A compressor and a compression system

Abstract

This application belongs to the technical field of compressors and provides a compressor and a compression system. The compressor includes: a housing assembly, within which a receiving portion is formed; a rotor assembly, the rotor assembly including a female rotor and a male rotor that mesh with each other, the rotor assembly being located in the receiving portion; and a slider assembly, disposed within the receiving portion, the slider assembly being movable along the radial direction of the rotor assembly to adjust the opening degree of the axial exhaust port and the opening degree of the radial exhaust passage of the compressor. While the compressor can flexibly adjust the compression ratio of the compressor, it also avoids the flow loss of a fixed-size axial exhaust port in the medium and low pressure modes, improves the working efficiency of the compressor, ensures the exhaust pressure, and also ensures the gas flow rate.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and more particularly to a compressor and a compression system. Background Art

[0002] A twin-screw compressor is a rotary positive-displacement compressor composed of two meshing screws, which is widely used in various industrial fields. In the prior art, when it is necessary to adjust the compression ratio of the compressor, the size of the radial exhaust port of the compressor is often changed, and the axial exhaust port is fixed; after testing, in the low-pressure mode of the variable compressor with this structure, there is still flow loss at its axial exhaust port, and the flow rate attenuation reaches 15-22% in the low-pressure mode, restricting its scope of application. Summary of the Invention

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

[0004] One aspect of the present invention provides a compressor, which includes:

[0005] A housing assembly, in which a receiving portion is formed;

[0006] A rotor assembly, which includes a female rotor and a male rotor that mesh with each other, and the rotor assembly is located in the receiving portion; and a slider assembly, which is arranged in the receiving portion, and the slider assembly can move along the radial direction of the rotor assembly to adjust the opening degree of the axial exhaust port and the opening degree of the radial exhaust passage of the compressor.

[0007] In some embodiments of the present application, the receiving portion includes a first receiving portion and a second receiving portion. The first receiving portion is used to receive the rotor assembly, and the second receiving portion is used to receive the slider assembly. The second receiving portion is arranged close to the axial exhaust port and protrudes along the radial direction of the rotor assembly relative to the first receiving portion.

[0008] In some embodiments of the present application, the slider assembly includes a radial slider assembly and an axial stop block assembly. The radial slider assembly is used to adjust the opening degree of the radial exhaust passage of the compressor, and the axial stop block assembly is used to adjust the opening degree of the axial exhaust port of the compressor.

[0009] In some embodiments of the present application, the radial slider assembly includes a first radial slider and a second radial slider that are separately arranged;

[0010] The surface of the first radial slider forms a female low-pressure radial exhaust spiral and a male low-pressure radial exhaust spiral derived from the low-pressure exhaust angle, a first female medium-pressure radial exhaust spiral and a first male medium-pressure radial exhaust spiral derived from the medium-pressure exhaust angle. The lead and helix direction of the female low-pressure radial exhaust spiral and the first female medium-pressure radial exhaust spiral are consistent with the lead and helix direction of the female rotor, and the lead and helix direction of the male low-pressure radial exhaust spiral and the first male medium-pressure radial exhaust spiral are consistent with the lead and helix direction of the male rotor.

[0011] The surface of the second radial slider forms a second female medium-pressure radial exhaust spiral and a second male medium-pressure radial exhaust spiral derived from the medium-pressure exhaust angle, a female high-pressure radial exhaust spiral and a male high-pressure radial exhaust spiral derived from the high-pressure exhaust angle. The lead and helix direction of the second female medium-pressure radial exhaust spiral and the female high-pressure radial exhaust spiral are consistent with the lead and helix direction of the female rotor, and the lead and helix direction of the second male medium-pressure radial exhaust spiral and the male high-pressure radial exhaust spiral are consistent with the lead and helix direction of the male rotor.

[0012] In some embodiments of the present application, the axial stop assembly further includes a first axial female stop, a first axial male stop, and a third axial stop. The first axial female stop and the first axial male stop are fixedly connected to the first radial slider through fasteners, and the third axial stop is fixedly connected to the second radial slider through fasteners.

[0013] In some embodiments of the present application, the first axial female stop is provided with a first dynamic sealing surface matching the root circle contour of the female rotor, the first axial male stop is provided with a second dynamic sealing surface matching the root circle contour of the male rotor, and the third axial stop is provided with a third dynamic sealing surface matching the root circle contour of the male rotor.

[0014] In some embodiments of the present application, along the length direction of the third axial stop, at the position corresponding to the high-pressure exhaust angle, the third axial stop is provided with a female rotor projection edge matching the contour of the female rotor and a male rotor projection edge matching the contour of the male rotor.

[0015] In some embodiments of the present application, the housing assembly includes a cylinder block and an end cover. The axial exhaust port is arranged on the end cover. The end cover is provided with a guiding groove, which is recessed along the thickness direction of the end cover. The guiding groove is used to limit the movement trajectories of the first axial female stop, the first axial male stop, and the third axial stop in the radial direction of the rotor assembly.

