WO2024037331A1 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

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Publication number
WO2024037331A1
WO2024037331A1 PCT/CN2023/110529 CN2023110529W WO2024037331A1 WO 2024037331 A1 WO2024037331 A1 WO 2024037331A1 CN 2023110529 W CN2023110529 W CN 2023110529W WO 2024037331 A1 WO2024037331 A1 WO 2024037331A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid channel
chamber
sound
screw compressor
compressor according
Prior art date
Application number
PCT/CN2023/110529
Other languages
English (en)
Chinese (zh)
Inventor
杨胜梅
安伟杰
林坤
朱剑
Original Assignee
江森自控空调冷冻设备(无锡)有限公司
江森自控泰科知识产权控股有限责任合伙公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 江森自控空调冷冻设备(无锡)有限公司, 江森自控泰科知识产权控股有限责任合伙公司 filed Critical 江森自控空调冷冻设备(无锡)有限公司
Publication of WO2024037331A1 publication Critical patent/WO2024037331A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/063—Sound absorbing materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present application provides a screw compressor, especially a screw compressor with a muffler structure.
  • the twin-screw compressor has a pair of male and female rotors that mesh with each other.
  • the pair of male and female rotors rotate relative to each other to compress the refrigerant.
  • the twin-screw compressor is connected to the economizer system, and the economizer system provides a part of the refrigerant (or other media) to the inside of the compressor to improve the capacity of the twin-screw compressor.
  • the economizer system is connected to the compression chamber of the compressor through pipelines.
  • the present application provides a screw compressor, including: a casing, a fluid channel and a muffler structure.
  • the casing has a compression chamber; the fluid channel is located in the casing, and the first end of the fluid channel It is connected to the outside of the compressor, and the second end of the fluid channel is connected to the compression chamber; the sound-absorbing structure is arranged outside the fluid channel, and the sound-absorbing structure includes at least one chamber, and the at least A chamber communicates with the fluid channel.
  • the at least one chamber is arranged in an annular shape surrounding the fluid passage.
  • the at least one chamber is arranged around a portion of the fluid passage.
  • the at least one chamber includes a plurality of chambers, and the plurality of chambers are arranged along the extending direction of the fluid passage.
  • the at least one chamber includes a plurality of chambers, and the plurality of chambers are staggered in the extending direction of the fluid passage.
  • the sound attenuation structure further includes a sound attenuation material, and the sound attenuation material is filled in the at least one chamber.
  • the sound attenuation material includes a plurality of acoustic meta-mufflers, and at least a part of the plurality of acoustic meta-mufflers is connected to the fluid channel.
  • the muffler structure further includes a side wall, the side wall is arranged around the fluid channel and is located between the fluid channel and the at least one chamber, and the side wall is A plurality of side wall channels are provided extending through the side wall to communicate the at least one chamber with the fluid channel.
  • the at least one chamber in the extending direction of the fluid channel, has a front end and a rear end, the front end is close to the first end of the fluid channel, and the rear end is away from the a first end of the fluid channel; at least one side wall channel of the plurality of side wall channels is proximate to a rear end of the at least one chamber.
  • the muffler structure is close to the first end of the fluid channel, and the first end of the fluid channel is connected to the economizer of the air conditioning system.
  • the screw compressor in this application has a fluid channel that can communicate with the compression chamber and the external economizer system. Fluid passages introduce refrigerant from the economizer into the compression chamber. Since the screw compressor is working, the teeth of the rotor periodically sweep across the outlet of the fluid channel, and the pressure in the slots on both sides of the teeth of the rotor is different, resulting in constant changes in the fluid pressure in the fluid channel, which may cause problems with the economizer.
  • the pipes connected to the system may have loose or broken interfaces due to vibration.
  • the fluid channel is provided with a sound-absorbing structure, which can reduce the impact of pressure changes on the external pipeline of the economizer system.
  • Figure 1A is a perspective view of the compressor in this application.
  • Figure 1B is a cross-sectional view of the compressor in Figure 1A;
  • Figure 2 is a perspective view of the rear housing of the first embodiment of the present application.
  • Figure 3 is a partial cross-sectional view of Figure 2;
  • Figure 4 is a partial cross-sectional view of the rear housing of the second embodiment of the present application.
  • Figure 5A is a perspective view of the noise reduction structure of the third embodiment of the present application.
