阅读说明：本技术 一种爪式压缩机 (Claw type compressor ) 是由 王君 谈庆朋 武萌 刘译阳 董丽宁 李祥艳 于 2020-07-03 设计创作，主要内容包括：本发明公开了一种爪式压缩机,该压缩机由小爪转子(1)、大爪转子(2)、气缸(3)、后端盖(4)、前端盖(5)组成,小爪转子(1)的端面型线由四段曲线组成,按逆时针方向依次为：第一爪顶圆弧ab、变速螺线bc、第一爪底圆弧cd、第一摆线da、第一爪顶圆弧ab和第一摆线da的交点为第一点a；大爪转子(2)的端面型线由四段曲线组成,按顺时针方向依次为：第二爪底圆弧AB、变速螺线的共轭曲线BC、第二爪顶圆弧CD、第二摆线DA、第二爪顶圆弧CD和第二摆线DA的交点为第一点D；所提出的爪式压缩机具有工作过程多样、设计步骤简单、便于加工的优点,丰富了爪式压缩机转子的型线类型。(The invention discloses a claw type compressor, which consists 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), wherein the end surface molded line of the small claw rotor (1) consists of four sections of curves, and the four sections of curves are sequentially arranged in the anticlockwise direction: the intersection point of the first claw top circular arc ab, the speed change spiral bc, the first claw bottom circular arc cd, the first cycloid da, the first claw top circular arc ab and the first cycloid da is a first point a; the end face molded line of the large claw rotor (2) consists of four sections of curves, and the four sections of curves are sequentially in the clockwise direction: a second claw bottom arc AB, a conjugate curve BC of the variable speed spiral, a second claw top arc CD, a second cycloid DA, and an intersection point of the second claw top arc CD and the second cycloid DA are a first point D; the claw type compressor has the advantages of various working processes, simple design steps and convenience in processing, and the molded line types of the claw type compressor rotor are enriched.)

1. A claw type compressor comprising: little claw rotor (1), big claw rotor (2), cylinder (3), rear end cap (4), front end cap (5), characterized by: the end face molded line of the small claw rotor (1) consists of four sections of curves, and the four sections of curves are sequentially in the anticlockwise direction: the intersection point of the first claw top circular arc ab, the speed change spiral bc, the first claw bottom circular arc cd, the first cycloid da, the first claw top circular arc ab and the first cycloid da is a first point a;

the end face molded line of the large claw rotor (2) consists of four sections of curves, and the four sections of curves are as follows in sequence in the clockwise direction: a second claw bottom arc AB, a conjugate curve BC of the variable speed spiral, a second claw top arc CD, a second cycloid DA, and an intersection point of the second claw top arc CD and the second cycloid DA are a first point D;

the molded line of the end face of the inner wall of the cylinder (3) consists of two arcs with different radiuses: radius is respectively R₁And R₄；

The rear end cover (4) is provided with an air suction port (401) and an air exhaust port (402);

in the working process of synchronous and opposite-direction double-rotation movement, the group forming line of the small claw rotor (1) and the group forming line of the large claw rotor (2) can realize correct meshing, and the meshing relationship is as follows: a first claw top circular arc AB, a speed change spiral BC, a first claw bottom circular arc CD, a first cycloid DA and a first point a of the small claw rotor (1) are respectively meshed with a second claw bottom circular arc AB, a conjugate curve BC of the speed change spiral, a second claw top circular arc CD, a second point D and a second cycloid DA in a group forming line of the large claw rotor (2);

in the working process, little claw rotor (1), big claw rotor (2), cylinder (3), rear end cap (4), front end housing (5), 3 groups working chamber that form periodic variation: the device comprises a small-claw working cavity (101), a large-claw working cavity (201) and a mixed working cavity (102), wherein the small-claw working cavity (101) and the large-claw working cavity (201) share one air suction port (401).

2. A claw type compressor according to claim 1, wherein: the composition linear equation of the small claw rotor (1) is as follows;

using the rotation center O of the small claw rotor (1)₁Establishing a coordinate system O by taking the point as an origin₁xy；

① the equation for the first jaw tip arc ab is:

② the equation for the first paw bottom arc cd is:

③ the equation for the first cycloid da is:

④ the equation for the variable speed spiral bc is:

the equation for the ⑤ pitch circle is:

the method comprises the following steps: t-is the angle parameter, rad; r₁-is the radius of the first claw top arc of the small claw rotor (1), mm; r₂-is pitch circle radius, mm; r₃The radius of a first claw bottom arc of the small claw rotor (1) is mm; r₄The radius of a second claw top arc of the large claw rotor (2) is mm; theta-is the central angle of the variable speed spiral.