[0016] In some embodiments of the present application, the end cover is provided with a first curved edge matching the root circle contour of the female rotor, a second curved edge matching the tip circle contour of the female rotor, a third curved edge matching the root circle contour of the male rotor, and a fourth curved edge matching the tip circle contour of the male rotor, and the axial exhaust port is formed between the first curved edge, the second curved edge, the third curved edge and the fourth curved edge.

[0017] In some embodiments of the present application, the end cover is further provided with auxiliary exhaust holes, and the auxiliary exhaust holes are communicated with the radial exhaust passage of the compressor.

[0018] In some embodiments of the present application, the end cover is provided with a fifth curved edge and a sixth curved edge matching the meshing conjugate line contour of the female rotor and the male rotor, and the first curved edge, the fifth curved edge, the sixth curved edge and the third curved edge are connected in sequence.

[0019] In some embodiments of the present application, the slider assembly has the following position states:

[0020] The first position, the opening degree of the axial exhaust port is S1, and the opening degree of the radial exhaust passage of the compressor is M1;

[0021] The second position, the opening degree of the axial exhaust port is S2, and the opening degree of the radial exhaust passage of the compressor is M2;

[0022] The third position, the opening degree of the axial exhaust port is S3, and the opening degree of the radial exhaust passage of the compressor is M3;

[0023] Wherein, S1 < S2 < S3, M1 < M2 < M3.

[0024] In some embodiments of the present application, when the slider assembly is in the first position, the first dynamic sealing surface fits with the first curved edge, the second dynamic sealing surface fits with the third curved edge, and the third dynamic sealing surface fits with the third curved edge; the first female medium-pressure radial exhaust spiral line fits with the second female medium-pressure radial exhaust spiral line, and the first male medium-pressure radial exhaust spiral line and the second male medium-pressure radial exhaust spiral line fit; the female low-pressure radial exhaust spiral line, the first female medium-pressure radial exhaust spiral line, the male low-pressure radial exhaust spiral line, and the first male medium-pressure radial exhaust spiral line all fit with the exhaust spiral line of the cylinder block;

[0025] When the slider assembly is in the second position, the first dynamic sealing surface fits with the first curved edge, the second dynamic sealing surface fits with the third curved edge, and the third dynamic sealing surface separates from the third curved edge and is located below the third curved edge; the first female medium-pressure radial exhaust spiral separates from the second female medium-pressure radial exhaust spiral, and the first male medium-pressure radial exhaust spiral separates from the second male medium-pressure radial exhaust spiral; the female low-pressure radial exhaust spiral, the first female medium-pressure radial exhaust spiral, the male low-pressure radial exhaust spiral, and the first male medium-pressure radial exhaust spiral all fit with the exhaust spiral of the cylinder block;

[0026] When the slider assembly is in the third position, the first dynamic sealing surface separates from the first curved edge and is located below the first curved edge, the second dynamic sealing surface separates from the third curved edge and is located below the third curved edge, and the third dynamic sealing surface separates from the third curved edge and is located below the third curved edge; the female low-pressure radial exhaust spiral and the male low-pressure radial exhaust spiral both separate from the exhaust spiral of the cylinder block.

[0027] The second aspect of the present application further provides a compression system, which includes the compressor described above.

[0028] By providing a slider assembly in the present invention, the slider assembly can move along the radial direction of the rotor assembly. In the radial direction of the rotor assembly, by changing the position of the slider assembly relative to the rotor assembly, the sizes of the axial exhaust port and the radial exhaust passage of the compressor are simultaneously changed. While the compressor can flexibly adjust the compression ratio of the compressor, it also avoids the flow loss of the fixed-size axial exhaust port in the medium-low pressure mode, improves the working efficiency of the compressor, ensures the exhaust pressure, and also ensures the gas flow rate. Description of the Drawings

[0029] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following will briefly introduce the drawings required for use in the embodiments of the present invention or the description of the prior art. Obviously, the following described drawings are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings.

[0030] Figure 1 is a schematic structural diagram of the compressor shown in some embodiments of the present invention;

[0031] Figure 2 is Figure 1 a partial structural explosion diagram of the compressor shown in;

[0032] Figure 3 is Figure 1Schematic diagram of the cylinder block structure of the compressor shown;

[0033] Figure 4 It is a schematic diagram of the structure of the slider assembly shown in some embodiments of the present invention;

[0034] Figure 5 It is a schematic diagram of the structures of the first radial slider, the first axial blocking block, and the first axial male blocking block shown in some embodiments of the present invention;

[0035] Figure 6 Is Figure 5 The front view of the first radial slider in;

[0036] Figure 7 Is Figure 5 The top view of the first radial slider in;

[0037] Figure 8 Is Figure 5 The front view of the first axial blocking block in;

[0038] Figure 9 Is Figure 5 The front view of the first axial male blocking block in;

[0039] Figure 10 It is a schematic diagram of the structures of the second radial slider and the third axial blocking block shown in some embodiments of the present invention;

[0040] Figure 11 Is Figure 10 The front view of the second radial slider in;

[0041] Figure 12 Is Figure 10 The top view of the second radial slider in;

[0042] Figure 13 Is Figure 10 The front view of the third axial blocking block in;

[0043] Figure 14 It is a schematic diagram of the structure of the end cover shown in some embodiments of the present invention;

[0044] Figure 15 Is Figure 14 The front view of the end cover shown;

[0045] Figure 16 It is a schematic diagram of the position of the slider assembly when the compressor is in the high-pressure exhaust mode in some embodiments of the present invention;

[0046] Figure 17 It is a schematic diagram of the position of the slider assembly when the compressor is in the medium-pressure exhaust mode in some embodiments of the present invention;

[0047] Figure 18It is a schematic diagram of the position of the slider assembly when the compressor is in the low-pressure exhaust mode in some embodiments of the present invention. Detailed implementation manners

[0048] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0049] The terms "first" and "second" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise stated, the meaning of "a plurality" is two or more.

