A claw type compressor

Abstract

The invention discloses a claw type compressor, which is composed of a small claw rotor (1), a large claw rotor (2), a cylinder (3), a rear end cover (4), and a front end cover (5). The end face profile of the small claw rotor (1) is composed of four curves, which are in sequence in the counterclockwise direction: a first claw top arc ab, a speed-changing spiral bc, a first claw bottom arc cd, a first cycloid da, and the intersection of the first claw top arc ab and the first cycloid da is a first point a; the end face profile of the large claw rotor (2) is composed of four curves, which are in sequence in the clockwise direction: a second claw bottom arc AB, a conjugate curve BC of the speed-changing spiral, a second claw top arc CD, a second cycloid DA, and the intersection of the second claw top arc CD and the second cycloid DA is a first point D. The claw type compressor has the advantages of diverse working processes, simple design steps, and easy processing, and enriches the profile types of claw type compressor rotors.

Description

Technical Field

[0001] The invention belongs to the technical field of compressor engineering, and in particular relates to a claw type compressor. Background Art

[0002] The claw compressor relies on the synchronous and counter-rotating double-rotational motion of gears to drive a pair of meshing rotors to rotate and mesh, realize the periodic change of the working chamber volume, complete the gas intake, compression and discharge process, and complete the entire working cycle; therefore, the rotor profile design is crucial and has a great impact on the working performance of the claw compressor.

[0003] As energy recovery and utilization systems are gaining more and more attention, research on new compressors and expanders becomes more necessary. Suitable compressors need to be found to match the temperature and volume of gases under different working conditions. Therefore, it is necessary to design new types of compressors to better adapt to various working conditions, ensure efficiency while keeping the structure as simple as possible, and at the same time ensure the life and reliability of the compressor.

[0004] Based on this situation, a claw compressor design scheme is given. The document (Wang Jun, Zha Haibin, Jiang Xitong, Li Xueqin, Zhang Dahai. Claw engine power generation cycle device for thermal power generation. Shandong: CN102926826B, 2015-12-09.) gives a scheme for using a claw compressor in a thermal power generation system, but does not give a specific line equation and design steps. Generally, there is a clearance volume in the compressor, which increases the power consumption of the compressor and needs to reduce the clearance volume. Summary of the invention

[0005] In view of the above problems, the present invention proposes a claw type compressor, in which the small claw rotor and the large claw rotor are respectively composed of four curve segments, and a point and cycloid meshing method is adopted during exhaust. At the same time, the position of the exhaust port is reasonably arranged so that the clearance volume is completely eliminated. Moreover, the proposed rotor profile design steps are simple, which is of significance for enriching the rotor profile types and promoting the development of claw type compressors.

[0006] The technical solution adopted by the present invention to solve its technical problem is:

[0007] A claw compressor, comprising: a small claw rotor, a large claw rotor, a cylinder, a rear end cover, and a front end cover, wherein the end face profile of the small claw rotor is composed of four curves, which are: a first claw top arc ab, a speed change spiral bc, a first claw bottom arc cd, a first cycloid da, and the intersection of the first claw top arc ab and the first cycloid da is a first point a;

[0008] The end profile of the large claw rotor is composed of four curves, which are in clockwise order: the second claw bottom arc AB, the conjugate curve BC of the speed change spiral, the second claw top arc CD, the second cycloid DA, and the intersection of the second claw top arc CD and the second cycloid DA is the first point D;

[0009] The inner wall end face profile of the cylinder is composed of two arcs with different radii: the radii are R1 and R4 respectively;

[0010] The rear end cover is provided with an air intake port and an air exhaust port;

[0011] In the working process of synchronous counter-rotating double-rotation motion, the component profile of the small claw rotor and the component profile of the large claw rotor can achieve correct meshing, and the meshing relationship is: the first claw top arc ab, the speed-changing spiral bc, the first claw bottom arc cd, the first cycloid da, and the first point a of the small claw rotor are respectively meshed with the second claw bottom arc AB, the conjugate curve BC of the speed-changing spiral, the second claw top arc CD, the second point D, and the second cycloid DA in the component profile of the large claw rotor;

[0012] During the working process, the small claw rotor, large claw rotor, cylinder, rear end cover and front end cover form three groups of working chambers that change periodically: the small claw working chamber, the large claw working chamber and the mixed working chamber. The small claw working chamber and the large claw working chamber share an air intake port.

