shaft middle step 214, and the right-handed male rotor 211 and the left-handed male rotor 212 are fixedly installed on both sides of the male main shaft middle step 214 of the male main shaft 213. This design integrates two symmetrical male rotors on one main shaft, ensures the coaxiality and phase consistency of the two rotors, and reduces the assembly error.

[0056] In some embodiments of the present application, as shown in Figure 3 、 Figure 11 、 Figure 12 The female rotor assembly 22 includes a female main shaft 223, a left-handed female rotor 221 and a right-handed female rotor 222. Optionally, the female main shaft 223 is a one-piece structure, the axial middle part of the female main shaft 223 is provided with a female main shaft middle step 224, and the left-handed female rotor 221 and the right-handed female rotor 222 are fixedly installed on both sides of the female main shaft middle step 224 of the female main shaft 223. This design integrates two symmetrical female rotors on one main shaft, ensures the coaxiality and phase consistency of the two rotors, and reduces the assembly error.

[0057] Of course, it can be understood that the right-handed male rotor 211 and the left-handed male rotor 212 can be press-fitted on the male main shaft 213, or can be fixed on the male main shaft 213 by other means, and the left-handed female rotor 221 and the right-handed female rotor 222 can be press-fitted on the female main shaft 223, or can be fixed on the female main shaft 223 by other means, which are not limited herein.

[0058] The axial exhaust baffle 3 is installed at the male main shaft intermediate step 214 and the female main shaft intermediate step 224 of the male main shaft 213 and the female main shaft 223, and is in tolerance fit with the male main shaft intermediate step 214 and the female main shaft intermediate step 224 to control the rotor axial exhaust gap, and the tolerance fit of the axial exhaust baffle 3 with the steps can also ensure the sealing of the compressor at high temperature and avoid thermal expansion jamming.

[0059] In addition, by installing the axial exhaust baffle 3 at the male main shaft intermediate step 214 and the female main shaft intermediate step 224 of the male main shaft 213 and the female main shaft 223, additional intermediate support can be provided for the male rotor assembly 21 and the female rotor assembly 22, effectively reducing the deflection deformation of the female main shaft 223 and the male main shaft 213, and improving the dynamic operation stability of the rotor, which enhances the rigidity of the male rotor assembly 21 and the female rotor assembly 22, especially in the case of long span, which can reduce the shaft deflection during high-speed rotation and avoid the contact between the rotor assembly 2 and the shell 1.

[0060] In some embodiments of the present application, as shown in Figure 3 The right-handed male rotor 211 and the left-handed 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-handed male rotor 211 and the left-handed male rotor 212 are completely the same, only the spiral directions are opposite, and the two are symmetrical mirror image structures, which ensures the strict symmetry of the rotor geometric parameters, simplifies the machining process, and improves the interchangeability of the rotor pair.

[0061] In some embodiments of the present application, as shown in Figure 3 The left-handed female rotor 221 and the right-handed 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-handed female rotor 221 and the right-handed female rotor 222 are completely the same, only the spiral directions are opposite, and the two are symmetrical mirror image structures. This design ensures the strict symmetry of the rotor geometric parameters, simplifies the machining process, and improves the interchangeability of the rotor pair.

[0062] In some embodiments of the present application, during assembly, the left-handed female rotor 221 and the right-handed female rotor 222 are respectively press-fitted on the female main shaft 223, and the rotation angle is limited and assembled, so that the female tooth short side of the right-handed female rotor 222 is aligned with the female tooth short side of the left-handed female rotor 221, and the female tooth long side of the right-handed female rotor 222 is aligned with the female tooth long side of the left-handed female rotor 221.

[0063] In some embodiments of the present application, the right-handed male rotor 211 and the left-handed male rotor 212 are respectively press-fitted on the male main shaft 213, and the rotation angle is limited and assembled, so that the short side of the male teeth of the right-handed male rotor 211 is aligned with the short side of the male teeth of the left-handed male rotor 212, and the long side of the male teeth of the right-handed male rotor 211 is aligned with the long side of the male teeth of the left-handed male rotor 212.