[0050] In the description of this specification, specific features, structures, materials, or characteristics may be combined in a suitable manner in any one or more embodiments or examples.

[0051] The twin-screw compressor is a rotary positive-displacement compressor. Its core components are a pair of meshing male and female rotors. The driving motor is connected to the male rotor, and the female rotor rotates passively. The two rotors are parallelly installed in a precisely fitted housing, and the compression of gas is achieved by using the volume change of the rotor meshing to continuously output high-pressure gas. Twin-screw compressors are widely used in various industrial fields. In the prior art, when it is necessary to adjust the compression ratio of a twin-screw compressor, a slide valve structure is often set. This slide valve structure can move along the axial direction of the compressor. By changing the position of the slide valve structure in the axial direction of the rotor assembly, the size of the radial exhaust port of the compressor is further changed, thereby realizing the adjustment of the compression ratio of the compressor. However, for this variable-compression-ratio compressor, the size of its axial exhaust port is fixed. After testing, in the low-pressure mode, there is still flow loss at its axial exhaust port, and the flow rate attenuation reaches 15-22% in the low-pressure mode, restricting its scope of application.

[0052] In view of this, to solve the above problems, in combination with Figures 1 to 18 As shown, the present application proposes a compressor, which includes:

[0053] A housing assembly 1, in which a receiving portion is formed;

[0054] The rotor assembly 3, the rotor assembly 3 includes a female rotor 31 and a male rotor 32 that mesh with each other, and the rotor assembly 3 is located in the accommodating portion; and the slider assembly 2 is disposed in the accommodating portion, and the slider assembly 2 can move along the radial direction of the rotor assembly 3 to adjust the opening degree of the axial exhaust port 123 and the opening degree of the radial exhaust passage of the compressor.

[0055] Specifically, as Figure 1 and Figure 2 shown, it is an overall schematic diagram of the compressor in some embodiments of the present application. The rotor assembly 3 is disposed in the housing assembly 1. An air inlet 111 is formed above the housing assembly 1. The air inlet 111 extends along the radial direction of the rotor and communicates with the accommodating portion in the housing assembly 1 for introducing the gas to be compressed into the compressor. The slider assembly 2 is also accommodated in the accommodating portion formed by the housing assembly 1 and is located on one side of the accommodating portion close to the axial exhaust port 123 of the compressor.

[0056] As Figure 1 、 Figure 2 、 Figures 16 to 18 shown, Figures 16 to 18 the up and down direction in Figures 16 to 18 is the radial direction of the rotor assembly 3, and the slider assembly 2 can move along the up and down direction in

[0057] In some embodiments of the present application, as Figure 3As shown, the accommodating part includes a first accommodating part 112 and a second accommodating part 113. The first accommodating part 112 is used to accommodate the rotor assembly 3, and the second accommodating part 113 is used to accommodate the slider assembly 2. The second accommodating part 113 is arranged near the axial exhaust port 123 of the compressor. Relative to the first accommodating part 112, the second accommodating part 113 protrudes along the radial direction of the rotor assembly 3. In this solution, only local adjustment of the structure of the cylinder block on one side of the housing assembly 1 near the exhaust end of the compressor is required, so as to provide a moving space for the radial movement of the slider assembly 2 relative to the rotor assembly 3, and realize the adjustment of the compression ratio of the compressor. Compared with the prior art, the structure of the solution described in this embodiment is simpler, and the overall volume of the compressor is smaller.

[0058] Further, the bottom surface of the second accommodating part 113 is a plane. Such a setting can provide greater convenience for the installation of the compressor and improve the installation stability of the compressor on industrial equipment.

[0059] In some embodiments of the present application, the slider assembly 2 includes a radial slider assembly and an axial stop block assembly. The radial slider assembly is used to adjust the opening degree of the radial exhaust passage of the compressor, and the axial stop block assembly is used to adjust the opening degree of the axial exhaust port 123 of the compressor.

[0060] Specifically, when the radial slider assembly moves away from the rotor assembly 3, the internal compression volume of the compressor gradually increases, and the radial exhaust passage of the compressor also becomes larger, so that the internal compression volume of the compressor gradually switches from the high-pressure exhaust volume to the medium-pressure exhaust volume and the low-pressure exhaust volume; when the radial slider assembly approaches the rotor assembly 3, the internal compression volume of the compressor gradually decreases, and the radial exhaust passage of the compressor also becomes smaller, so that the internal compression volume of the compressor gradually switches from the low-pressure exhaust volume to the medium-pressure exhaust volume and the high-pressure exhaust volume.