3. A claw type compressor according to claim 1, wherein: the composition linear equation of the large claw rotor (2) is as follows;

the rotation center O of the big claw rotor (2)₂Establishing a coordinate system O by taking the point as an origin₂xy；

① the equation for the second paw bottom arc AB is:

② the equation for the second jaw tip arc CD is:

③ the equation for the second cycloid DA is:

④r_BC＝M₁₂·M_bc

in the formula: m₁₂For rotating the transformation matrix, M_bcIn the form of a matrix of the variable speed spiral equation of the small jaw rotor (1), as follows:

in the formula:

the equation for the ⑤ pitch circle is:

the method comprises the following steps: r₂-is pitch circle radius, mm; r₄The radius of a second claw top arc of the large claw rotor (2) is mm; r₅The radius of a second claw bottom arc of the large claw rotor (2) is mm; t-angle parameter, rad; l-the centre-to-centre distance of the two rotors.

4. A claw type compressor according to claim 1, wherein: the composition type line equation of the end face molded line 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 coordinate system O₁In xy, the molded line equation of the cylinder (3) at the contact part of the small claw rotor (1) is as follows:

② in coordinate system O₂In xy, the molded line equation of the cylinder (3) at the contact part of the large claw rotor (2) is as follows:

in the formula: r₁-is the radius of the first claw top arc of the small claw rotor (1), mm; r₄-is the second claw top arc radius of the large claw rotor (2); l-the centre-to-centre distance of the two rotors.

5. A claw type compressor according to claim 1, wherein: the small claw rotor (1) and the large claw rotor (2) synchronously rotate for a circle, and working gas in the formed small claw working cavity (101) sequentially undergoes a suction process, an equal-volume conveying process, a mixing process, a mixed compression process and an exhaust process by 5 processes:

the air suction process: when the small claw working cavity (101) is communicated with the air suction port (401), the air suction process starts, and along with rotation, when the small claw working cavity (101) is separated from the air suction port (401), the air suction process is finished, and then the constant volume conveying process is started;

and (2) carrying out an equal-volume conveying process: the closed volume of the small claw working cavity (101) is unchanged along with the rotation of the small claw rotor (1) and the large claw rotor (2);

③ the mixing process: when the small claw working cavity (101) is communicated with the large claw working cavity (201), gas in the small claw working cavity (101) is mixed with gas compressed in the large claw working cavity (201), and the gas enters the mixed working cavity (102);

and fourthly, a mixed compression process: the closed volume of the mixing working chamber (102) is gradually reduced, and the gas in the mixing working chamber is compressed;

and a gas exhaust process: when the mixed working chamber (102) is communicated with the exhaust port (402), an exhaust process is carried out, and compressed gas is exhausted.

6. A claw type compressor according to claim 1, wherein: the small claw rotor (1) and the large claw rotor (2) synchronously rotate for a circle, and the working gas in the formed large claw working cavity (201) sequentially undergoes the following 6 processes:

the air suction process: when the big claw working cavity (201) is communicated with the air suction port (401), the air suction process starts, and along with the rotation, when the big claw working cavity (201) is separated from the air suction port (401), the air suction process is finished, and then the constant volume conveying process is started;

and (2) carrying out an equal-volume conveying process: the closed volume of the large claw working cavity (201) is unchanged along with the rotation of the small claw rotor (1) and the large claw rotor (2);

③ the compression process: along with the rotation of the small claw rotor (1) and the large claw rotor (2), the closed volume of the large claw working cavity (201) is gradually reduced;

and fourthly, a mixing process: when the big claw working cavity (201) is communicated with the small claw working cavity (101), compressed gas in the big claw working cavity (201) is mixed with gas in the small claw working cavity (101), and the gas enters the mixed working cavity (102);

a mixed compression process: the closed volume of the mixing working chamber (102) is gradually reduced, and the gas in the mixing working chamber is compressed;

the exhaust process: when the mixed working chamber (102) is communicated with the exhaust port (402), an exhaust process is carried out, and compressed gas is exhausted.