[0064] The short side of the male teeth of the right-handed male rotor 211 is aligned with the short side of the male teeth of the left-handed male rotor 212, and the long side of the male teeth of the right-handed male rotor 211 is aligned with the long side of the male teeth of the left-handed male rotor 212; the short side of the female teeth of the left-handed female rotor 221 is aligned with the short side of the female teeth of the right-handed female rotor 222, and the long side of the female teeth of the left-handed female rotor 221 is aligned with the long side of the female teeth of the right-handed 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 force acting on the male main shaft 213 and the female main shaft 223 is completely balanced.

[0065] The running rotation direction of the female rotor assembly 22 and the male rotor assembly 21 is as shown in Figure 16 When the short side of the female rotor assembly 22 (the left-handed female rotor 221 or the right-handed female rotor 222) is about to invade the tooth space area A1 of the male rotor assembly 21 (the right-handed male rotor 211 or the left-handed male rotor 212), that is, the tangent position A of the long side of the female rotor assembly 22 and the addendum circle of the male rotor assembly 21, the included angle between the connecting line of the tangent point A and the center of the female rotor and the male rotor is the invasion angle a of the male rotor assembly invaded by the tooth shape short side of the female rotor assembly. The design of the invasion angle a optimizes the geometric relationship of the rotor, so that the short side of the female rotor (the left-handed female rotor 221 or the right-handed female rotor 222) forms a high-pressure volume in the axial direction when invading the tooth space area of the male rotor (the right-handed male rotor 211 or the left-handed male rotor 212), further improving the compression ratio and the pressure.

[0066] In some embodiments of the present application, as Figures 5-8As shown, the first shell 11 side is provided with a first suction end seat 41, the first suction end seat 41 includes a first suction shaft end groove 411, the first suction shaft end groove 411 is communicated with the first gas inlet 110; the second shell 12 side is provided with a second suction end seat 42, the second suction end seat 42 includes a second suction shaft end groove 421, the second suction shaft end groove 421 is communicated with the second gas inlet 120. This double-sided arrangement of the suction end seat matches the double gas inlet structure, ensuring that the two compression cavities can independently obtain sufficient gas source, avoiding the phenomenon of gas 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 cavity, reduce the gas temperature, reduce the gas heating effect, thereby improving the actual gas density and mass flow; the design of the first suction shaft end groove 411 and the second suction shaft end groove 421 can effectively improve the axial suction volume, and the symmetrical design of the double-sided groove ensures the uniformity of the gas inlet of the two compression cavities.

[0067] In some embodiments of the present application, as shown in Figure 6 As shown, according to the rotor characteristics, the suction angle positions of the right-handed male rotor 211 and the left-handed female rotor 221 are calculated at the suction end face of the first suction end seat 41 respectively; the profile of the first suction shaft end groove 411 is jointly formed by the dedendum circle of the left-handed female rotor 221, the tooth type projection line of the left-handed female rotor 221 at the suction angle position, the dedendum circle of the right-handed male rotor 211, the tooth type projection line of the right-handed male rotor 211 at the suction angle position (male axial suction closed line), and the suction volume outer circle.

[0068] As shown in Figure 8 As shown, according to the rotor characteristics, the suction angle positions of the left-handed male rotor 212 and the right-handed female rotor 222 are calculated at the suction end face of the second suction end seat 42 respectively, and the profile of the second suction shaft end groove 421 is jointly formed by the dedendum circle of the left-handed male rotor 212, the tooth type projection line of the left-handed male rotor 212 at the suction angle position (female axial suction closed line), the dedendum circle of the right-handed female rotor 222, the tooth type projection line of the right-handed female rotor 222 at the suction angle position, and the suction volume outer circle.

[0069] By accurately matching the shape of the first suction shaft end groove 411 and the second suction shaft end groove 421 with the profile design of the rotor geometry, it is ensured that the gas inlet process is perfectly synchronized with the rotor motion, and the gas inlet vortex and pressure loss are minimized. Compared with the traditional screw compressor, this suction shaft end groove accurately matched with the rotor tooth type can still maintain a high volumetric efficiency when the compressor is running at high speed.

[0070] In some embodiments of the present application, as shown in 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.

[0071] 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.

[0072] 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.

[0073] 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.

[0074] 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.

[0075] 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.

[0076] 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.

