A compressor and a compression system

Abstract

The present invention belongs to the technical field of compressors, and provides a compressor and a compression system. The present application proposes a compressor, which includes a housing. A compression chamber for installing a female rotor and a male rotor is formed in the housing. The compression chamber sequentially includes a suction section, a low-pressure compression chamber section, and a high-pressure compression chamber section along the axial direction of the rotor. A plurality of spray holes are provided on the housing, and all of the plurality of spray holes are located in the low-pressure compression chamber section for spraying a cooling medium into the compression chamber. By optimizing the installation position of the spray holes, the present application designs all the spray holes in the low-pressure compression chamber section of the compression chamber. Since the low-pressure compression chamber section is in the closed section of the compression chamber, the suction volume flow rate of the compressor can be guaranteed, and the ambient pressure during the suction process of the suction volume of each tooth space is not affected by the spray holes. At the same time, the pressure in the low-pressure compression chamber section is relatively low, and the driving power load of the pump for spraying the cooling medium is minimized, reducing the driving power of the compressor, which is energy-saving and efficient.

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 screw compressor is a compression device widely used in the industrial field. Its working principle is that through the mutual meshing of the male and female rotors, a compression chamber is formed within the housing, and gas is transported from the low-pressure region to the high-pressure region to complete the compression process. During the compression process, the gas temperature will increase significantly, so effective cooling measures need to be taken to ensure the normal operation of the compressor and improve efficiency.

[0003] In the related art, heat exchange is achieved by spraying water or oil through a single hole or multiple holes on the compressor housing to achieve the purpose of temperature control. However, the hole positions are designed in the suction section or the high-pressure sealed chamber section of the compression chamber. When the hole positions are designed in the suction section, this design seriously affects the suction volume flow rate. When the hole positions are designed in the high-pressure sealed chamber section of the compression chamber, the driving shaft power of the main engine is increased, and the energy consumption increases. Summary of the Invention

[0004] The purpose of the present application is to provide a compressor and a compression system, which can improve the above problems.

[0005] One aspect of the present invention provides a compressor. The compressor includes a housing, a compression chamber for installing a male rotor and a female rotor is formed within the housing. The compression chamber sequentially includes a suction section, a low-pressure compression chamber section, and a high-pressure compression chamber section along the axial direction of the rotor. A plurality of spray holes are provided on the housing, and all of the plurality of spray holes are located in the low-pressure compression chamber section for spraying a cooling medium into the compression chamber.

[0006] In some embodiments of the present application, the plurality of spray holes are distributed in a spiral.

[0007] In some embodiments of the present application, the plurality of spray holes include a plurality of first spray holes, and the plurality of first spray holes are distributed in a first spiral. The lead of the first spiral is equal to the lead of the outer diameter of the male rotor tooth tip, and the spiral angle of the first spiral is equal to the spiral angle of the male rotor.

[0008] In some embodiments of the present application, the plurality of spray holes include a plurality of second spray holes, and the plurality of second spray holes are distributed in a second spiral. The lead of the second spiral is equal to the lead of the outer diameter of the female rotor tooth tip, and the spiral angle of the second spiral is equal to the spiral angle of the female rotor.

[0009] In some embodiments of the present application, the spray holes are atomizing spray holes for spraying a mist-like cooling medium into the compression chamber.

[0010] In some embodiments of the present application, the diameter range of the atomizing nozzle holes is 0.1 mm - 2 mm.

[0011] In some embodiments of the present application, the starting angle of the first spiral is determined by the following formula:

[0012] ;

[0013] The starting angle of the second spiral is determined by the following formula:

[0014] ;

[0015] In the formula: is the starting angle of the first spiral, is the starting angle of the second spiral, is the suction angle of the male rotor, is the suction angle of the female rotor, is the number of teeth of the male rotor, is the number of teeth of the female rotor, is the tip radius of the male rotor, is the tip radius of the female rotor, is the diameter of the first nozzle hole, is the diameter of the second nozzle hole.

[0016] In some embodiments of the present application, the number of the nozzle holes on the housing satisfies: ; wherein, is the designed flow rate of the cooling medium, is the flow velocity of the cooling medium, is the diameter of the nozzle hole.

[0017] In some embodiments of the present application, the multiple nozzle holes are distributed at intervals along the axial direction of the housing.

[0018] The second aspect of the present application also provides a compression system, which includes the compressor described above.