[0013] The composition line equation of the small claw rotor is as follows: a coordinate system O1xy is established with the rotation center O1 of the small claw rotor as the origin;

[0014] ①The equation of the first claw top arc ab is:

[0015] ②The equation of the arc cd at the bottom of the first claw is:

[0016] ③The equation of the first cycloid da is:

[0017] ④The equation of the speed-changing spiral bc is:

[0018] ⑤The equation of the pitch circle is:

[0019] Above: t is the angle parameter, rad; R1 is the arc radius of the top of the first claw of the small claw rotor, mm; R2 is the pitch circle radius, mm; R3 is the arc radius of the bottom of the first claw of the small claw rotor, mm; R4 is the arc radius of the top of the second claw of the large claw rotor, mm; θ is the central angle of the speed change spiral.

[0020] The composition line equation of the large claw rotor is as follows: a coordinate system O2xy is established with the rotation center O2 of the large claw rotor as the origin;

[0021] ①The equation of the arc AB at the bottom of the second claw is:

[0022] ②The equation of the second claw top arc CD is:

[0023] ③The equation of the second cycloid DA is:

[0024] ④r BC =M 12 ·M bc

[0025] Where: M 12 is the rotation transformation matrix, M bc The matrix form of the speed-changing spiral equation of the small claw rotor is as follows:

[0026]

[0027] Where:

[0028] ⑤The equation of the pitch circle is:

[0029] Above: R2 is the pitch circle radius, mm; R4 is the top arc radius of the second claw of the large claw rotor, mm; R5 is the bottom arc radius of the second claw of the large claw rotor, mm; t is the angle parameter, rad; L is the center distance between the two rotors.

[0030] The composition line equation of the end surface line of the cylinder is as follows: the center distance between the cylinder of the small claw rotor contact part and the cylinder of the large claw rotor contact part is L;

[0031] ① In the coordinate system O1xy, the cylinder line equation of the small claw rotor contact part is:

[0032] ② In the coordinate system O2xy, the cylinder line equation of the large claw rotor contact part is:

[0033] Where: R1 is the radius of the top arc of the first claw of the small claw rotor, mm; R4 is the radius of the top arc of the second claw of the large claw rotor; L is the center distance between the two rotors.

[0034] The small claw rotor and the large claw rotor rotate synchronously for one circle, and the working gas in the small claw working chamber formed undergoes five processes in sequence: suction process, isochoric conveying process, mixing process, mixing compression process, and exhaust process:

[0035] ① Inhalation process: When the small claw working chamber is connected to the air inlet, the inhalation process begins. As the small claw working chamber is rotated, the inhalation process ends when the small claw working chamber is separated from the air inlet, and then enters the isochoric conveying process;

[0036] ② Isovolumetric conveying process: As the small claw rotor and the large claw rotor rotate, the closed volume of the small claw working chamber remains unchanged;

[0037] ③Mixing process: When the small claw working chamber is connected to the large claw working chamber, the gas in the small claw working chamber is mixed with the compressed gas in the large claw working chamber, and the gas enters the mixing working chamber;

[0038] ④ Mixing and compression process: The closed volume of the mixing working chamber gradually decreases, and the gas inside it undergoes a compression process;

[0039] ⑤ Exhaust process: When the mixing working chamber is connected to the exhaust port, it enters the exhaust process and discharges the compressed gas.

[0040] The small claw rotor and the large claw rotor rotate synchronously for one circle, and the working gas in the large claw working chamber formed undergoes the following six processes in sequence:

[0041] ① Inhalation process: When the working chamber of the large claw is connected to the air inlet, the inhalation process begins. As the large claw rotates, the working chamber of the large claw is separated from the air inlet, and the inhalation process ends, and then enters the isochoric conveying process;

[0042] ② Isovolumetric conveying process: As the small claw rotor and the large claw rotor rotate, the closed volume of the large claw working chamber remains unchanged;

[0043] ③Compression process: As the small claw rotor and the large claw rotor rotate, the closed volume of the large claw working chamber gradually decreases;

[0044] ④Mixing process: When the large claw working chamber is connected to the small claw working chamber, the compressed gas in the large claw working chamber is mixed with the gas in the small claw working chamber, and the gas enters the mixing working chamber;

[0045] ⑤ Mixing and compression process: the closed volume of the mixing working chamber gradually decreases, and the gas inside it undergoes a compression process;

[0046] ⑥ Exhaust process: When the mixing working chamber is connected to the exhaust port, it enters the exhaust process and discharges the compressed gas.