  • Fig. 5B is a bottom view of the noise reduction structure in Fig. 5A viewed along the axial direction;
  • Figure 5C is an axial cross-sectional view of the sound-absorbing structure taken along line B-B in Figure 5B;
  • Figure 5D is an axial cross-sectional view of the sound-absorbing structure taken along line C-C in Figure 5B;
  • Figure 6 is an axial cross-sectional view of the sound-absorbing structure of the fourth embodiment of the present application.
  • Figure 7 is an axial cross-sectional view of the noise reduction structure of the fifth embodiment of the present application.
  • Figure 8 is a radial cross-sectional view of the noise reduction structure of the sixth embodiment of the present application.
  • Figure 9 is a partial cross-sectional view of the rear housing of the seventh embodiment of the present application.
  • Figure 10 is a partial cross-sectional view of the rear housing of the eighth embodiment of the present application.
  • Figure 11 is a partial cross-sectional view of the rear housing of the ninth embodiment of the present application.
  • Figure 12 is a partial cross-sectional view of the rear housing of the tenth embodiment of the present application.
  • FIG. 1A is a perspective view of the compressor in this application
  • FIG. 1B is a cross-sectional view of the compressor in FIG. 1A
  • the compressor 100 includes a housing 101 and a male rotor 102 and a female rotor 103 located in the housing 101 .
  • the male rotor 102 and the female rotor 103 can be driven to rotate.
  • the male rotor 102 is drivingly connected to the motor 160 so that the motor 160 can drive the male rotor 102 to rotate around the axis of the male rotor 102 relative to the housing 101 .
  • the female rotor 103 can be driven by the male rotor 102 to rotate relative to the housing 101 about the axis of the female rotor 103 .
  • the outside of the male rotor 102 has a plurality of spiral teeth 168 and spiral grooves formed between adjacent teeth 168.
  • the outside of the female rotor 103 also has a plurality of spiral teeth 169 and between adjacent teeth 169. spiral grooves formed between them.
  • the teeth 168 and grooves of the male rotor 102 and the grooves and teeth 169 of the female rotor 103 form an intermeshing structure, so that the male rotor 102, the female rotor 103 and the housing 101 together form a compression chamber 105.
  • a fluid passage 140 is provided in the casing 101 for providing refrigerant into the compression chamber 105 of the compressor 100 .
  • the housing 101 includes a front housing 171 , a middle housing 172 and a rear housing 173 .
  • the front housing 171, the middle housing 172 and the rear housing 173 are connected in sequence. Fluid flows from front housing 171 to rear housing 173 within the compressor.
  • Fluid passage 140 is located on rear housing 173 .
  • the outlet of the fluid channel 140 is connected to the compression chamber 105, and the inlet is connected to the economizer system through a pipeline.
  • the economizer system leads part of the refrigerant in the refrigeration cycle system back to the compressor to improve the capacity of the compressor.
  • the economizer system connects the fluid channel 140 to the bottom of the condenser or the subcooler, and leads a small part of the refrigerant liquid from the bottom of the condenser or the subcooler back to the compressor.
  • This part of the refrigerant liquid can use the natural pressure difference to enter the compressor. machine.
  • the teeth of the male rotor 102 or the female rotor 103 periodically pass through the outlet of the fluid passage 140. Due to the The pressure in the tooth grooves on both sides of the tooth is obviously different, so the pressure at the outlet of the fluid channel 140 changes to a certain extent.
  • the complex flow patterns and pressure pulsations present in the fluid channel 140 may lead to the risk of loosening or rupture of the interface of the pipeline connected to the economizer system due to vibration.
  • the fluid channel 140 in this application is provided with a sound-absorbing structure, which can reduce the amplitude of pressure pulsation, thereby reducing the impact of pressure pulsation on external pipelines.
  • FIG 2 is a perspective view of the rear housing of the first embodiment of the present application.
  • the rear housing 173 has a housing end surface 202 disposed toward the middle housing 172.
  • the male rotor 102 and the female rotor 103 are The exhaust end abuts against the housing end surface 202 , and the housing end surface 202 can close the end of the compression chamber 105 .
  • the housing end face 202 is also provided with an internal exhaust orifice 235 , and the compression chamber 105 can be aligned with the internal exhaust orifice 235 .
  • Fluid channel 140 has an inlet 241 and an outlet 242.
  • the outlet 242 is disposed on the housing end face 202 and can be swept by the exhaust end of the male rotor 102 or the female rotor 103 so as to be connected with the compression chamber 105 .
  • the inlet 241 is provided on the outer surface of the rear housing 173.
  • the inlet 241 is connected to the external pipeline 250.
  • the external pipeline 250 is used to connect the economizer system, so that the economizer system can supplement refrigeration into the compression chamber 105 through the fluid channel 140. agent.