[0019] The twin-screw compressor includes a housing, and a compression chamber for installing a female rotor and a male rotor is formed inside the housing. The compression chamber sequentially includes a suction section, a low-pressure compression chamber section, and a high-pressure compression chamber section along the axial direction of the rotor. A spray hole for spraying a cooling medium into the compression chamber is provided on the housing. Different from the prior art in which the spray hole is arranged in the suction section or the high-pressure compression chamber section of the compression chamber, the present application optimizes the setting position of the spray hole and designs all the spray holes in the low-pressure compression chamber section of the compression chamber. Since the low-pressure compression chamber section is in the closed section of the compression chamber, the suction volume flow rate of the compressor can be ensured, and the ambient pressure during the suction process of each tooth space suction volume is not affected by the spray hole. At the same time, the pressure in the low-pressure compression chamber section is relatively low, the driving power load of the pump for spraying the cooling medium is minimized, the driving power of the compressor is reduced, and it is energy-saving and efficient. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] 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 describing the embodiments of the present invention or 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.

[0021] Figure 1 is a schematic structural diagram of the compressor shown in some embodiments of the present invention;

[0022] Figure 2 is Figure 1 a cross-sectional view of the compressor shown in

[0023] Figure 3 is Figure 1 a schematic structural diagram of the housing of the compressor shown in

[0024] Figure 4 is Figure 3 another schematic structural diagram of the housing of the compressor shown in

[0025] Figure 5 is Figure 3 yet another schematic structural diagram of the housing of the compressor shown in DETAILED DESCRIPTION OF THE EMBODIMENTS

[0026] The following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only some of the embodiments of the present invention, rather than all of them. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts fall within the scope of protection of the present invention.

[0027] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the 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 specified, the meaning of "a plurality of" is two or more.

[0028] 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.

[0029] A twin-screw compressor is a rotary positive-displacement compressor. Its core components are a pair of meshing male rotor and female rotor. Through the meshing of the male and female rotors, a compression chamber is formed within the housing, and the gas is transported from the low-pressure region to the high-pressure region to complete the compression process. During the compression process, the gas temperature will increase significantly. Therefore, effective cooling measures need to be taken to ensure the normal operation of the compressor and improve efficiency.

[0030] Regarding the gas overheating phenomenon generated during the operation of the twin-screw compressor, in the related art, single holes with a linear distribution of male and female rotors or multiple holes with a linear distribution are used to spray water or oil for heat exchange to achieve the purpose of temperature control; for larger flow rates and higher flow rates, the hole diameter is increased or the number of holes with a linear distribution is increased to achieve temperature control. In some designs, the holes are designed in the suction process section, seriously affecting the suction volumetric flow rate; for the multi-hole structure, problems such as unbalanced spray hole pressure, different flow rates and flow velocities, and backflow from the high-pressure chamber to the low-pressure chamber occur; and for the design of holes in the high-pressure closed chamber section, the driving shaft power of the main engine is increased; the energy consumption increases. [[ID=I0]]

[0031] In view of this, to solve the above problems, in combination with Figures 1 to 5 As shown, in some embodiments of the present application, a compressor is proposed. The compressor includes a housing 1, and a compression chamber for installing a male rotor 21 and a female rotor 22 is formed within the housing 1. The compression chamber sequentially includes a suction section, a low-pressure compression chamber section, and a high-pressure compression chamber section along the axial direction of the rotor. A plurality of spray holes 3 are provided on the housing 1, and the plurality of spray holes 3 are located in the low-pressure compression chamber section for spraying a cooling medium into the compression chamber.

[0032] Specifically, the compressor housing 1 is made of cast iron or steel material, having sufficient strength and stiffness to withstand the pressure and temperature generated during the compression process. The inside of the housing 1 is designed with a precision-machined compression chamber for installing the male rotor 21 and the female rotor 22. The male rotor 21 and the female rotor 22 are respectively supported at both ends of the housing 1 by bearings and maintain an accurate relative position relationship through synchronous gears. The tooth profiles of the male rotor 21 and the female rotor 22 are designed as involute curves to ensure the formation of continuously changing sealed chambers during rotation.

