WO2020024514A1 - Screw compressor and compressor body thereof - Google Patents

Screw compressor and compressor body thereof Download PDF

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Publication number
WO2020024514A1
WO2020024514A1 PCT/CN2018/120602 CN2018120602W WO2020024514A1 WO 2020024514 A1 WO2020024514 A1 WO 2020024514A1 CN 2018120602 W CN2018120602 W CN 2018120602W WO 2020024514 A1 WO2020024514 A1 WO 2020024514A1
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WO
WIPO (PCT)
Prior art keywords
channel
rotor
rotor cavity
refrigerant flow
refrigerant
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Application number
PCT/CN2018/120602
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French (fr)
Chinese (zh)
Inventor
张治平
孟强军
龙忠铿
李日华
毕雨时
Original Assignee
珠海格力电器股份有限公司
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Publication of WO2020024514A1 publication Critical patent/WO2020024514A1/en

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    • 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
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the present application relates to the technical field of compressors, and in particular, to a screw compressor and its body.
  • the female and male rotors are usually meshed with the gap, the gap between the female and female rotor cavities, and the gap between the male and male rotor cavities.
  • the design is relatively small to prevent the low energy efficiency caused by excessive compression leakage when the screw compressor is running. Because the values of the gaps above are designed to be relatively small, the amount of deformation of the rotors (including female and male rotors) that can be accommodated by these gaps is also relatively small.
  • Rotor deformation is mainly caused by force deformation and thermal deformation of the rotor.
  • the screw compressor when the screw compressor runs to the limit point of its operating range, the rotor is deformed by force and thermal deformation.
  • the screw compressor In order to prevent the rotor from being deformed by an amount larger than the above-mentioned gap value, the screw compressor must be operated within a narrow operating range. This limits the operating range of the screw compressor and limits the applicability of the screw compressor.
  • a machine body includes a housing, and a rotor cavity is provided inside the housing;
  • the casing is provided with a refrigerant flow channel around the rotor cavity.
  • the refrigerant flow channel is close to the wall surface of the rotor cavity.
  • the refrigerant flow channel is used for circulating the refrigerant.
  • the machine body further includes an exhaust bearing seat, and the exhaust bearing seat is used for sealing connection with the exhaust end of the housing;
  • the exhaust end face of the casing is provided with a groove, which extends in the circumferential direction of the rotor cavity.
  • the exhaust bearing seat When the exhaust bearing seat is connected to the casing, the exhaust bearing seat covers the groove, and the space between the groove and the exhaust bearing seat Form refrigerant flow channels.
  • the refrigerant flow path includes a first end and a second end.
  • the first end is in communication with the outside of the housing, and the second end is in communication with the rotor cavity.
  • the flow direction of the refrigerant in the refrigerant flow path is from the first end to the first end. Both ends.
  • the body further includes a first channel, the first channel is provided on a side wall of the casing, one end of the first channel is communicated with the first end, and the other end of the first channel is communicated with the outside of the casing.
  • the flow passage communicates with the outside of the casing through the first passage.
  • the first channel is disposed on a sidewall of the casing along a radial direction of the casing.
  • the body further includes a second channel, the second channel is disposed on a side wall of the housing, one end of the second channel communicates with the second end, the other end of the second channel communicates with the rotor cavity, and the refrigerant flow channel It communicates with the rotor cavity through the second channel.
  • the body further includes a third channel, the third channel is disposed on a side wall of the housing, one end of the third channel is in communication with the second end, the other end of the third channel is in communication with the second channel, and the second The passage communicates with the refrigerant flow passage through the third passage.
  • the second channel and the third channel are perpendicular to each other, the second channel is disposed along a radial direction of the casing, and the third channel is disposed along an axial direction of the casing.
  • the rotor cavity includes a male rotor cavity and a female rotor cavity, and a refrigerant flow path surrounds the male rotor cavity and the female rotor cavity.
  • a screw compressor includes the body of any one of the above schemes.
  • the refrigerant flow channel can circulate the refrigerant, and the heat exchange between the refrigerant and the rotor can cool the rotor, thereby reducing the amount of deformation of the rotor.
  • the compressor uses the body, it can effectively widen the operating range of the compressor and improve the applicability of the compressor.
  • FIG. 1 is a schematic structural diagram of a body provided by an embodiment of the present application.
  • FIG. 2 is a schematic structural diagram of a casing in the structure shown in FIG. 1.
  • the size of the compressor's operating range determines the variety of places where the compressor can be used, and is one of the important factors controlling the competitiveness of compressor products.