  • Figure 3 is a partial cross-sectional view of Figure 2.
  • Figure 3 is a partial view of the rear housing 173 in Figure 2 cut along the direction shown by A-A and viewed along the direction shown by the arrow, showing the rear The structure near the fluid channel 140 in the housing 173.
  • the fluid channel 140 includes a first end 311 and a second end 312.
  • the inlet 241 is located at the first end 311 and the outlet 242 is located at the second end 312.
  • the area of the inlet 241 is equal to or smaller than the cross-sectional area of the fluid channel 140 .
  • the fluid channel 140 includes a front section 351 and a rear section 352.
  • the front section 351 extends along the vertical direction as shown in Figure 3, and the rear section 352 extends along the horizontal direction.
  • the front section 351 and the rear section 352 are provided to facilitate processing and to adapt to the relative positions of the inlet 241 and the outlet 242 to connect the compression chamber 105 with the external pipeline.
  • the position setting of the inlet 241 changes, the position setting and the setting of the extending direction of the front section 351 and the rear section 352 of the fluid channel 140 change accordingly.
  • the first end 311 includes a top plate 357 with a hole 359 in the middle, and the top plate 357 covers an end of the first end 311 .
  • Hole 359 in top plate 357 forms inlet 241 .
  • the inlet 241 is provided at other positions of the rear housing 173, and the fluid channel 140 extends along the same direction.
  • Sound-attenuating structure 320 includes a chamber 308 , and sound-attenuating material 371 located in chamber 308 .
  • the chamber 308 is connected with the front section 351 Pass.
  • the chamber 308 has an inner side 361 and an outer side 362. There is a certain distance between the inner side 361 and the outer side 362, so that the chamber 308 has a certain thickness in the radial direction of the fluid channel.
  • the chamber 308 is generally annular with a certain thickness.
  • the outer side 362 has a side wall formed by the rear housing 173 and the inner side 361 has an opening 365 that communicates with the front section 351 of the fluid channel 140 .
  • the height of the opening 365 is equal to the height of the chamber 308, and the opening 365 extends for one week along the circumferential direction and forms a closed ring shape. That is, the area of the opening 365 is equal to the outer surface area of the front section surrounded by the sound-absorbing structure. That is to say, the chamber 308 and the front section 351 of the fluid channel 140 can form an integral space.
  • the area of the opening 365 is less than the outer surface area of the front section 351 surrounded by the chamber 308, for example, the height of the opening 365 is less than the height of the chamber 308, or the opening 365 extends along the circumferential direction. Less than a week.
  • the sound-absorbing material 371 is an acoustic material composed of multiple acoustic superstructure sound-absorbing units.
  • the acoustic meta-muffler unit is a resonant cavity type acoustic meta-unit. Each acoustic meta-muffler unit has a cavity, and the cavity of the acoustic meta-muffler unit can be communicated with the front section 351 of the fluid channel 140 .
  • the sound-absorbing material 371 can absorb the pressure pulsation in the fluid channel 140 to a certain extent and reduce the impact of the pressure pulsation on the external pipeline.
  • the silencing units in the silencing material 371 are set to a single size or multiple sizes, so that they can be set to silencing the sound of a certain Hertz (ie, a certain frequency), or can silencing the sound of multiple Hertz. Voice.
  • the muffler structure 320 is disposed close to the inlet 241 of the fluid channel 140, that is, close to the connection between the fluid channel 140 and the external pipeline, so as to minimize the impact of pressure pulsation on the external pipeline.
  • the sound-absorbing structure 320 can also be provided around the entire fluid channel 140 , that is, the sound-absorbing structure 320 is provided on the outside of each section of the fluid channel 140 .
  • the hollow chamber 308 can absorb the pressure pulsation in the fluid channel 140 to a certain extent.
  • FIG. 4 is a partial cross-sectional view of the rear housing of the second embodiment of the present application. Similar to the embodiment shown in FIG. 3 , the difference is that a plurality of chambers 408 are provided in the extending direction of the fluid channel 140 , and there is a distance between each chamber 408 and adjacent chambers 408 . Sound-absorbing material 371 is provided in each chamber 408, or is a cavity. That is, the chambers may be intermittently provided in the extending direction of the fluid channel 140 . Compared with the first embodiment in Fig. 3, the second embodiment in Fig. 4 has similar technical effects.
  • Figure 5A is a perspective view of the sound-absorbing structure of the third embodiment of the present application.