[0033] The compression chamber is axially divided into three functional regions along the rotor: an intake section, a low-pressure compression chamber section, and a high-pressure compression chamber section. The intake section is located at one end of the compression chamber and is provided with an intake port for sucking in the gas to be compressed. The low-pressure compression chamber section is located in the middle position where the gas starts to be compressed and the pressure gradually increases but has not reached the maximum value yet. The high-pressure compression chamber section is located at the other end of the compression chamber where the gas is compressed to the maximum pressure and discharged through the exhaust port.

[0034] On the housing 1, especially at the position corresponding to the low-pressure compression chamber section, a plurality of spray holes 3 are provided. These spray holes 3 are connected to an external cooling medium supply system for spraying the cooling medium into the compression chamber. The cooling medium can be lubricating oil, water, or other suitable liquids, which are pressurized by an external pump system and then fed into the spray holes 3. The positions of the spray holes 3 precisely correspond to the low-pressure compression chamber section. Since the low-pressure compression chamber section is in the sealed section of the compression chamber, this can ensure the suction volume flow rate of the compressor and ensure that the ambient pressure during the suction process of each tooth space suction volume is not affected by the spray holes 3. At the same time, the pressure in the low-pressure compression chamber section is relatively low, and the driving power load of the pump for spraying the cooling medium is minimized, reducing the driving power of the compressor, which is energy-saving and efficient.

[0035] In some embodiments of the present application, the plurality of spray holes 3 are distributed in a spiral. This distribution method enables the cooling medium to be evenly sprayed along the rotation direction of the rotor, ensuring that all parts in the compression chamber can be fully cooled. The spray holes 3 distributed in a spiral can also continuously spray the cooling medium into the compression chamber as the rotor rotates, avoiding the problem of uneven cooling. At the same time, the design of the spiral distribution of multiple spray holes 3 can spray-cool the entire screw rod, which can reduce the driving power consumption of the compression main shaft power.

[0036] In the related art, multiple spray holes 3 are linearly distributed, which may cause some spray holes 3 to be distributed in the suction section, some spray holes 3 to be distributed in the low-pressure compression cavity section, and some spray holes 3 to be distributed in the high-pressure compression cavity section, resulting in unbalanced water spray point pressures at the hole positions; there may also be a risk of gas in the high-pressure cavity flowing back to the low-pressure cavity, affecting performance. In some embodiments of the present application, the multiple spray holes 3 include multiple first spray holes 31, and the multiple first spray holes 31 are distributed along a first spiral line L1. The lead of the first spiral line L1 is equal to the lead of the outer diameter of the tooth tip of the male rotor 21, and the helix angle of the first spiral line L1 is equal to the helix angle of the male rotor 21. This design can not only make the distribution of the first spray holes 31 completely match the rotation trajectory of the male rotor 21, ensuring that the cooling medium can be accurately sprayed into the compression cavity formed between the tooth tip of the male rotor 21 and the inner wall of the housing 1, improving the cooling efficiency. At the same time, since each first spray hole 31 corresponds to the same tooth space, the pressure received by each first spray hole 31 is equal, and thus the flow rate and flow velocity of each first spray hole 31 can be made equal, avoiding the backflow phenomenon caused by unbalanced pressures of the first spray holes 3, and improving the safety of the compressor.

[0037] Further, in some embodiments of the present application, the multiple spray holes 3 include multiple second spray holes 32, and the multiple second spray holes 32 are distributed along a second spiral line L2. The lead of the second spiral line L2 is equal to the lead of the outer diameter of the tooth tip of the female rotor 22, and the helix angle of the second spiral line L2 is equal to the helix angle of the female rotor 22. This design can not only make the distribution of the second spray holes 32 completely match the rotation trajectory of the female rotor 22, ensuring that the cooling medium can be accurately sprayed into the compression cavity formed between the tooth tip of the female rotor 22 and the inner wall of the housing 1, further improving the overall cooling efficiency. At the same time, each second spray hole 32 faces the same tooth space, so that the pressure received by each second spray hole 32 is equal, and thus the flow rate and flow velocity of each second spray hole 32 can be made equal, avoiding the backflow phenomenon caused by unbalanced pressures of the second spray holes 32, and improving the safety of the compressor.