[0047] The phase correspondence between the small claw working chamber and the large claw working chamber is:

[0048] ①When the small claw working chamber is in the process of suction, the large claw working chamber is in the process of isochoric conveying and compression;

[0049] ② When the working chamber of the small claw is in the isochoric conveying process, the working chamber of the large claw is in the compression process;

[0050] ③When the small claw working chamber is in the mixing process, the large claw working chamber is also in the mixing process;

[0051] ④ When the small claw working chamber is in the mixing and compression process, the large claw working chamber is in the mixing and compression process;

[0052] ⑤ When the small claw working chamber is in the exhaust process, the large claw working chamber is in the exhaust process.

[0053] The upper end point of the air intake port on the rear end cover should be higher than the second claw top arc CD of the large claw rotor, and the lower end point of the air intake port should be lower than the first claw top arc ab of the small claw rotor;

[0054] The lower end contour straight line of the exhaust port on the rear end cover is tangent to the second claw top arc CD of the large claw rotor, and the left end point of the exhaust port is located on the center line of the small claw rotor and the large claw rotor.

[0055] The meshing of the first claw top arc ab of the small claw rotor and the second claw bottom arc AB of the large claw rotor is defined as the moment when the rotor angle is 0°, the small claw working chamber is connected to the air intake port, and the air intake process is carried out, and at the same time, the large claw working chamber of the previous cycle is undergoing a compression process; when the rotor rotates from 0° to 47°, the volume of the small claw working chamber gradually increases, and is divided into two independent working chambers, the large claw working chamber and the small claw working chamber; when the rotor rotates from 47° to 78°, the air intake process of the small claw working chamber ends, and an isochoric conveying process is carried out, and at the same time, the large claw working chamber on the left side is undergoing an air intake process, and the large claw working chamber on the right side is undergoing a compression process; when the rotor rotates from 78° to 203°, the gas in the isochoric conveying process of the small claw working chamber is mixed with the gas after the compression process of the large claw working chamber on the right side to form a new mixed working chamber, and a mixed compression process is carried out; when the rotor rotates from 203° to 360°, when the outer contour of the small claw rotor coincides with the right end point of the exhaust port, it is the minimum exhaust volume before the mixed working chamber starts to connect to the exhaust hole, and then the exhaust port is opened to discharge all compressed gas.

[0056] The beneficial effects of the present invention are:

[0057] ① The claw compressor proposed has a unique mixed boosting process in addition to the three working processes of suction, compression and exhaust of a traditional compressor.

[0058] ② The claw compressor proposed adopts the meshing mode of point and cycloid when exhausting, and opens the exhaust port at the appropriate position, so that the compressor completely eliminates the clearance volume and saves power consumption.

[0059] ③ The proposed claw-type compressor has a simple profile of small claw rotor and large claw rotor, and is easy to process and manufacture.

[0060] ④ The claw compressor proposed adopts an asymmetric distribution of the small claw rotor and the large claw rotor, so that under the same suction volume and exhaust pressure conditions, the load on the synchronous gear connecting the small claw rotor is reduced.

[0061] ⑤The proposed claw compressor enriches the types of claw compressor rotor profiles. BRIEF DESCRIPTION OF THE DRAWINGS

[0062] Figure 1 The invention discloses a line diagram of a small claw rotor (1) of a claw type compressor.

[0063] Figure 2 The invention discloses a line diagram of a claw-type compressor having a large claw rotor (2).

[0064] Figure 3 The invention discloses a schematic diagram of the meshing of a small claw rotor (1) and a large claw rotor (2) of a claw compressor.

[0065] Figure 4 It is a schematic diagram of the working process when the small claw rotor (1) is at 0°.

[0066] Figure 5 It is a schematic diagram of the working process of starting the isochoric conveying process when the small claw rotor (1) is at 47°.

[0067] Figure 6 It is a schematic diagram of the working process of the isochoric conveying process when the small claw rotor (1) rotates from 47° to 78°.

[0068] Figure 7 It is a schematic diagram of the working process of the mixing process when the small claw rotor (1) rotates from 78° to 203°.