[0077] In the above scheme, the radial force and axial force generated by the symmetrically designed female rotor assembly 22 and male rotor assembly 21 during rotation can be offset, which greatly reduces the load of the first bearing 51 and the second bearing 52, reduces the vibration and wear of the compressor, and prolongs the service life of the equipment; at the same time, the first gas inlet 110 and the second gas inlet 120 supply gas to the first compression chamber 101 and the second compression chamber 102 respectively, and the compressed gas is first collected through the axial exhaust port 31 on the axial exhaust baffle 3, and then discharged through the radial exhaust port 100 at the bottom of the shell 1. By setting the axial exhaust port 31, the gas in the two chambers is merged, and the bottom radial exhaust port 100 is matched to avoid gas retention in the shell and reduce the exhaust resistance.

[0078] The exhaust angle is a key node of 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 the minimum, the compression is completed, and the exhaust needs to be communicated with the axial exhaust port 31. If the profile of the axial exhaust port 31 is greater than the rotor projection, it will cause early 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 cause delayed exhaust (i.e., the compression volume has passed the minimum point but still not exhaust, and the gas is backflushed).

[0079] In some embodiments of the present application, as Figure 13As shown, the axial exhaust baffle 3 adopts a mirror image structure design, and the side of the axial exhaust baffle 3 close to the first compression cavity 101 is completely symmetrical with the side of the axial exhaust baffle 3 close to the second compression cavity 102. The axial exhaust port 31 is surrounded by the first edge L1, the second edge L2, the third edge L3, the fourth edge L4 and the fifth edge L5. When the male rotor assembly 21 and the female rotor assembly 22 are both at the exhaust angle position, on the side of the axial exhaust baffle 3 close to the first compression cavity 101, the first edge L1 coincides with the tooth profile projection line of the right-handed male rotor 211 on the axial exhaust baffle 3, the second edge L2 coincides with the dedendum circle projection line of the right-handed male rotor 211 on the axial exhaust baffle 3, the third edge L3 coincides with the projection line of the meshing line of the right-handed male rotor 211 and the left-handed female rotor 221 on the axial exhaust baffle 3, the fourth edge L4 coincides with the dedendum circle projection line of the left-handed female rotor 221 on the axial exhaust baffle 3, and the fifth edge L5 coincides with the tooth profile projection line of the left-handed female rotor 221 on the axial exhaust baffle 3. Since the axial exhaust baffle is a mirror image structure, the first edge L1 also coincides with the tooth profile projection line of the left-handed male rotor 212 on the axial exhaust baffle 3, the second edge L2 also coincides with the dedendum circle projection line of the left-handed male rotor 212 on the axial exhaust baffle 3, the third edge L3 also coincides with the projection line of the meshing line of the left-handed male rotor 212 and the right-handed female rotor 222 on the axial exhaust baffle 3, the fourth edge L4 also coincides with the dedendum circle projection line of the right-handed female rotor 222 on the axial exhaust baffle 3, and the fifth edge L5 also coincides with the tooth profile projection line of the right-handed female rotor 222 on the axial exhaust baffle 3.

[0080] It can be understood that when the male rotor assembly 21 and the female rotor assembly 22 are both at the exhaust angle position, the tooth profile projection line of the right-handed male rotor 211 on the axial exhaust baffle 3 is the right-handed male axial exhaust open line, the tooth profile projection line of the left-handed male rotor 212 on the axial exhaust baffle 3 is the left-handed male axial exhaust open line, the tooth profile projection line of the right-handed female rotor 222 on the axial exhaust baffle 3 is the right-handed female axial exhaust open line, and the tooth profile projection line of the left-handed female rotor 221 on the axial exhaust baffle 3 is the left-handed female axial exhaust open line. The calculation method of the exhaust angle of the male rotor assembly 21 and the female rotor assembly 22 is a prior art, which is not described here.

[0081] When the male rotor assembly 21 and the female rotor assembly 22 are both in the exhaust angle position, the above scheme can ensure that the radial exhaust port 100 is fully open and has no overlap and no gap with the profile of the female rotor assembly 22 and the male rotor assembly 21, avoiding early / late exhaust, and the high-pressure gas after compression will not backflow to the compression chamber, ensuring stable exhaust pressure; and the conformal profile enables the gas to flow smoothly from the closed volume into the exhaust port, reducing airflow separation and vortex, reducing exhaust resistance loss, thereby improving compression efficiency.