7. A claw type compressor according to claim 1, wherein: the phase corresponding relation between the small claw working cavity (101) and the large claw working cavity (201) is as follows:

firstly, when the small claw working cavity (101) is in the air suction process, the large claw working cavity (201) is in the constant volume conveying and compressing process;

secondly, when the small claw working cavity (101) is in the constant-volume conveying process, the large claw working cavity (201) is in the compression process;

thirdly, when the small claw working chamber (101) is in the mixing process, the large claw working chamber (201) is in the mixing process;

fourthly, when the small claw working cavity (101) is in the mixed compression process, the large claw working cavity (201) is in the mixed compression process;

fifthly, when the small claw working chamber (101) is in the exhaust process, the large claw working chamber (201) is in the exhaust process.

8. A claw type compressor according to claim 1, wherein: the upper end point of an air suction port (401) on the rear end cover (4) is higher than a second claw top arc CD of the large claw rotor (2), and the lower end point of the air suction port (401) is lower than a first claw top arc ab of the small claw rotor (1); the lower end profile straight line of the exhaust port (402) on the rear end cover (4) is tangent to the second claw top arc CD of the large claw rotor (2), and the left end point of the exhaust port (402) is positioned on the central connecting line of the small claw rotor (1) and the large claw rotor (2).

Technical Field

The invention belongs to the technical field of compressor engineering, and particularly relates to a claw type compressor.

Background

The claw type compressor drives a pair of meshed rotors to rotate and mesh by means of synchronous opposite-direction double-rotation movement of the gears, so that the periodic change of the volume of a working cavity is realized, the processes of gas suction, compression and discharge are completed, and the whole working cycle is completed; therefore, the profile design of the rotor is very important, and the working performance of the claw type compressor is greatly influenced.

Along with the increasing importance of energy recovery and utilization systems, the research of novel compressors and expanders is more necessary, and proper compressors are required to be found for matching the temperature and the gas quantity of gas under different working conditions, so that the novel compressor type is necessarily designed to be better suitable for various working conditions, the structure of the compressor is as simple as possible while the efficiency is ensured, and the service life and the reliability of the compressor are ensured.

Based on the situation, a design scheme of the claw type compressor is provided, and a scheme of the claw type compressor used by a thermal power generation system is provided in a document (Wangjun, Chaihabi, Jiang Xitong, Li Xueqin, Chao sea, claw type engine power generation circulating device for thermal power generation, Shandong: CN102926826B,2015-12-09.), but specific line equations and design steps are not given. Typically, clearance volumes exist within the compressor, which results in increased compressor power consumption, requiring a reduction in the clearance volume.

Disclosure of Invention

In order to solve the problems, the invention provides a claw type compressor, wherein a small claw rotor and a large claw rotor are respectively composed of four sections of curves, a point and cycloid meshing mode is adopted during air exhaust, the positions of air exhaust ports are reasonably arranged, so that the clearance volume is completely eliminated, and the proposed rotor profile design step is simple and has significance for enriching the rotor profile types and promoting the development of the claw type compressor.

The technical scheme adopted by the invention for solving the technical problems is as follows:

a claw type compressor comprising: the end face molded line of the small claw rotor consists of four sections of curves and sequentially comprises the following steps in the anticlockwise direction: the intersection point of the first claw top circular arc ab, the speed change spiral bc, the first claw bottom circular arc cd, the first cycloid da, the first claw top circular arc ab and the first cycloid da is a first point a;

the end face molded line of the large claw rotor consists of four sections of curves, and the four sections of curves sequentially comprise the following curves in the clockwise direction: a second claw bottom arc AB, a conjugate curve BC of the variable speed spiral, a second claw top arc CD, a second cycloid DA, and an intersection point of the second claw top arc CD and the second cycloid DA are a first point D;

the molded line of the end face of the inner wall of the cylinder consists of two arcs with different radiuses: radius is respectively R₁And R₄；

The rear end cover is provided with an air suction port and an air exhaust port;

in the working process of synchronous opposite-direction double-rotation movement, the group forming line of the small claw rotor and the group forming line of the large claw rotor can realize correct meshing, and the meshing relationship is as follows: a first claw top circular arc AB, a speed change spiral BC, a first claw bottom circular arc CD, a first cycloid DA and a first point a of the small claw rotor are respectively meshed with a second claw bottom circular arc AB, a conjugate curve BC of the speed change spiral, a second claw top circular arc CD, a second point D and a second cycloid DA in a forming line of the large claw rotor;

in the working process, the small claw rotor, the large claw rotor, the cylinder, the rear end cover and the front end cover form 3 groups of working cavities with periodic variation: the device comprises a small claw working cavity, a large claw working cavity and a mixed working cavity, wherein the small claw working cavity and the large claw working cavity share one air suction port.