[0038] In some embodiments of the present application, the first spray holes 31 and the second spray holes 32 are simultaneously provided on the housing 1. The first spray holes 31 are located on the housing 1 that matches the position of the male rotor 21, and the second spray holes 32 are located on the housing 1 that matches the position of the female rotor 22. The first spray holes 31 are distributed along the first spiral line L1 on the housing 1, and the second spray holes 32 are distributed along the second spiral line L2; in the low-pressure compression cavity section, each spray hole 3 communicates with the corresponding tooth space, and the pressure received by each spray hole 3 is consistent, so that the flow rate and flow rate of each spray hole 3 can be ensured to be the same, avoiding the backflow problem caused by inconsistent pressures of each spray hole 3.

[0039] Of course, it can be understood that the aforementioned plurality of first spray holes 31 may also be provided only on the housing 1 that matches the position of the male rotor 21, or the aforementioned plurality of second spray holes 32 may also be provided only on the housing 1 that matches the position of the female rotor 22, without limitation herein.

[0040] In the related art, for large-flow models, the heat dissipation efficiency is often improved by increasing the aperture, but this will cause the cooling medium in the compression chamber to exist in a relatively large amount of liquid form. The liquid cannot be compressed, occupies the volume of the compression chamber, and is prone to the risk of liquid hammer.

[0041] In some embodiments of the present application, the spray hole 3 is an atomizing spray hole for spraying a misty cooling medium into the compression chamber. The atomizing spray hole adopts a special structural design inside, so that the cooling medium is atomized into fine droplets when passing through the spray hole 3. This misty cooling medium has a larger specific surface area, can absorb the heat generated during the compression process more quickly, and improves the cooling efficiency. At the same time, the misty cooling medium is more evenly distributed, can cover a larger area in the compression chamber, and avoids local overheating.

[0042] In some embodiments of the present application, the diameter range of the atomizing spray hole 3 is 0.1 mm - 2 mm. Optionally, the diameter of the atomizing spray hole 3 is 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, 0.5 mm, 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1 mm, 1.1 mm, 1.2 mm, 1.3 mm, 1.4 mm, 1.5 mm, 1.6 mm, 1.7 mm, 1.8 mm, 1.9 mm, 2 mm, etc. When the diameter of the spray hole 3 is 0.1 mm, the cooling medium is atomized into extremely fine droplets, and the cooling effect is the best, but the purity requirement for the cooling medium is relatively high, and it is easy to be blocked; when the diameter of the spray hole 3 is 2 mm, the atomizing effect of the cooling medium is relatively poor, but the flow rate is large and it is not easy to be blocked. In practical applications, the appropriate diameter of the spray hole 3 can be selected according to the type and purity of the cooling medium. For example, for a cooling medium containing a small amount of impurities, a spray hole 3 with a diameter of 1.5 mm can be selected, which can ensure a certain atomizing effect and is not easy to be blocked.

[0043] In some embodiments of the present application, as Figure 4 shown, the centers of the first spray holes 31 are distributed in a first spiral line L1, the centers of the second spray holes 32 are distributed in a second spiral line L2, and the chord length angle of the diameter of the first spray holes 31 on the housing 1

[0044] ;

[0045] The chord length angle of the diameter of the second spray holes 32 on the housing 1

[0046] ;

[0047] In some embodiments of the present application, the intake angle of the male rotor 21 plus the included angle between the teeth of the male rotor 21 , plus half of the chord length included angle on the housing 1 with the diameter of the first injection hole 31 , after arrangement, the included angle of the starting point of the first helix L1 formed by the center of the first injection hole 31 can be obtained: :

[0048] ;

[0049] That is: ;

[0050] Similarly, the intake angle of the female rotor 22 plus the included angle between the teeth of the male rotor 21 , plus half of the chord length included angle on the housing 1 with the diameter of the second injection hole 32 , after arrangement, the included angle of the starting point of the second helix L2 formed by the center of the second injection hole 32 is:

[0051] ;

[0052] That is: ;

[0053] In the formula: is the starting included angle of the first helix L1, is the starting included angle of the second helix L2, is the intake angle of the male rotor 21, is the intake angle of the female rotor 22, is the number of teeth of the male rotor 21, is the number of teeth of the female rotor 22, is the tip radius of the male rotor 21, is the tip radius of the female rotor 22, is the diameter of the first injection hole 31, is the diameter of the second injection hole 32.