[0082] In some embodiments of the present application, as shown in Figure 1 、 Figure 14 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 arranged between the first housing 11 and the second housing 12. The first intake port 110 and the second intake port 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 intake port 110 is located on the first housing 11, and the second intake port 120 is located on the second housing 12. The first intake port 110 and the second intake port 120 are symmetrically arranged, so that the intake amount and intake speed of the first compression chamber 101 and the second compression chamber 102 are completely consistent, avoiding the difference in compression ratio caused by uneven intake, and making the overall structure of the compressor more compact. At the same time, the first intake port 110 and the second intake port 120 supply gas to the first compression chamber 101 and the second compression chamber 102 respectively, and the compressed gas is discharged synchronously through the radial exhaust port 100 at the bottom of the housing, eliminating the single high-pressure area. The axial force of the compressor can be balanced during operation, greatly reducing the influence of the axial force of the gas on the bearing, prolonging the service life of the bearing, and improving the operation stability and reliability of the compressor.

[0083] In some embodiments of the present application, the axial exhaust port 31 communicates with the radial exhaust port 100, and the radial exhaust port 100 is located directly below the axial exhaust port 31. In this way, the high-pressure gas after compression can flow directly into the radial exhaust port 100 after converging through the axial exhaust port 31 from the first compression chamber 101 and the second compression chamber 102, without turning or branching, so that the flow resistance loss of the gas flow is minimized.

[0084] In some embodiments of the present application, as shown in Figure 14 、 Figure 15As shown, the profile of the radial exhaust port 100 is formed by a sixth side L6, a seventh side L7, an eighth side L8 and a ninth side L9, wherein the sixth side L6 is configured to coincide with the projection line of the addendum helix of the left-handed female rotor 221 on the housing 1 at the left-handed female rotor 221 exhaust angle position; the seventh side L7 is configured to coincide with the projection line of the addendum helix of the right-handed female rotor 222 on the housing 1 at the right-handed female rotor 222 exhaust angle position; the eighth side L8 is configured to coincide with the projection line of the addendum helix of the right-handed male rotor 211 on the housing 1 at the right-handed male rotor 211 exhaust angle position; and the ninth side L9 is configured to coincide with the projection line of the addendum helix of the left-handed male rotor 212 on the housing 1 at the left-handed male rotor 212 exhaust angle position.

[0085] It can be understood that when the male rotor assembly 21 and the female rotor assembly 22 are both at the exhaust angle position, the projection line of the addendum helix of the left-handed female rotor 221 on the housing 1 is the left-handed female radial exhaust open line, the projection line of the addendum helix of the right-handed female rotor 222 on the housing 1 is the right-handed female radial exhaust open line, the projection line of the addendum helix of the right-handed male rotor 211 on the housing 1 is the right-handed male radial exhaust open line, and the projection line of the addendum helix of the left-handed male rotor 212 on the housing 1 is the left-handed male radial exhaust open line.

[0086] In some embodiments of the present application, the radial exhaust open line and the axial exhaust open line simultaneously exhaust when the gas is compressed to the target compression volume, thereby improving the compression efficiency.

[0087] The present application also provides a compression system comprising the compressor as described above. When the compressor is working, the gas enters the compression chamber through the first gas inlet 110 and the second gas inlet 120. In the compression chamber in the first housing 11 region, the right-handed male rotor 211 and the left-handed female rotor 221 mesh and rotate to compress the gas from low pressure to high pressure. Meanwhile, in the compression chamber in the second housing 12 region, the left-handed male rotor 212 and the right-handed female rotor 222 mesh and rotate to also compress the gas from low pressure to high pressure. The compressed high-pressure gas is discharged through the radial exhaust port 100. Due to the adoption of the symmetrical structure design, the single-end high-pressure area is eliminated, the axial force during the working process of the compressor can be balanced, the influence of the axial force generated by the gas on the bearing is greatly reduced, the bearing life is prolonged, and the operation stability and reliability of the compressor are improved.

[0088] Those skilled in the art can understand that the above-mentioned embodiments are specific embodiments for realizing the present application, and in actual applications, various changes can be made in form and details without departing from the spirit and scope of the present application.