The constitutive line equation of the small claw rotor is as follows: with the centre of rotation O of the claw rotor₁Establishing a coordinate system O by taking the point as an origin₁xy；

① the equation for the first jaw tip arc ab is:

② the equation for the first paw bottom arc cd is:

③ the equation for the first cycloid da is:

④ the equation for the variable speed spiral bc is:

the equation for the ⑤ pitch circle is:

the method comprises the following steps: t-is the angle parameter, rad; r₁The radius of a first claw top arc of the small claw rotor is mm; r₂-is pitch circle radius, mm; r₃The radius of a first claw bottom arc of the small claw rotor is mm; r₄The radius of a second claw top arc of the large claw rotor is mm; theta-is the central angle of the variable speed spiral.

The constitutive line equation of the big claw rotor is as follows: with the centre of rotation O of the large-claw rotor₂Establishing a coordinate system O by taking the point as an origin₂xy；

① the equation for the second paw bottom arc AB is:

② the equation for the second jaw tip arc CD is:

③ the equation for the second cycloid DA is:

④r_BC＝M₁₂·M_bc

in the formula: m₁₂For rotating the transformation matrix, M_bcIn the form of a matrix of the variable speed spiral equation for a small claw rotor as follows:

in the formula:

the equation for the ⑤ pitch circle is:

the method comprises the following steps: r₂-is pitch circle radius, mm; r₄The radius of a second claw top arc of the large claw rotor is mm; r₅The radius of a circular arc at the bottom of a second claw of the large claw rotor is mm; t-angle parameter, rad; l-the centre-to-centre distance of the two rotors.

The composition line equation of the end face molded 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;

① in coordinate system O₁In xy, the cylinder profile equation of the small claw rotor contact part is as follows:

② in coordinate system O₂In xy, the cylinder profile equation of the contact part of the large claw rotor is as follows:

in the formula: r₁The radius of a first claw top arc of the small claw rotor is mm; r₄The radius of a second claw top arc of the large claw rotor is-the radius of the second claw top arc; l-the centre-to-centre distance of the two rotors.

The small claw rotor and the large claw rotor synchronously rotate for a circle, and working gas in the formed small claw working cavity sequentially undergoes 5 processes of an air suction process, an equal volume conveying process, a mixing process, a mixed compression process and an exhaust process:

the air suction process: when the small claw working cavity is communicated with the air suction port, the air suction process starts, and along with rotation, when the small claw working cavity is separated from the air suction port, the air suction process is finished, and then the constant volume conveying process is carried out;

and (2) carrying out an equal-volume conveying process: the closed volume of the small claw working cavity is unchanged along with the rotation of the small claw rotor and the large claw rotor;

③ the mixing process: when the small claw working cavity is communicated with the large claw working cavity, gas in the small claw working cavity is mixed with gas compressed in the large claw working cavity, and the gas enters the mixed working cavity;

and fourthly, a mixed compression process: the closed volume of the mixing working chamber is gradually reduced, and the gas in the mixing working chamber is compressed;

and a gas exhaust process: when the mixing working cavity is communicated with the exhaust port, the exhaust process is carried out, and compressed gas is exhausted.

The small claw rotor and the large claw rotor synchronously rotate for a circle, and working gas in the formed large claw working cavity sequentially undergoes the following 6 processes:

the air suction process: when the big claw working cavity is communicated with the air suction port, the air suction process starts, and along with the rotation, when the big claw working cavity is separated from the air suction port, the air suction process is finished, and then the constant volume conveying process is carried out;

and (2) carrying out an equal-volume conveying process: the closed volume of the large claw working cavity is unchanged along with the rotation of the small claw rotor and the large claw rotor;

③ the compression process: along with the rotation of the small claw rotor and the large claw rotor, the closed volume of the large claw working cavity is gradually reduced;

and fourthly, a mixing process: when the big claw working cavity is communicated with the small claw working cavity, the compressed gas in the big claw working cavity is mixed with the gas in the small claw working cavity, and the gas enters the mixed working cavity;

a mixed compression process: the closed volume of the mixing working chamber is gradually reduced, and the gas in the mixing working chamber is compressed;

the exhaust process: when the mixing working cavity is communicated with the exhaust port, the exhaust process is carried out, and compressed gas is exhausted.