[0069] Figure 8 This is a schematic diagram of the working process when the exhaust process starts when the small claw rotor (1) is at 203°.

[0070] Fig. 9 It is a schematic diagram of the working process of the exhaust process when the small claw rotor (1) rotates from 203° to 360°.

[0071] Fig.10 It is a schematic diagram of the working process when the small claw rotor (1) rotates from 203° to 360° and the exhaust process ends.

[0072] Fig.11 It is a partial enlarged view of the opening position of the exhaust port (402) of a claw-type compressor.

[0073] Fig.12 This is a diagram of the main components of a claw compressor.

[0074] Fig.13 The invention discloses a parts diagram of a rear end cover (4) of a claw type compressor.

[0075] In the figure: R1—radius of the first claw top arc ab of the small claw rotor (1); R2—pitch circle radius; R3—radius of the first claw bottom arc cd of the small claw rotor (1); R4—radius of the second claw top arc CD of the large claw rotor (2); R5—radius of the second claw bottom arc AB of the large claw rotor (2); 101—small claw working chamber (101); 201—large claw working chamber (201); 102—mixing working chamber (102); 1—small claw rotor (1); 2—large claw rotor (2); 3—cylinder (3); 4—rear end cover (4); 5—front end cover (5); 401—intake port (401); 402—exhaust port (402). DETAILED DESCRIPTION

[0076] The present invention will be further described below in conjunction with the accompanying drawings.

[0077] like Figure 1 As shown, it is a profile diagram of a small claw rotor 1 of a claw compressor. The end profile of the small claw rotor 1 includes: 2 arcs, 1 cycloid and 1 speed-changing spiral, which are: the first claw top arc ab, the speed-changing spiral bc, the first claw bottom arc cd, and the first cycloid da in the counterclockwise direction; a coordinate system O1xy is established, with O1 as the origin; the equations of the first claw top arc ab, the first claw bottom arc cd, and the pitch circle of the small claw rotor 1 are as follows:

[0078] The equation of the first claw top arc ab is:

[0079] The equation of the arc cd at the bottom of the first claw is:

[0080] The equation of the pitch circle is:

[0081] Above: t is the angle parameter, rad; R1 is the top arc radius of the first claw of the small claw rotor 1, mm; R2 is the pitch circle radius, mm; R3 is the bottom arc radius of the first claw of the small claw rotor 1, mm;

[0082] The equations of the first cycloid da and the speed-changing spiral bc of the small claw rotor 1 are as follows:

[0083] The equation of the first cycloid da is:

[0084] The equation of the speed change spiral bc is:

[0085] Above: R4 is the arc radius of the second claw top of the large claw rotor 2, mm; θ is the central angle of the speed change spiral.

[0086] like Figure 2As shown, it is a profile diagram of a claw rotor 2 of a claw compressor. The end profile of the claw rotor 2 includes: 2 arcs, 1 cycloid and 1 conjugate curve of the speed-changing spiral, which are: the second claw bottom arc AB, the conjugate curve BC of the speed-changing spiral, the second claw top arc CD, and the second cycloid DA in clockwise direction; a coordinate system O2xy is established, with O2 as the origin; the second claw bottom arc AB, the second claw top arc CD, and the pitch circle of the large claw rotor 2 are as follows:

[0087] The equation of the arc AB at the bottom of the second claw is:

[0088] The equation of the second claw top arc CD is:

[0089] The equation of the pitch circle is:

[0090] Above: t is the angle parameter, rad; R2 is the pitch circle radius, mm; R4 is the top arc radius of the second claw of the large claw rotor 2, mm; R5 is the bottom arc radius of the second claw of the large claw rotor 2, mm;

[0091] The equation of the conjugate curve BC of the first cycloid DA and the speed-changing spiral of the large claw rotor (2) is as follows:

[0092] The equation of the second cycloid DA is:

[0093] The equation of the conjugate curve BC of the speed-changing spiral is: BC =M 12 ·M bc

[0094] Where: M 12 is the rotation transformation matrix, M bc The matrix form of the speed change spiral equation of the small claw rotor 1 is as follows:

[0095]

[0096] Where:

[0097]

[0098] L—center distance between two rotors;

[0099] Above: t—angle parameter, rad.