[0054] The helix starting included angle of the injection hole 3 calculated through these formulas can ensure the precise matching of the position of the injection hole 3 with the rotation position of the rotor, enabling the cooling medium to be injected into the compression chamber at the optimal timing. For example, the number of teeth of the male rotor 21 is 5, and the number of teeth of the female rotor 22 is 7; according to the parameters of the male and female rotors, the intake angle of the male rotor is calculated to be 277.787°, and the intake angle of the female rotor is 233.573°, and the tip radius of the male rotor 21 is 50 mm, and the tip radius of the female rotor 22 is 45 mm; the diameter of the first injection hole 31 is 1.5 mm, and the diameter of the second injection hole 32 is 1.5 mm. According to the above formula, the starting angle of the first helix L1 can be calculated to be 350.647°, and the starting angle of the second helix L2 is 285.956°. Among them, the suction angle of the male rotor and the suction angle of the female rotor are obtained according to the parameters of the male and female rotors. and the suction angle of the female rotor The method is a well-known technology and will not be introduced in detail here.

[0055] In actual design, the cooling medium flow rate of the twin-screw compressor can be calculated by thermal calculation first, and then the number of injection holes 3 can be obtained according to the flow rate and the diameter of the injection hole 3.

[0056] In some embodiments of the present application, the number of the injection holes 3 on the housing 1 satisfies: ; where is the designed flow rate of the cooling medium, is the flow velocity of the cooling medium, is the diameter of the injection hole 3. This design ensures that the number of injection holes 3 can meet the requirements of the designed flow rate of the cooling medium. For example, when the flow rate of the cooling medium is calculated to be 10 L / min according to the thermal performance controlled by temperature, and the flow velocity of the cooling medium is 8 m / s, it is calculated that the number of injection holes should be no less than 12. Of course, according to actual design requirements, the number of injection holes can be appropriately increased or decreased to meet the cooling requirements.

[0057] In some embodiments of the present application, the multiple injection holes 3 are on the housing 1. On the one hand, they are distributed along a helix with the same lead and helix angle as the female rotor 22 and the male rotor 21. On the other hand, according to the thermal distribution during the twin-screw compression process, the multiple injection holes 3 are spaced apart along the axial direction of the housing. This distribution method ensures that the cooling medium can evenly cover the entire low-pressure compression cavity section, avoiding local overheating. The equally spaced injection holes 3 also simplify the processing technology of the housing 1, reduce the manufacturing cost. At the same time, the pressure received by each injection hole 3 is equal, so that the flow rate and flow velocity of each injection hole 3 are equal, avoiding the backflow phenomenon caused by the pressure imbalance of each injection hole 3 and improving the safety of the compressor.

[0058] In practical applications, the working process of the compressor is as follows: First, the gas enters the suction process section through the suction port; then, as the female rotor 22 and the male rotor 21 rotate, the gas is brought into the low-pressure compression chamber section to start compression; at this time, the cooling medium is sprayed into the compression chamber through multiple spray holes 3 to absorb the heat generated during the compression process; finally, the gas enters the high-pressure compression chamber section and is further compressed to the highest pressure and discharged through the exhaust port. During the whole process, the spraying of the cooling medium effectively controls the temperature rise during the compression process, improving the efficiency and reliability of the compressor.

[0059] The second aspect of this application also provides a compression system, which includes the aforementioned compressor. The compressor optimizes the setting position of the spray holes 3, and all the spray holes 3 are designed in the low-pressure compression chamber section of the compression chamber; since the low-pressure compression chamber section is in the closed section of the compression chamber, this can ensure the suction volume flow rate of the compressor and ensure that the ambient pressure of the suction process of each inter-tooth suction volume is not affected by the spray holes 3; at the same time, the pressure in the low-pressure compression chamber section is relatively low, and the driving power load of the pump for spraying the cooling medium is minimized, reducing the driving power of the compressor, being energy-saving and efficient, and improving the working efficiency of the entire compression system.

[0060] Furthermore, multiple spray holes 3 are provided on the housing 1, and the multiple spray holes 3 present a helical hole position distribution with the same lead and the same rotation direction as the female rotor and the male rotor. Each spray hole 3 faces the same inter-tooth groove of the female and male rotors, so the pressure received by each spray hole 3 position is equal, thus ensuring that the flow rate and flow velocity of each spray hole 3 are equal, and it can also avoid the phenomenon of gas backflow through the spray holes.