The phase corresponding relation between the small claw working cavity and the large claw working cavity is as follows:

firstly, when the small claw working cavity is in the air suction process, the large claw working cavity is in the constant volume conveying and compressing process;

secondly, when the small claw working cavity is in the equal-volume conveying process, the large claw working cavity is in the compression process;

thirdly, when the small claw working chamber is in the mixing process, the large claw working chamber is in the mixing process;

fourthly, when the small claw working chamber is in the mixed compression process, the large claw working chamber is in the mixed compression process;

fifthly, when the small claw working chamber is in the exhaust process, the large claw working chamber is in the exhaust process.

The upper end point of an air suction port on the rear end cover is higher than a second claw top circular arc CD of the large claw rotor, and the lower end point of the air suction port is lower than a first claw top circular arc ab of the small claw rotor;

the lower end profile 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 positioned on the central connecting line of the small claw rotor and the large claw rotor.

The moment when the first claw top arc AB of the small claw rotor and the second claw bottom arc AB of the large claw rotor start to mesh is defined as the moment when the rotor angle is 0 degrees, the small claw working cavity is communicated with the air suction port to perform the air suction process, and meanwhile, the large claw working cavity in the previous period performs the compression process; when the rotor rotates from 0 degree to 47 degrees, the volume of the small claw working cavity is gradually increased and is divided into two independent working cavities, namely a large claw working cavity and a small claw working cavity; when the rotor rotates from 47 degrees to 78 degrees, the air suction process of the small claw working cavity is finished, the equal-volume conveying process is carried out, meanwhile, the air suction process of the left large claw working cavity is carried out, and the compression process of the right large claw working cavity is carried out; when the rotor rotates from 78 degrees to 203 degrees, gas in the constant-volume conveying process of the small claw working cavity is mixed with gas in the compression process of the large claw working cavity on the right side to form a new mixed working cavity for the mixed compression process; when the rotor rotates from 203 degrees to 360 degrees, when the outer contour of the small claw rotor is superposed with the right end point of the exhaust port, the mixing working chamber is communicated with the minimum exhaust volume before the exhaust port, and then the exhaust port is opened to exhaust all compressed gas.

The invention has the beneficial effects that:

the claw type compressor has three working processes of air suction, compression and air exhaust of the traditional compressor, and also has a unique mixed pressurization process.

Secondly, the claw type compressor adopts a point and cycloid meshing mode during exhaust, and meanwhile, an exhaust port is arranged at a proper position, so that the clearance volume of the compressor is completely eliminated, and the power consumption is saved.

The molded lines of the small claw rotor and the large claw rotor of the claw type compressor are simple to form and convenient to process and manufacture.

The claw type compressor adopts the asymmetrical distribution mode of the small claw rotor and the large claw rotor, so that the load of the synchronous gear connected with the small claw rotor is reduced under the condition of the same air suction amount and pressure removal.

The claw type compressor enriches the types of the rotor molded lines of the claw type compressor.

Drawings

Fig. 1 is a line drawing of a claw rotor (1) of a claw type compressor.

Fig. 2 is a line drawing of a large claw rotor (2) of a claw type compressor.

Fig. 3 is a schematic view of the engagement of the small claw rotor (1) and the large claw rotor (2) of the claw type compressor.

Fig. 4 is a schematic view of the operation of the small jaw rotor (1) at 0 °.

Fig. 5 is a schematic working process diagram of the constant volume conveying process started when the claw rotor (1) is at 47 degrees.

Fig. 6 is a schematic working process diagram of the constant volume conveying process when the small claw rotor (1) rotates from 47 degrees to 78 degrees.

Fig. 7 is a schematic diagram of the operation of the mixing process when the claw rotor (1) rotates from 78 ° to 203 °.

Fig. 8 is a schematic view of the operation of starting the exhaust process when the claw rotor (1) is at 203 °.