[0100] like Figure 3The figure shows a schematic diagram of the meshing of a small claw rotor 1 and a large claw rotor 2 of a claw compressor. During the working process of synchronous counter-rotating double-rotation motion, the component profile of the small claw rotor 1 and the component profile of the large claw rotor 2 can achieve correct meshing, and the meshing relationship is: the first claw top arc ab, the speed change spiral bc, the first claw bottom arc cd, the first cycloid da, and the first point a in the component profile of the small claw rotor 1 are respectively meshed with the second claw bottom arc AB, the conjugate curve BC of the speed change spiral, the second claw top arc CD, the second point D, and the second cycloid DA in the component profile of the large claw rotor 2.

[0101] like Figure 4 As shown, it is a schematic diagram of the working process when the small claw rotor 1 is at 0°. When the rotor moves to the position shown, the small claw working chamber 101 is connected to the air intake port 401 to continuously inhale air.

[0102] like Figure 5 As shown, it is a schematic diagram of the working process of the isochoric conveying process starting when the small claw rotor 1 is 47°. As the rotor rotates, the small claw working chamber 101 is divided into the small claw working chamber 101 and the large claw working chamber 201 on the left. The small claw working chamber 101 is cut off from the air intake port 401, and the small claw working chamber 101 realizes the isochoric conveying process. The large claw working chamber 201 on the left is connected to the air intake port 401 to continuously inhale air. This inhalation continues until the air intake port 401 is cut off by the large claw rotor 2, and the gas in the large claw working chamber 201 on the right is continuously compressed.

[0103] like Figure 6 As shown, it is a schematic diagram of the working process of the isochoric conveying process when the small claw rotor 1 rotates from 47° to 78°. The gas in the small claw working chamber 101 is isochorically conveyed to be mixed with the compressed gas in the large claw working chamber 201 on the right, and at this time the volume of the large claw working chamber 201 on the right has also reached the minimum.

[0104] like Figure 7 As shown, it is a schematic diagram of the working process of the mixing process when the small claw rotor 1 rotates from 78° to 203°, and the compressed gas in the small claw working chamber 101 and the large claw working chamber 201 on the right are mixed to form a new mixing working chamber 102.

[0105] like Figure 8 As shown, it is a schematic diagram of the working process when the exhaust process starts when the small claw rotor 1 is 203°, and the outer contour line of the small claw rotor 1 coincides with the right end point of the exhaust port 402. When the exhaust port 402 is about to open, it is the minimum exhaust volume before the mixing working chamber 102 starts to connect to the exhaust hole.

[0106] like Fig. 9As shown, it is a schematic diagram of the working process of the exhaust process when the small claw rotor 1 rotates from 203° to 360°. The exhaust port 402 has been opened and exhaust has begun. At this time, the large claw working chamber 201 has also completed the air intake and started the isochoric conveying process. The newly formed small claw working chamber 101 is also constantly inhaling air.

[0107] like Fig.10 As shown, it is a schematic diagram of the working process when the small claw rotor 1 rotates from 203° to 360° and the exhaust process ends, and the compressed gas is completely discharged from the exhaust port 402.

[0108] like Fig.11 As shown, it is a partial enlarged view of the opening position of the exhaust port 402 of a claw type compressor. The opening of the exhaust port 402 depends on the position where the small claw rotor 1 and the large claw rotor 2 produce the residual volume after the last exhaust. The lower end contour straight line of the exhaust port 402 is tangent to the arc of the second claw top of the large claw rotor 2, and the left end point of the exhaust port 402 is located on the center line connecting the center of the small claw rotor 1 and the center of the large claw rotor 2, which avoids the generation of residual volume.

[0109] like Fig.12 As shown, it is a main component part diagram of a claw compressor, including: a small claw rotor 1, a large claw rotor 2, a cylinder 3, a rear end cover 4 and a front end cover 5. The rear end cover 4 is provided with an intake port 401 and an exhaust port 402. During the working process, an intake chamber, an isochoric closed chamber, a compression chamber, a mixed compression chamber and an exhaust chamber can be formed, which are respectively used for gas intake, isochoric conveying, compression, mixed compression and exhaust processes; the volume of the intake chamber gradually increases and is always connected with the intake port 401, the volume of the isochoric closed chamber remains unchanged and is closed, the volume of the compression chamber is closed and gradually decreases, the volume of the mixed compression chamber is closed and gradually decreases, and the volume of the exhaust chamber gradually decreases and is always connected with the exhaust port 402.