[0061] Further, by adjusting the position of the axial stop block assembly relative to the axial exhaust port 123 of the compressor, and then changing the opening degree of the axial exhaust port 123, when the compression volume in the compressor changes, the follow-up adjustment of the axial exhaust port 123 can avoid the flow loss caused by the axial exhaust port 123 in the low-pressure mode and improve the working efficiency of the compressor.

[0062] In some embodiments of the present application, as Figure 4 shown, the radial slider assembly includes a first radial slider 21 and a second radial slider 22 which are separately arranged; by separately arranging the first radial slider 21 and the second radial slider 22, during use, the position of the first radial slider 21 can be adjusted independently according to requirements, the position of the second radial slider 22 can also be adjusted independently, or the positions of the first radial slider 21 and the second radial slider 22 can be adjusted simultaneously, so that the adjustment range of the internal compression volume of the compressor is larger, and the adjustment range of the compression ratio of the compressor is improved.

[0063] Further, as Figures 5 to 7 shown, based on the center distance A between the female rotor 31 and the male rotor 32, and the tip circles of the female rotor 31 and the male rotor 32, the female low-pressure exhaust angle, male low-pressure exhaust angle, female medium-pressure exhaust angle, and male medium-pressure exhaust angle of the female rotor 31 and the male rotor 32 are calculated; respectively starting from the female low-pressure exhaust angle and male low-pressure exhaust angle of the female rotor 31 and the male rotor 32 as the starting points of the helical lines, and the lead is consistent with the leads of the female rotor 31 and the male rotor 32, and the helix directions are the same as the rotation directions of the female rotor 31 and the male rotor 32 respectively, a female low-pressure radial exhaust helical line L1 derived from the female low-pressure exhaust angle and a male low-pressure radial exhaust helical line L3 derived from the male low-pressure exhaust angle are formed on the surface of the first radial slider 21; then respectively starting from the female medium-pressure exhaust angle and male medium-pressure exhaust angle of the female rotor 31 and the male rotor 32 as the starting points of the helical lines, and the lead is consistent with the leads of the female rotor 31 and the male rotor 32, and the helix directions are the same as the rotation directions of the female rotor 31 and the male rotor 32 respectively, a first female medium-pressure radial exhaust helical line L2 derived from the female medium-pressure exhaust angle and a first male medium-pressure radial exhaust helical line L4 derived from the male medium-pressure exhaust angle are formed on the surface of the first radial slider 21.

[0064] Further, as Figures 10 to 12 shown, based on the center distance A between the female rotor 31 and the male rotor 32, and the tip circles of the female rotor 31 and the male rotor 32, the female medium-pressure exhaust angle, male medium-pressure exhaust angle, female high-pressure exhaust angle, and male high-pressure exhaust angle of the female rotor 31 and the male rotor 32 are calculated. Respectively starting from the female medium-pressure exhaust angle and male medium-pressure exhaust angle of the female rotor 31 and the male rotor 32 as the starting points of the helical lines, and the lead is consistent with the leads of the female rotor 31 and the male rotor 32, and the helix directions are the same as the rotation directions of the female rotor 31 and the male rotor 32 respectively, a second female medium-pressure radial exhaust helical line L5 derived from the female medium-pressure exhaust angle and a second male medium-pressure radial exhaust helical line L7 derived from the male medium-pressure exhaust angle are formed on the surface of the second radial slider 22. Then starting from the female high-pressure exhaust angle and male high-pressure exhaust angle of the female rotor 31 and the male rotor 31 as the starting points of the helical lines, and the lead is consistent with the leads of the female rotor 31 and the male rotor 32, and the helix directions are the same as the rotation directions of the female rotor 31 and the male rotor 32 respectively, a female high-pressure radial exhaust helical line L6 derived from the female high-pressure exhaust angle and a male high-pressure radial exhaust helical line L8 derived from the male high-pressure exhaust angle are formed on the surface of the second radial slider 22.

[0065] In some embodiments of the present application, as Figures 4 to 13As shown, the axial stop assembly includes a first axial female stop 23, a first axial male stop 25, and a third axial stop 24. The first axial female stop 23 and the first axial male stop 25 are fixedly connected to the first radial slider 21 by fasteners, so that the first axial male stop 25 and the first axial female stop 23 can move along with the movement of the first radial slider 21; the third axial stop 24 is fixedly connected to the second radial slider 22 by fasteners, so that the third axial stop 24 can move along with the movement of the second radial slider 22; by fixedly connecting the axial stop and the radial slider, when the slider assembly 2 moves in the radial direction of the rotor assembly 3, the linkage adjustment of the opening degree of the radial exhaust passage and the opening degree of the axial exhaust port 123 of the compressor can be realized.

[0066] Further, as Figure 5 and Figure 8 shown, taking the female rotor 31 as the center, the female low-pressure exhaust angle and the female medium-pressure exhaust angle of the female rotor 31 are calculated based on the root circle and the tip circle of the female rotor 31, and a first dynamic sealing surface 231 matching the root circle contour of the female rotor 31 is provided on the first axial female stop 23.