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

Fig. 10 is a schematic view of the operation process in which the exhaust process is finished when the claw rotor (1) rotates from 203 ° to 360 °.

Fig. 11 is a partially enlarged view of the opening position of the claw type compressor discharge port (402).

Fig. 12 is a view of the main components of a claw type compressor.

Fig. 13 is a detail view of the rear end cover (4) of a claw type compressor.

In the figure: r₁-the radius of the first jaw tip arc ab of the small jaw rotor (1); r₂-pitch circle radius; r₃-radius of the first claw base arc cd of the claw rotor (1); r₄-radius of the second claw top arc CD of the large claw rotor (2); r₅The radius of a second claw bottom arc AB of the large claw rotor (2); 101-small claw working chamber (101); 201-big claw working chamber (201); 102-a mixing working chamber (102); 1-small claw rotor (1); 2-big claw rotor (2); 3-a cylinder (3); 4-rear end cap (4); 5-front end cover (5); 401-suction inlet (401); 402-exhaust port (402).

Detailed Description

The invention will be further explained with reference to the drawings.

As shown in fig. 1, a profile of a claw rotor 1 of a claw type compressor is shown, and an end face profile of the claw rotor 1 includes: 2 sections of circular arcs, 1 section of cycloids and 1 section of variable speed spiral, which are sequentially arranged in the anticlockwise direction: a first claw top circular arc ab, a speed change spiral bc, a first claw bottom circular arc cd and a first cycloid da; establishing a coordinate system O₁xy，O₁Is the origin; the equation of the first claw top arc ab, the first claw bottom arc cd and the pitch circle of the small claw rotor 1 is as follows:

the equation for the first jaw tip arc ab is:

the equation for the first paw bottom arc cd is:

the equation for the pitch circle is:

the method comprises the following steps: t-is the angle parameter, rad; r₁Is-smallThe radius of a first claw top arc of the claw rotor 1 is mm; r₂-is pitch circle radius, mm; r₃The radius of a first claw bottom arc of the small claw rotor 1 is mm;

the equation of the first cycloid da and the variable speed spiral bc of the small-jaw rotor 1 is as follows:

the equation for the first cycloid da is:

the equation for the shift spiral bc is:

the method comprises the following steps: r₄The radius of the arc of the second claw top of the large claw rotor 2 is mm; theta-is the central angle of the variable speed spiral.

As shown in fig. 2, a profile of a large claw rotor 2 of a claw type compressor is shown, and an end face profile of the large claw rotor 2 comprises: the conjugate curves of 2 sections of circular arcs, 1 section of cycloids and 1 section of variable speed spiral are as follows according to the clockwise direction: a second claw bottom arc AB, a conjugate curve BC of the variable speed spiral, a second claw top arc CD and a second cycloid DA; establishing a coordinate system O₂xy，O₂Is the origin; the second claw bottom arc AB, the second claw top arc CD and the pitch circle of the large claw rotor 2 have the following equations:

the equation for the second paw bottom arc AB is:

the equation for the second jaw tip arc CD is:

the equation for the pitch circle is:

the method comprises the following steps: t-is the angle parameter, rad; r₂-is pitch circle radius, mm; r₄The radius of the arc of the second claw top of the large claw rotor 2 is mm; r₅The radius of a second claw bottom arc of the large claw rotor 2 is mm;

the first cycloid DA of the big claw rotor (2) and the conjugate curve BC of the variable speed spiral have the following equations:

the equation for the second cycloid DA is:

the equation for the conjugate curve BC of the variable speed spiral is: r is_BC＝M₁₂·M_bc

In the formula: m₁₂For rotating the transformation matrix, M_bcIn the form of a matrix of the variable speed spiral equation for the claw rotor 1, as follows:

in the formula:

l is the center distance of the two rotors;

the method comprises the following steps: t-angular parameter, rad.

As shown in fig. 3, which is a schematic diagram of the engagement between the small claw rotor 1 and the large claw rotor 2 of the claw type compressor, in the working process of the synchronous counter-rotating movement, the forming line of the small claw rotor 1 and the forming line of the large claw rotor 2 can be correctly engaged, and the engagement relationship is as follows: the first claw top circular arc AB, the speed change spiral BC, the first claw bottom circular arc CD, the first cycloid DA and the first point a in the forming line of the small claw rotor 1 are respectively meshed with the second claw bottom circular arc AB, the conjugate curve BC of the speed change spiral, the second claw top circular arc CD, the second point D and the second cycloid DA in the forming line of the large claw rotor 2.