[0110] like Fig.13 As shown, it is a part drawing of the rear end cover 4 of a claw type compressor, from which the positions and shapes of the intake port 401 and the exhaust port 402 on the rear end cover 4 can be observed. The principle of opening the intake port 401 is: the upper end point of the intake port 401 must be higher than the second claw top arc of the large claw rotor 2 to ensure that the small claw working chamber 101 can continuously inhale air, and the lower end point of the intake port 401 must be lower than the first claw top arc of the small claw rotor 1 to ensure that the large claw working chamber 201 can continuously inhale air.

[0111] Although the above describes the specific implementation mode of the present invention in conjunction with the accompanying drawings, it is not intended to limit the scope of protection of the present invention. Those skilled in the art should understand that various modifications or variations that can be made by those skilled in the art on the basis of the technical solution of the present invention without creative work are still within the scope of protection of the present invention.

Claims

1. A claw compressor, comprising: A small claw rotor (1), a large claw rotor (2), a cylinder (3), a rear end cover (4), and a front end cover (5), wherein the end face profile of the small claw rotor (1) is composed of four curves, which are, in a counterclockwise direction, first claw top arc ab, speed change spiral bc, first claw bottom arc cd, first cycloid da, and the intersection of the first claw top arc ab and the first cycloid da is the first point a; The end profile of the large claw rotor (2) is composed of four curves, which are arranged in a clockwise direction: the second claw bottom arc AB, the conjugate curve BC of the speed change spiral bc, the second claw top arc CD, the second cycloid DA, and the intersection of the second claw top arc CD and the second cycloid DA is the first point D; The inner wall end face profile of the cylinder (3) is composed of two arcs with different radii: the radii are R1 and R4 respectively; The rear end cover (4) is provided with an air intake port (401) and an air exhaust port (402); During the working process of synchronous counter-rotating double-rotation motion, the component profile of the small claw rotor (1) and the component profile of the large claw rotor (2) can achieve correct meshing, and the meshing relationship is: the first claw top arc ab, the speed change spiral bc, the first claw bottom arc cd, the first cycloid da, and the first point a of the small claw rotor (1) are respectively meshed with the second claw bottom arc AB, the conjugate curve BC of the speed change spiral bc, the second claw top arc CD, the second point D, and the second cycloid DA in the component profile of the large claw rotor (2); During operation, the small claw rotor (1), the large claw rotor (2), the cylinder (3), the rear end cover (4), and the front end cover (5) form three groups of working chambers that change periodically: a small claw working chamber (101), a large claw working chamber (201), and a mixing working chamber (102). The small claw working chamber (101) and the large claw working chamber (201) share a common air intake port (401). The composition line equation of the small claw rotor (1) is as follows: A coordinate system O1xy is established with the rotation center O1 of the small claw rotor (1) as the origin; ①The equation of the first claw top arc ab is: ②The equation of the arc cd at the bottom of the first claw is: ③The equation of the first cycloid da is: ④The equation of the speed-changing spiral bc is: ⑤The equation of the pitch circle is: In the above, t is an angle parameter, rad; R1 is a radius of the top arc of the first claw of the small claw rotor (1), mm; R2 is a radius of the pitch circle, mm; R3 is a radius of the bottom arc of the first claw of the small claw rotor (1), mm; R4 is a radius of the top arc of the second claw of the large claw rotor (2), mm; θ is a central angle of the speed change spiral; The composition line equation of the large claw rotor (2) is as follows: A coordinate system O2xy is established with the rotation center O2 of the large claw rotor (2) as the origin; ①The equation of the arc AB at the bottom of the second claw is: ②The equation of the second claw top arc CD is: ③The equation of the second cycloid DA is: ④ The equation of the conjugate curve BC of the speed-changing spiral bc is: BC =M 12 ·M bc Where: M 12 is the rotation transformation matrix, M bc The matrix form of the variable speed spiral equation of the small claw rotor (1) is as follows: Where: ⑤The equation of the pitch circle is: Above: R2 is the pitch circle radius, mm; R4 is the top arc radius of the second claw of the large claw rotor (2), mm; R5 is the bottom arc radius of the second claw of the large claw rotor (2), mm; t is the angle parameter, rad; L is the center distance between the two rotors; The upper end point of the air intake port (401) on the rear end cover (4) is higher than the second claw top circular arc CD of the large claw rotor (2), and the lower end point of the air intake port (401) is lower than the first claw top circular arc ab of the small claw rotor (1); the lower end contour straight line of the air exhaust port (402) on the rear end cover (4) is tangent to the second claw top circular arc CD of the large claw rotor (2), and the left end point of the air exhaust port (402) is located on the center line connecting the small claw rotor (1) and the large claw rotor (2).