  • Figure 5B is a bottom view of the sound-absorbing structure in Figure 5A seen along the axial direction.
  • Figure 5C is a cross-section of the sound-absorbing structure along line BB in Figure 5B An axial cross-sectional view of An axial cross-sectional view of the acoustic structure taken along line CC in Figure 5B.
  • the cross-section in Figure 5B is shown in Figures 5A and 5B.
  • the sound attenuation structure 520 is generally cylindrical and has an axial direction and a radial direction.
  • the sound absorbing structure 520 has an inner wall 511 and an outer wall 512 .
  • At least a section of the fluid channel 140 is surrounded by the inner wall 511 , for example, the front section 351 of the fluid channel 140 is surrounded by the inner wall 511 .
  • the outer wall 512 is connected to the rear housing 173 .
  • a space 522 is formed between the inner wall 511 and the outer wall 512 .
  • a plurality of radial partition walls 518 extending in the radial direction and a plurality of axial partition walls 519 extending in the axial direction are provided between the inner wall 511 and the outer wall 512 .
  • a plurality of radial partition walls 518 are arranged side by side along the axial direction to divide the space 522 into a plurality of segmented spaces 521.
  • a plurality of axial partition walls 519 are arranged along the radial direction to divide the multiple segmented spaces 521. is a plurality of chambers 508.
  • a plurality of axial partition walls 519 in adjacent segmented spaces 521 are staggered, so that a plurality of chambers 508 are staggered.
  • the inner wall 511 forms a side wall 539 of a sound-absorbing structure.
  • the side wall 539 is provided with a plurality of side wall channels 529 that penetrate the side wall 539.
  • the plurality of side wall channels 529 can connect the fluid channel 140 with the fluid in the plurality of chambers 508. Every connection.
  • each of the plurality of chambers 508 has a front end 581 and a rear end 582, the front end 581 is close to the first end 311 of the fluid channel 140, and the rear end 582 is away from the first end of the fluid channel 140 311.
  • At least one of the plurality of sidewall channels 529 is close to the rear end 582 of the chamber 508 to guide the fluid in the chamber 508 back into the fluid channel 140 so that no or a small amount of liquid accumulates in the fluid channel 140 .
  • the third embodiment in Fig. 5A has similar technical effects.
  • Figure 6 is an axial cross-sectional view of the sound-absorbing structure 620 of the fourth embodiment of the present application. It is similar to the embodiment shown in Figure 5A. The difference is that the sound-absorbing structure 620 of the fourth embodiment no longer has an outer wall. After the sound attenuation structure 620 is installed into the rear housing 173, the rear housing 173, the axial partition wall, the inner wall 611 and the radial partition wall 618 together form a plurality of chambers 608.
  • the fourth embodiment in FIG. 6 has similar technical effects.
  • Figure 7 is an axial cross-sectional view of the sound-absorbing structure of the fifth embodiment of the present application. It is similar to the embodiment shown in Figure 5A. The difference is that the bottom 765 of the chamber 708 of the fifth embodiment faces from the outside to the inside. Extending at a downward slope, this design is more conducive to discharging the liquid in the chamber 708 to the fluid channel 140 and avoiding accumulation of liquid in the chamber 708 .
  • the fifth embodiment in Fig. 7 has similar technical effects.
  • Figure 8 is a radial cross-sectional view of the sound-absorbing structure of the sixth embodiment of the present application. It is similar to the embodiment shown in Figure 5A. The difference is that the inner wall 811 and the outer wall 812 of the sixth embodiment are no longer the same. The axis is arranged, that is, the distance between the inner wall 811 and the outer wall 812 is unequal as seen in radial section. Thus, each chamber 808 is no longer evenly distributed in the circumferential direction. This embodiment is suitable for situations where the installation position of some fluid channels 140 has specific requirements.
  • the sixth embodiment in Fig. 8 has similar technical effects.
  • Figure 9 is a partial cross-sectional view of the rear housing of the seventh embodiment of the present application. It is similar to the embodiment shown in Figure 3. The difference is that the sound attenuation structure of the seventh embodiment in Figure 9 also includes side
  • the wall 939 and the side wall 939 are generally cylindrical, and the side wall 939 surrounds at least a section of the fluid channel 140 . That is, sidewall 939 is disposed between fluid channel 140 and chamber 908 .
  • the side wall 939 is provided with a plurality of side wall channels 929 penetrating the side wall 939, and the plurality of side wall channels 929 can communicate the fluid channel 140 with each of the chambers 908. In the extending direction of the fluid channel 140, there are a front end 981 and a rear end 982 in the chamber 908.