As shown in fig. 4, it is a schematic diagram of the operation process when the small claw rotor 1 is at 0 °, and when the position shown by the rotor moves, the small claw working chamber 101 communicates with the suction port 401 to continuously suck air.

As shown in fig. 5, which is a schematic view of the working process when the small-jaw rotor 1 starts the isometric transportation process when it is 47 °, the small-jaw working chamber 101 is divided into the small-jaw working chamber 101 and the left large-jaw working chamber 201 along with the rotation of the rotor, the small-jaw working chamber 101 is cut off from the air inlet 401, the small-jaw working chamber 101 realizes the isometric transportation process, the left large-jaw working chamber 201 is communicated with the air inlet 401 to continuously suck air, the air suction is continued until the air inlet 401 is cut off by the large-jaw rotor 2, and the air in the right large-jaw working chamber 201 is continuously compressed.

As shown in fig. 6, which is a schematic diagram of the operation process of the constant volume conveying process when the small claw rotor 1 rotates from 47 ° to 78 °, the gas in the small claw working chamber 101 is conveyed in constant volume to be mixed with the compressed gas in the right large claw working chamber 201, and the volume of the right large claw working chamber 201 is minimized.

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

As shown in fig. 8, which is a schematic view of the operation process of starting the exhaust process when the claw rotor 1 is at 203 °, the outer contour line of the claw rotor 1 coincides with the right end point of the exhaust port 402, and the exhaust port 402 is the minimum exhaust volume before the mixing operation chamber 102 starts to communicate with the exhaust port immediately before opening.

As shown in fig. 9, which 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 is opened to start exhaust, at this time, the large claw working chamber 201 also completes suction, the isochoric conveying process starts, and the newly formed small claw working chamber 101 also continuously sucks air.

As shown in fig. 10, the operation process diagram is the operation process diagram when the exhaust process is finished when the small claw rotor 1 rotates from 203 ° to 360 °, and the compressed gas is completely exhausted from the exhaust port 402.

As shown in fig. 11, a partial enlarged view of the opening position of the exhaust port 402 of the claw type compressor is shown, the opening position of the exhaust port 402 depends on the position where the clearance volume is generated by the last exhaust of the small claw rotor 1 and the large claw rotor 2, the lower end contour straight line of the exhaust port 402 is tangent to the second claw top arc of the large claw rotor 2, and the left end point of the exhaust port 402 is located on the central line connecting the centers of the small claw rotor 1 and the large claw rotor 2, so that the generation of the clearance volume is avoided.

As shown in fig. 12, it is a view of the main components of a claw type compressor, including: the gas-liquid separation device comprises 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 rear end cover 4 is provided with a gas suction port 401 and a gas exhaust port 402, and a gas suction cavity, a constant-volume closed cavity, a compression cavity, a mixed compression cavity and a gas exhaust cavity can be formed in the working process and are respectively used for the processes of gas suction, constant-volume conveying, compression, mixed compression and gas exhaust; the volume of the air suction cavity is gradually increased and is communicated with the air suction port 401 all the time, the volume of the constant-volume closed cavity is unchanged and closed, the volume of the compression cavity is closed and gradually reduced, the volume of the mixed compression cavity is closed and gradually reduced, and the volume of the exhaust cavity is gradually reduced and is communicated with the exhaust port 402 all the time.

As shown in fig. 13, which is a component view of the rear end cover 4 of the claw type compressor, the opening positions and shapes of the suction port 401 and the exhaust port 402 on the rear end cover 4 can be observed, and the principle of opening the suction port 401 is as follows: the upper end point of the air suction port 401 must be higher than the second claw top arc of the large claw rotor 2 to ensure that the small claw working cavity 101 can continuously suck air, and the lower end point of the air suction port 401 must be lower than the first claw top arc of the small claw rotor 1 to ensure that the large claw working cavity 201 can continuously suck air.

Although the embodiments of the present invention have been described with reference to the accompanying drawings, it is not intended to limit the scope of the present invention, and it should be understood by those skilled in the art that various modifications and variations can be made without inventive efforts by those skilled in the art based on the technical solution of the present invention.