Claims

1. A compressor characterized by, The compressor comprises: a shell (1) in which a compression cavity is formed, and which comprises a first shell (11) and a second shell (12) symmetrically arranged, a first air inlet (110) is formed on the first shell (11), and a second air inlet (120) is formed on the second shell (12), and a radial exhaust port (100) in communication with the compression cavity is arranged on the shell (1); a rotor assembly (2) installed in the compression cavity, and comprising a male rotor assembly (21) and a female rotor assembly (22), the male rotor assembly (21) comprises a right-handed male rotor (211) and a left-handed male rotor (212) symmetrically arranged, and the female rotor assembly (22) comprises a left-handed female rotor (221) and a right-handed female rotor (222) symmetrically arranged, the right-handed male rotor (211) and the left-handed female rotor (221) form a first compression pair, and the left-handed male rotor (212) and the right-handed female rotor (222) form a second compression pair; a first suction end seat (41) is arranged on the first shell (11) of the compressor, and the first suction end seat (41) comprises a first suction shaft end groove (411) in communication with the first air inlet (110); a second suction end seat (42) is arranged on the second shell (12) of the compressor, and the second suction end seat (42) comprises a second suction shaft end groove (421) in communication with the second air inlet (120); the profile of the first suction shaft end groove (411) is jointly formed by a left-handed female rotor dedendum circle, a tooth profile projection line of the left-handed female rotor at a suction angle position, a right-handed male rotor dedendum circle, a tooth profile projection line of the right-handed male rotor at a suction angle position, and an outer circle of a suction volume; the profile of the second suction shaft end groove (421) is jointly formed by a left-handed male rotor dedendum circle, a tooth profile projection line of the left-handed male rotor at a suction angle position, a right-handed female rotor dedendum circle, a tooth profile projection line of the right-handed female rotor at a suction angle position, and an outer circle of a suction volume.

2. The compressor of claim 1, wherein, An axial exhaust baffle (3) is further arranged at a middle position of the shell (1), the axial exhaust baffle (3) divides the compression cavity into a first compression cavity (101) and a second compression cavity (102), the first compression pair is located in the first compression cavity (101), and the second compression pair is located in the second compression cavity (102).

3. The compressor of claim 2, wherein, The male rotor assembly (21) further comprises a male main shaft (213), the right-handed male rotor (211) and the left-handed male rotor (212) are assembled on the male main shaft (213); the female rotor assembly (22) further comprises a female main shaft (223), the left-handed female rotor (221) and the right-handed female rotor (222) are assembled on the female main shaft (223); and the axial exhaust baffle (3) is installed at a middle step of the male main shaft (213) and the female main shaft (223).

4. The compressor of claim 3, wherein, The right-handed male rotor (211) and the left-handed male rotor (212) are equal-pitch structures generated based on the same end face tooth profile, and the left-handed female rotor and the right-handed female rotor are equal-pitch structures generated based on the same end face tooth profile.

5. The compressor of claim 4, wherein, The short edge of the male teeth of the right-handed male rotor (211) is aligned with the short edge of the male teeth of the left-handed male rotor (212), and the long edge of the male teeth of the right-handed male rotor (211) is aligned with the long edge of the male teeth of the left-handed male rotor (212); the short edge of the female teeth of the left-handed female rotor is aligned with the short edge of the female teeth of the right-handed female rotor, and the long edge of the female teeth of the left-handed female rotor is aligned with the long edge of the female teeth of the right-handed female rotor.

6. The compressor of claim 1, wherein, The inner circumferential surface of the first housing (11) is provided with a first spiral line (111) and a second spiral line (112), when the right-handed male rotor (211) is at the right-handed male rotor suction angle position, the first spiral line (111) coincides with the projection line of the tooth top of the right-handed male rotor (211) on the first housing (11); when the left-handed female rotor (221) is at the left-handed female rotor suction angle position, the second spiral line (112) coincides with the projection line of the tooth top of the left-handed female rotor (221) on the first housing (11); 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-handed male rotor (212) is at the left-handed male rotor suction angle position, the third spiral line (121) coincides with the projection line of the tooth top of the left-handed male rotor (212) on the second housing (12); when the right-handed female rotor (222) is at the right-handed female rotor suction angle position, the fourth spiral line (122) coincides with the projection line of the tooth top of the right-handed female rotor (222) on the second housing (12).

7. The compressor of claim 1, wherein, Further comprising a first bearing (51) arranged on the first suction end seat (41), and a second bearing (52) arranged on the second suction end seat (42), the rotor assembly (2) is mounted on the first suction end seat (41) through the first bearing (51), and is mounted on the second suction end seat (42) through the second bearing (52).

8. A compression system characterized by, The compressor comprises the compressor according to any one of claims 1-7. The compressor comprises the compressor according to any one of claims 1-7.

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