  • the front end 981 is close to the first end 311 of the fluid channel 140, and the rear end 982 is far away from the first end 311 of the fluid channel 140.
  • At least one of the plurality of sidewall channels 929 is close to the rear end 982 of the chamber 908 to guide the fluid in the chamber 908 back into the fluid channel 140 so that no or a small amount of liquid accumulates in the fluid channel 140 .
  • the sound-absorbing structure of the seventh embodiment in FIG. 9 also includes a top plate 945 covering the top of the chamber 908 and the side walls 939 to isolate the chamber 908 from the outside.
  • the top plate 945 is provided with a hole 958, and the external pipeline is connected to the fluid channel through the hole 958.
  • the side wall 939 and the top plate 945 are integrated structures to facilitate installation.
  • chamber 908 is provided with sound attenuating material.
  • the seventh embodiment in Fig. 9 has similar technical effects.
  • FIG. 10 is a partial cross-sectional view of the rear housing of the eighth embodiment of the present application. It is similar to the embodiment shown in FIG. 9 , but the difference is that multiple chambers 1008 are provided in the extending direction of the fluid channel 140 , there is a distance between each chamber 1008 and adjacent chambers 1008. That is, the chambers may be intermittently provided in the extending direction of the fluid channel 140 .
  • the eighth embodiment in Fig. 10 has similar technical effects.
  • FIG. 11 is a partial cross-sectional view of the rear housing of the ninth embodiment of the present application. It is similar to the embodiment shown in FIG. 9 . The difference is that the cavity 1108 is no longer provided with a sound-absorbing material and is a cavity. Compared with the embodiment in Fig. 9, the ninth embodiment in Fig. 11 has similar technical effects.
  • Figure 12 is a partial cross-sectional view of the rear housing of the tenth embodiment of the present application. It is similar to the embodiment shown in Figure 10. The difference is that the cavity 1208 is no longer provided with a sound-absorbing material and is a cavity. Compared with the embodiment in Fig. 10, the ninth embodiment in Fig. 12 has similar technical effects.
  • the fluid passage in this application can introduce the refrigerant in the economizer into the compression chamber.
  • the teeth of the rotor periodically sweep across the outlet of the fluid channel, which is the connection port between the fluid channel and the compression chamber. Due to the different pressures in the grooves on both sides of the teeth of the screw rotor, the fluid pressure in the fluid channel continues to change, causing vibration and noise. Pressure changes are transmitted to the external piping connecting the economizer system to the compressor fluid passage, possibly causing the interface of the external piping to loose or damaged.
  • a sound-absorbing structure is provided outside the fluid channel, which can absorb at least part of the pressure fluctuations, reduce noise, and reduce the impact of pressure changes on the external pipelines of the economizer system.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention concerne un compresseur à vis (100) comprenant : un logement (101), un canal de fluide (140) et une structure d'insonorisation (320, 520, 620). Le logement (101) est pourvu d'une cavité de compression (105) ; le canal de fluide (140) est situé dans le logement (101), une première extrémité (311) du canal de fluide (140) est en communication avec l'extérieur du compresseur (100), et une seconde extrémité (312) du canal de fluide (140) est en communication avec la cavité de compression (105) ; la structure d'insonorisation (320, 520, 620) est disposée sur le côté extérieur du canal de fluide (140), la structure d'insonorisation (320, 520, 620) comprend au moins une cavité (308, 408, 508, 608, 708, 808, 908, 1008, 1108, 1208), et la ou les cavités (308, 408, 508, 608, 708, 808, 908, 1008, 1108, 1208) sont en communication avec le canal de fluide (140). La structure d'insonorisation (320, 520, 620) est disposée au niveau du canal de fluide (140) du compresseur à vis (100), de telle sorte que l'effet de changements de pression sur des conduites externes raccordées au canal de fluide (140) peut être réduit.
PCT/CN2023/110529 2022-08-16 2023-08-01 Compresseur à vis WO2024037331A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202210982105.6A CN115324892A (zh) 2022-08-16 2022-08-16 螺杆压缩机
CN202210982105.6 2022-08-16

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Publication Number Publication Date
WO2024037331A1 true WO2024037331A1 (fr) 2024-02-22

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TW (1) TW202409425A (fr)
WO (1) WO2024037331A1 (fr)

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Publication number Priority date Publication date Assignee Title
CN115324892A (zh) * 2022-08-16 2022-11-11 江森自控空调冷冻设备(无锡)有限公司 螺杆压缩机

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