2. A claw type compressor according to claim 1, characterized in that: The composition profile equation of the end profile of the cylinder (3) is as follows: The center distance between the cylinder (3) of the contact part of the small claw rotor (1) and the cylinder (3) of the contact part of the large claw rotor (2) is L; ① In the coordinate system O1xy, the line equation of the cylinder (3) at the contact part of the small claw rotor (1) is: ② In the coordinate system O2xy, the line equation of the cylinder (3) at the contact part of the large claw rotor (2) is: Wherein: R1 is the radius of the top arc of the first claw of the small claw rotor (1), mm; R4 is the radius of the top arc of the second claw of the large claw rotor (2); L is the center distance between the two rotors.

3. A claw type compressor according to claim 1, characterized in that: The small claw rotor (1) and the large claw rotor (2) rotate synchronously for one circle, and the working gas in the small claw working chamber (101) formed thereby undergoes five processes in sequence: an intake process, an isochoric conveying process, a mixing process, a mixing compression process, and an exhaust process: ① Inhalation process: When the small claw working chamber (101) is connected to the air inlet (401), the inhalation process begins. As the small claw working chamber (101) and the air inlet (401) are separated, the inhalation process ends, and then the isochoric conveying process begins. ② Isovolumetric conveying process: as the small claw rotor (1) and the large claw rotor (2) rotate, the closed volume of the small claw working chamber (101) remains unchanged; ③ Mixing process: when the small claw working chamber (101) is connected to the large claw working chamber (201), the gas in the small claw working chamber (101) is mixed with the compressed gas in the large claw working chamber (201), and the gas enters the mixing working chamber (102); ④ Mixing and compression process: the closed volume of the mixing working chamber (102) gradually decreases, and the gas therein undergoes a compression process; ⑤ Exhaust process: When the mixing working chamber (102) is connected to the exhaust port (402), the exhaust process begins and the compressed gas is discharged.

4. A claw type compressor according to claim 1, characterized in that: The small claw rotor (1) and the large claw rotor (2) rotate synchronously for one circle, and the working gas in the large claw working chamber (201) formed thereby undergoes the following six processes in sequence: ① Inhalation process: When the large claw working chamber (201) is connected to the air inlet (401), the inhalation process begins. As the large claw working chamber (201) and the air inlet (401) are separated, the inhalation process ends, and then the isochoric conveying process begins. ② Isovolumetric conveying process: as the small claw rotor (1) and the large claw rotor (2) rotate, the closed volume of the large claw working chamber (201) remains unchanged; ③ Compression process: As the small claw rotor (1) and the large claw rotor (2) rotate, the closed volume of the large claw working chamber (201) gradually decreases; ④ Mixing process: when the large claw working chamber (201) is connected to the small claw working chamber (101), the compressed gas in the large claw working chamber (201) is mixed with the gas in the small claw working chamber (101), and the gas enters the mixing working chamber (102); ⑤ Mixing and compression process: the closed volume of the mixing working chamber (102) gradually decreases, and the gas therein undergoes a compression process; ⑥ Exhaust process: When the mixing working chamber (102) is connected to the exhaust port (402), the exhaust process begins and the compressed gas is discharged.

5. A claw type compressor according to claim 1, characterized in that: The phase correspondence between the small claw working chamber (101) and the large claw working chamber (201) is: ① When the small claw working chamber (101) is in the process of inhaling, the large claw working chamber (201) is in the process of isochoric conveying and compression; ② When the small claw working chamber (101) is in the isochoric conveying process, the large claw working chamber (201) is in the compression process; ③ When the small claw working chamber (101) is in the mixing process, the large claw working chamber (201) is in the mixing process; ④ When the small claw working chamber (101) is in the mixing and compression process, the large claw working chamber (201) is in the mixing and compression process; ⑤ When the small claw working chamber (101) is in the exhaust process, the large claw working chamber (201) is in the exhaust process.

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