[0067] Further, as Figure 5 and Figure 9 shown, taking the male rotor 32 as the center, the male low-pressure exhaust angle and the male medium-pressure exhaust angle of the male rotor 32 are calculated based on the root circle and the tip circle of the male rotor 32, and a second dynamic sealing surface 251 matching the root circle contour of the male rotor 32 is provided on the first axial male stop 25.

[0068] Further, as Figure 10 and Figure 13 shown, based on the center distance A between the female rotor 31 and the male rotor 32, the tip circle and the root circle of the female rotor 31, and the tip circle and the root circle of the male rotor 32, the female medium-pressure exhaust angle, the female high-pressure exhaust angle, the male medium-pressure exhaust angle, and the male high-pressure exhaust angle of the female rotor 31 are calculated; and a third dynamic sealing surface 241 matching the root circle contour of the male rotor 32 is provided on the third axial stop 24.

[0069] In some embodiments of the present application, as Figure 13 shown, Figure 13The left - right direction therein is the length direction of the third axial stop 24. Along the length direction of the third axial stop 24, corresponding to the positions of the high - pressure exhaust angles of the female rotor 31 and the male rotor 32, the third axial stop 24 is provided with a female - rotor projection edge 242 matching the contour of the female rotor 31 and a male - rotor projection edge 243 matching the contour of the male rotor 32. This can optimize the flow rate of the high - pressure exhaust port. When the gas is compressed to the pressure of the required internal volume, the shape of the projection line of the air outlet is blocked and hollowed out. In order to reduce the gas flow rate, reduce the pressure loss caused by being blocked during gas discharge, reduce the gas flow power consumption, and improve economic efficiency.

[0070] In some embodiments of the present application, such as Figure 2 、 Figure 14 and Figure 15 shown, the housing assembly includes a cylinder block 11 and an end cover 12. The axial exhaust port 123 is arranged on the end cover 12. The end cover 12 is provided with a guiding groove 121. The guiding groove 121 is recessed along the thickness direction of the end cover. The guiding groove 121 is used to limit the movement trajectories of the first axial female stop 23, the first axial male stop 25, and the third axial stop 24 in the radial direction of the rotor assembly 3.

[0071] In some embodiments of the present application, such as Figure 14 、 Figure 15 shown, based on the center distance A between the female rotor 31 and the male rotor 32, the tip circle and root circle of the female rotor 31, and the tip circle and root circle of the male rotor 32, the female medium - pressure exhaust angle sum, female high - pressure exhaust angle, male medium - pressure exhaust angle, and male high - pressure exhaust angle of the female rotor 31 are calculated; and on the end cover 12, there are a first curved edge B1 matching the contour of the root circle of the female rotor 31, a second curved edge B2 matching the contour of the tip circle of the female rotor 31, a third curved edge B3 matching the contour of the root circle of the male rotor 32, and a fourth curved edge B4 matching the contour of the tip circle of the male rotor 32. The axial exhaust port 123 is formed between the first curved edge B1, the second curved edge B2, the third curved edge B3, and the fourth curved edge B4.

[0072] In some embodiments of the present application, such as Figure 14 and Figure 15 shown, the end cover 12 is further provided with auxiliary exhaust holes 122. The auxiliary exhaust holes 122 are communicated with the radial exhaust passage of the compressor. Specifically, there can be multiple auxiliary exhaust holes 122, and the multiple auxiliary exhaust holes 122 are arranged at intervals. There is no limit to the shape of the auxiliary exhaust holes 122, which can be square, circular, or other shapes. When the compressor is in the low - pressure exhaust state or the medium - pressure exhaust state, the auxiliary exhaust holes 122 are used for auxiliary exhaust of the gas discharged from the radial exhaust passage.

[0073] In some embodiments of the present application, the end cap 12 is provided with a fifth curved edge B5 and a sixth curved edge B6 that match the conjugate line profiles of the meshing of the female rotor 31 and the male rotor 32. The first curved edge B1, the fifth curved edge B5, the sixth curved edge B6, and the third curved edge B3 are connected in sequence, so as to isolate the intake port 111 of the compressor from the exhaust end.

[0074] In some embodiments of the present application, the slider assembly 2 has the following position states:

[0075] The first position, as Figure 16 shown, the opening degree of the axial exhaust port 123 is S1, and the opening degree of the radial exhaust passage of the compressor is M1;

[0076] The second position, as Figure 17 shown, the opening degree of the axial exhaust port 123 is S2, and the opening degree of the radial exhaust passage of the compressor is M2;

[0077] The third position, as Figure 18 shown, the opening degree of the axial exhaust port 123 is S3, and the opening degree of the radial exhaust passage of the compressor is M3;

[0078] Wherein, S1 < S2 < S3, and M1 < M2 < M3.