[0061] In some embodiments of this application, in addition to the above-mentioned compressor, the compression system further includes a cooling medium supply system, a driving system, and a control system. The cooling medium supply system includes a cooling medium storage tank, a filter, a pump, and pipelines, and is used to provide clean and constant-pressure cooling medium to the spray holes 3 of the compressor. The driving system includes a motor and a transmission device, and is used to drive the rotation of the male rotor of the compressor. The male rotor maintains an accurate relative position relationship with the male rotor through a synchronous gear. The control system includes various sensors, controllers, and actuators, and is used to monitor and control the operating state of the compression system.

[0062] The pump in the cooling medium supply system pumps the cooling medium out of the storage tank, removes impurities through the filter, and then sends it into the spray holes 3 of the compressor through the pipeline. The outlet pressure of the pump is usually set to be 20 - 30% higher than the pressure in the low-pressure compression chamber section of the compressor to ensure that the cooling medium can be smoothly sprayed into the compression chamber. The accuracy of the filter is usually selected to be 1 / 3 of the diameter of the spray holes 3 to prevent impurities from clogging the spray holes 3.

[0063] In a drive system, a variable-frequency motor is usually selected for the motor, which can adjust the speed according to the load demand and improve the energy efficiency of the system. The motor is connected to the male rotor through a coupling or belt drive to ensure the smoothness of power transmission.

[0064] The control system monitors the temperature of each part of the compressor through a temperature sensor, monitors the inlet and outlet pressures of the compressor through a pressure sensor, and monitors the flow rate of the cooling medium through a flow sensor. The controller adjusts the speed of the motor and the flow rate of the cooling medium according to these parameters to ensure that the compression system operates in an optimal state.

[0065] In practical applications, the compression system can be used in various occasions such as air compression, refrigerant compression, and natural gas compression. Different application occasions may require adjusting the type and parameters of the cooling medium to adapt to different working conditions. For example, in air compression applications, lubricating oil is usually used as the cooling medium; in refrigerant compression applications, lubricating oil compatible with the refrigerant can be used as the cooling medium; in natural gas compression applications, special cooling media may be required to avoid reactions with natural gas.

[0066] Those of ordinary skill in the art can understand that the above embodiments are specific implementation manners for implementing the present invention, and in practical applications, various changes can be made to them in form and details without departing from the spirit and scope of the present invention.

Claims

1. A compressor, characterized in that, It includes a housing, a compression chamber for installing a female rotor and a male rotor is formed inside the housing. The compression chamber sequentially includes a suction section, a low-pressure compression chamber section, and a high-pressure compression chamber section along the axial direction of the rotor. A plurality of spray holes are provided on the housing, and all of the plurality of spray holes are located in the low-pressure compression chamber section. The spray holes are used to spray a cooling medium into the compression chamber; the plurality of spray holes are distributed in a spiral shape; The plurality of spray holes include a plurality of first spray holes, and the plurality of first spray holes are distributed in a first spiral shape. The lead of the first spiral is equal to the lead of the outer diameter of the male rotor tooth tip, and the helix angle of the first spiral is equal to the helix angle of the male rotor; The plurality of spray holes include a plurality of second spray holes, and the plurality of second spray holes are distributed in a second spiral shape. The lead of the second spiral is equal to the lead of the outer diameter of the female rotor tooth tip, and the helix angle of the second spiral is equal to the helix angle of the female rotor; The starting angle of the first spiral is determined by the following formula: ; The starting angle of the second spiral is determined by the following formula: ; Wherein: is the starting angle of the first helical line, is the starting angle of the second helical line, is the intake angle of the male rotor, is the intake angle of the female rotor, is the number of teeth of the male rotor, is the number of teeth of the female rotor, is the tip radius of the male rotor, is the tip radius of the female rotor, is the diameter of the first injection hole, is the diameter of the second injection hole.

2. The compressor according to claim 1, characterized in that: The spray holes are atomizing spray holes, which are used to spray a misty cooling medium into the compression chamber.

3. The compressor according to claim 2, wherein, The diameter range of the atomizing spray holes is 0.1 mm - 2 mm.

4. The compressor according to claim 1, wherein The number of the spray holes on the housing Satisfies: ; wherein, is the designed flow rate of the cooling medium, is the flow velocity of the cooling medium, is the diameter of the spray hole.

5. The compressor according to claim 1, characterized in that, The plurality of spray holes are spaced apart along the axial direction of the housing.

6. A compression system, characterized in that, It includes the compressor according to any one of claims 1 - 5.

Images