[0079] In some embodiments of the present application, as Figure 16 shown, when the slider assembly 2 is in the first position, the first dynamic sealing surface 231 of the first axial female blocking block 23 fits with the first curved edge B1, the second dynamic sealing surface 251 of the first axial male blocking block 25 fits with the third curved edge B3, and the third dynamic sealing surface 241 of the third axial blocking block 24 fits with the third curved edge B3; at this time, the opening degree of the axial exhaust port 123 of the compressor is S1, and the axial exhaust port 123 of the compressor forms a high-pressure axial exhaust port 123;

[0080] Further, at the first position, the compressor is in the high-pressure exhaust condition. The first female medium-pressure radial exhaust spiral line L2 of the first radial slider 21 fits with the second female medium-pressure radial exhaust spiral line L5 of the first radial slider 21, and the first male medium-pressure radial exhaust spiral line L4 of the first radial slider 21 fits with the second male medium-pressure radial exhaust spiral line L7 of the second radial slider 22; and the female low-pressure radial exhaust spiral line L1, the first female medium-pressure radial exhaust spiral line L2, the male low-pressure radial exhaust spiral line L3, the first male medium-pressure radial exhaust spiral line L4, the second female medium-pressure radial exhaust spiral line L5, and the second male medium-pressure radial exhaust spiral line L7 of the first radial slider 21 and the second radial slider 22 all fit with the exhaust spiral line inside the cylinder block 11. The opening degree of the radial exhaust passage formed between the rotor assembly 3 and the radial slider is M1; when the slider assembly 2 is in the first position, the female rotor 31 and the male rotor 32 start to exhaust only when rotating to the high-pressure exhaust angle during the compression process, forming a relatively high internal volume compression ratio, so as to obtain a relatively high exhaust pressure.

[0081] Further, as Figure 17 shown, when the slider assembly 2 is in the second position, the compressor is in the medium-pressure exhaust condition. Specifically, the first dynamic sealing surface 231 of the first axial female stop block 23 fits with the first curved edge B1 of the end cover 12, and the second dynamic sealing surface 251 of the first axial male stop block 25 fits with the third curved edge B3 of the end cover 12. The third dynamic sealing surface 241 of the third axial stop block 24 is separated from the third curved edge B3 of the end cover 12 and is located below the third curved edge B3; at this time, the opening degree of the axial exhaust port 123 of the compressor is S2, S2 > S1, and the axial exhaust port 123 of the compressor forms a high-pressure axial exhaust port 123.

[0082] Further, the first radial slider 21 remains stationary, and the second radial slider 22 moves away from the rotor assembly 3. That is, the female low-pressure radial exhaust spiral line L1, the first female medium-pressure radial exhaust spiral line L2, the male low-pressure radial exhaust spiral line L3, and the first male medium-pressure radial exhaust spiral line L4 of the first radial slider 21 still fit with the exhaust spiral line of the cylinder block 11. As the second radial slider 22 moves away from the rotor assembly 3, the second female medium-pressure radial exhaust spiral line L5 of the second radial slider 22 separates from the first female medium-pressure radial exhaust spiral line L2 of the first radial slider 21, and the second male medium-pressure radial exhaust spiral line L7 of the second radial slider 22 separates from the first male medium-pressure radial exhaust spiral line L4 of the first radial slider 21. That is, the second male medium-pressure radial exhaust spiral line L7 of the second radial slider 22 also separates from the exhaust spiral line of the cylinder block. Compared with the first position, the position of the second radial slider 22 moves downward, increasing the opening degree of the radial exhaust passage between the rotor assembly 3 and the slider assembly 2. At this time, the opening degree of the radial exhaust passage formed between the rotor assembly 3 and the radial slider is M2, and M2 > M1. When the slider assembly 2 is in the second position, the male rotor 31 and the female rotor 32 start to exhaust when rotating to the medium-pressure exhaust angle during the compression process, forming a medium-pressure internal volume compression ratio, thereby obtaining a medium-pressure exhaust pressure.

[0083] Further, as Figure 18 shown, when the slider assembly 2 is in the third position, the compressor is in the low-pressure exhaust working condition. Specifically, the first axial female baffle 23 is moved away from the rotor assembly 3, so that the first dynamic sealing surface 231 of the first axial female baffle 23 separates from the first curved edge B1 of the end cover 12 and is located below the first curved edge B1 of the end cover 12, and the second dynamic sealing surface 251 of the first axial male baffle 25 separates from the third curved edge B3 of the end cover 12 and is located below the third curved edge B3, and the third dynamic sealing surface 241 separates from the third curved edge B3 and is located below the third curved edge B3; at this time, the opening degree of the axial exhaust port 123 of the compressor is S3, S3 > S2, and the axial exhaust port 123 of the compressor forms a low-pressure axial exhaust port 123.

[0084] Further, the first radial slider 21 also moves away from the rotor assembly 3, so that the female low-pressure radial exhaust spiral line L1 and the male low-pressure radial exhaust spiral line L3 of the first radial slider 21 both separate from the exhaust spiral line of the cylinder block 11; compared with the second position, the position of the first radial slider 21 moves downward, further increasing the opening degree of the radial exhaust passage between the rotor assembly 3 and the radial slider. At this time, the opening degree of the radial exhaust passage formed between the rotor assembly 3, the radial slider, and the radial slider is M3, M3 > M2 > M1; the male rotor 31 and the female rotor 32 start to exhaust when rotating to the low-pressure exhaust angle during the compression process, forming a low-pressure internal volume compression ratio, thereby obtaining a low-pressure exhaust pressure.

[0085] The second aspect of the present application also provides a compression system, which includes the aforementioned compressor. The compression system can be a blower, an air compressor, a refrigeration compressor, a process gas compressor, a heat pump, a vacuum pump, a steam compressor, etc. Of course, the compression system protected by the second aspect of the present application is not limited to the categories listed above. If the compressor described in the present application is configured in other systems, it also belongs to the scope protected by the present application.

[0086] In the present application, a slider assembly 2 that can move in the radial direction of the rotor assembly 3 is provided inside the compressor. When the slider assembly 2 approaches or moves away from the rotor assembly 3, the opening degree of the radial exhaust passage between the rotor assembly 3 and the slider assembly 2 changes, thereby changing the compression ratio of the compressor. Further, when the slider assembly 2 moves in the radial direction of the rotor assembly 3, the opening degree of the axial exhaust port 123 of the compressor will be further changed. That is, when the slider assembly 2 moves in the radial direction of the rotor assembly 3, it can simultaneously change the opening degree of the radial exhaust passage between the rotor assembly 3 and the slider assembly 2 and the opening degree of the axial exhaust port 123 of the compressor. During use, the position of the slider assembly 2 can be adjusted adaptively according to requirements to adjust the compression ratio of the compressor, so that the internal compression volume of the compressor can be switched between the low-pressure exhaust volume, the medium-pressure exhaust volume, and the high-pressure exhaust volume to achieve the change of the compression ratio of the compression type, making the application range of the compressor wider. Compared with the prior art in which only the size of the radial exhaust passage is adjusted, when the slider assembly 2 in the solution described in the present application moves in the radial direction of the rotor assembly 3, it can simultaneously adjust the size of the radial exhaust passage and the axial exhaust port 123 of the compressor. While flexibly adjusting the compression ratio of the compressor, it also avoids the flow loss of the fixed-size axial exhaust port 123 in the medium and low-pressure modes, improves the working efficiency of the compressor, and ensures the exhaust pressure while also ensuring the gas flow rate.

[0087] Optionally, during use, the following modes can be adopted for operation:

[0088] Light-load start-up operation: When the equipment is just started, the compressor can be adjusted to a low-pressure state, the internal volume compression ratio is relatively low, and the motor drive power is also relatively small, saving power consumption.

[0089] Loading operation: When the equipment is running to pressurize the pressure vessel, the position of the slider assembly 2 can be adjusted to change the compression ratio of the compressor, so as to achieve synchronous pressurization of the exhaust pressure of the compressor and the pressure vessel, avoiding situations such as overpressure and underpressure power consumption in the operating conditions of the compressor, and saving energy.

[0090] Temperature control: Especially in the steam compressor industry, when the suction at a relatively low temperature is required for high-temperature exhaust conditions, the slider assembly 2 is adjusted to the high-pressure exhaust state; high-pressure and high-temperature gases can be obtained to improve efficiency. During the steam compression operation, for the overheating phenomenon generated, the slider assembly 2 can be adjusted to the low-pressure exhaust port state to relieve the generation of compression heat.

[0091] Those of ordinary skill in the art can understand that the above embodiments are specific embodiments for implementing the present invention, and in actual applications, various changes can be made in form and details without departing from the spirit and scope of the present invention.

Claims

1. A compressor, characterized in that, including a housing assembly, in which a receiving portion is formed; a rotor assembly, which includes a female rotor and a male rotor that mesh with each other, and the rotor assembly is located in the receiving portion; and a slider assembly, which is arranged in the receiving portion and can move along the radial direction of the rotor assembly to adjust the opening degree of the axial exhaust port and the opening degree of the radial exhaust passage of the compressor; the receiving portion includes a first receiving portion and a second receiving portion. The first receiving portion is used to receive the rotor assembly, and the second receiving portion is used to receive the slider assembly. The second receiving portion is arranged close to the axial exhaust port and protrudes along the radial direction of the rotor assembly relative to the first receiving portion; the slider assembly includes a radial slider assembly and an axial stop block assembly. The radial slider assembly is used to adjust the opening degree of the radial exhaust passage of the compressor, and the axial stop block assembly is used to adjust the opening degree of the axial exhaust port; the radial slider assembly includes a first radial slider and a second radial slider that are separately arranged; on the surface of the first radial slider, there are formed a female low-pressure radial exhaust spiral line and a male low-pressure radial exhaust spiral line derived from the low-pressure exhaust angle, a first female medium-pressure radial exhaust spiral line and a first male medium-pressure radial exhaust spiral line derived from the medium-pressure exhaust angle. The lead and helix direction of the female low-pressure radial exhaust spiral line and the first female medium-pressure radial exhaust spiral line are the same as those of the female rotor, and the lead and helix direction of the male low-pressure radial exhaust spiral line and the first male medium-pressure radial exhaust spiral line are the same as those of the male rotor; on the surface of the second radial slider, there are formed a second female medium-pressure radial exhaust spiral line and a second male medium-pressure radial exhaust spiral line derived from the medium-pressure exhaust angle, a female high-pressure radial exhaust spiral line and a male high-pressure radial exhaust spiral line derived from the high-pressure exhaust angle. The lead and helix direction of the second female medium-pressure radial exhaust spiral line and the female high-pressure radial exhaust spiral line are the same as those of the female rotor, and the lead and helix direction of the second male medium-pressure radial exhaust spiral line and the male high-pressure radial exhaust spiral line are the same as those of the male rotor; the axial stop block assembly further includes a first axial female stop block, a first axial male stop block and a third axial stop block. The first axial female stop block and the first axial male stop block are fixedly connected to the first radial slider through fasteners, and the third axial stop block is fixedly connected to the second radial slider through fasteners; on the first axial female stop block, there is a first dynamic sealing surface that matches the tooth root circle contour of the female rotor. On the first axial male stop block, there is a second dynamic sealing surface that matches the tooth root circle contour of the male rotor. On the third axial stop block, there is a third dynamic sealing surface that matches the tooth root circle contour of the male rotor.

2. The compressor according to claim 1, characterized in that, along the length direction of the third axial stop block, at the position corresponding to the high-pressure exhaust angle, on the third axial stop block, there is a female rotor projection edge that matches the contour of the female rotor, and a male rotor projection edge that matches the contour of the male rotor.

3. The compressor according to claim 1, characterized in that, The housing assembly includes a cylinder block and an end cover. The axial exhaust port is arranged on the end cover. A guiding groove is provided on the end cover and is recessed along the thickness direction of the end cover. The guiding groove is used to limit the movement trajectories of the first axial blocking block, the first axial male blocking block, and the third axial blocking block in the radial direction of the rotor assembly.

4. The compressor according to claim 3, characterized in that, The end cover is provided with a first curved edge matching the root circle contour of the female rotor, a second curved edge matching the tip circle contour of the female rotor, a third curved edge matching the root circle contour of the male rotor, and a fourth curved edge matching the tip circle contour of the male rotor. The axial exhaust port is formed among the first curved edge, the second curved edge, the third curved edge, and the fourth curved edge.

5. The compressor according to claim 3, wherein, An auxiliary exhaust hole is further provided on the end cover, and the auxiliary exhaust hole is communicated with the radial exhaust passage of the compressor.

6. The compressor according to claim 4, characterized in that, The end cover is provided with a fifth curved edge and a sixth curved edge matching the meshing conjugate line contour of the female rotor and the male rotor. The first curved edge, the fifth curved edge, the sixth curved edge, and the third curved edge are connected in sequence.

7. The compressor according to claim 4, characterized in that, The slider assembly has the following position states: The first position, where the opening degree of the axial exhaust port is S1 and the opening degree of the radial exhaust passage of the compressor is M1; The second position, where the opening degree of the axial exhaust port is S2 and the opening degree of the radial exhaust passage of the compressor is M2; The third position, where the opening degree of the axial exhaust port is S3 and the opening degree of the radial exhaust passage of the compressor is M3; wherein, S1 < S2 < S3 and M1 < M2 < M3.

8. The compressor according to claim 7, wherein in the first position, the first dynamic sealing surface is in contact with the first curved edge, the second dynamic sealing surface is in contact with the third curved edge, and the third dynamic sealing surface is in contact with the third curved edge; the first female medium-pressure radial exhaust spiral line is in contact with the second female medium-pressure radial exhaust spiral line, and the first male medium-pressure radial exhaust spiral line and the second male medium-pressure radial exhaust spiral line are in contact; the female low-pressure radial exhaust spiral line, the first female medium-pressure radial exhaust spiral line, the male low-pressure radial exhaust spiral line, and the first male medium-pressure radial exhaust spiral line are all in contact with the exhaust spiral line of the cylinder block; in the second position, the first dynamic sealing surface is in contact with the first curved edge, the second dynamic sealing surface is in contact with the third curved edge, and the third dynamic sealing surface is separated from the third curved edge and is located below the third curved edge; the first female medium-pressure radial exhaust spiral line is separated from the second female medium-pressure radial exhaust spiral line, and the first male medium-pressure radial exhaust spiral and the second male medium-pressure radial exhaust spiral line are separated; the female low-pressure radial exhaust spiral line, the first female medium-pressure radial exhaust spiral line, the male low-pressure radial exhaust spiral line, and the first male medium-pressure radial exhaust spiral line are all in contact with the exhaust spiral line of the cylinder block; At the third position, the first dynamic sealing surface is separated from the first curved edge and is located below the first curved edge, the second dynamic sealing surface is separated from the third curved edge and is located below the third curved edge, and the third dynamic sealing surface is separated from the third curved edge and is located below the third curved edge; both the female low-pressure radial exhaust spiral and the male low-pressure radial exhaust spiral are separated from the exhaust spiral of the cylinder block.

9. A compression system, characterized in that, Comprising the compressor according to any one of claims 1-8.

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