  • the so-called compressor operating range means that the compressor can operate normally within a certain range of evaporation / condensation temperature, and this range is the operating range of the compressor.
  • the screw compressor and its body of the present application can have a wide operating range.
  • a body 10 provided by an embodiment of the present application includes a housing 100, and a rotor cavity 110 is provided inside the housing 100.
  • the rotor cavity 110 is used for accommodating a rotor, and the rotor is rotatable about the rotor shaft in the rotor cavity 110.
  • the casing 100 is provided with a refrigerant flow channel 200 around the rotor cavity 110.
  • the refrigerant flow channel 200 is close to the wall surface of the rotor cavity 110.
  • the refrigerant flow channel 200 is used for circulating the refrigerant.
  • the refrigerant flowing through the refrigerant flow channel 200 is used to exchange heat with the rotor, thereby reducing the temperature of the rotor, thereby reducing the thermal deformation of the rotor, and further reducing the amount of deformation of the rotor.
  • the compressor uses the body 10 since the amount of deformation of the rotor is effectively reduced, the operable range of the compressor is relatively enlarged. As a result, the diversity of compressor application places is effectively improved, and the competitiveness of compressor products is enhanced.
  • the rotor cavity 110 includes a male rotor cavity 111 and a female rotor cavity 112, and a refrigerant flow channel 200 surrounds the male rotor cavity 111 and the female rotor cavity 112.
  • a refrigerant flow channel 200 surrounds the male rotor cavity 111 and the female rotor cavity 112.
  • the refrigerant runner 200 surrounds the male rotor cavity 111 and the female rotor cavity 112.
  • the refrigerant flowing in the refrigerant runner 200 can exchange heat with the male rotor through the wall surface of the male rotor cavity 111.
  • the walls are heat exchanged. Therefore, the amount of deformation of the male and female rotors can be effectively reduced, and the operating range of the compressor can be widened.
  • the structure of the refrigerant flow channel 200 may be various. As shown in FIG. 1 and FIG. 2, as an implementable manner, the body 10 further includes an exhaust bearing seat 300, and the exhaust bearing seat 300 is used for sealing connection with the exhaust end of the housing 100.
  • the exhaust end surface 120 of the housing 100 is provided with a groove 121, and the groove 121 extends in the circumferential direction of the rotor cavity 110.
  • the exhaust bearing housing 300 When the exhaust bearing housing 300 is connected to the housing 100, the exhaust bearing housing 300 covers the groove 121, the groove A space between 121 and the exhaust bearing housing 300 forms a refrigerant flow path 200.
  • the refrigerant flow channel 200 includes a groove 121 provided on the exhaust end surface 120 of the housing 100.
  • the groove 121 can form a refrigerant flow channel through which the refrigerant is circulated through the sealed connection between the housing 100 and the exhaust bearing housing 300. 200.
  • the structure is simple and easy to process, and at the same time, it is convenient to form a closed refrigerant flow channel 200.
  • the formation of the refrigerant flow channel 200 makes flexible use of the sealed connection between the exhaust bearing seat 300 and the casing 100, and no additional structure is required to form a closed refrigerant flow channel 200.
  • setting the refrigerant flow channel 200 at the position of the exhaust end surface 120 can effectively cool the rotor according to the maximum thermal deformation of the rotor, thereby directly and effectively reducing the thermal deformation of the rotor, thereby reducing the amount of deformation of the rotor.
  • the rotor includes a female rotor and a male rotor. Due to the tooth shape of the female rotor, the amount of deformation of the female rotor is greater than that of the male rotor. Therefore, the analysis is mainly performed on the amount of deformation of the female rotor. After the simulation experiment analysis, the maximum deformation point of the female rotor is concentrated on the tooth top position of the female rotor near the exhaust end.
  • the thermal deformation has a large effect on the amount of deformation of the rotor, and the maximum position of the rotor thermal deformation is the position of the rotor tooth near the exhaust end face 120. It can be understood that the rotor crest is close to the wall surface of the rotor cavity 110.
  • the refrigerant flow channel 200 for circulating the refrigerant, heat exchange with the rotor can be effectively performed, the temperature of the rotor can be reduced, and the deformation of the rotor can be reduced.
  • the refrigerant flow channel 200 is arranged on the exhaust end surface 120 of the body 10, which can directly and effectively cool the maximum position of the rotor deformation, reduce the heating of the rotor from the root cause, thereby reducing the rotor deformation and ensuring that the compressor operates in a wide operating range. Reliable operation.
  • the cross-sectional shape of the groove 121 may be various, such as rectangular, U-shaped, and the like. Theoretically, the closer the refrigerant flow path 200 is to the wall surface of the rotor cavity 110, the better, so that it can fully exchange heat with the rotor. However, from a practical perspective, taking the refrigerant runner 200 as an example of the groove 121 provided on the exhaust end surface 120, the distance between the groove 121 and the wall surface of the rotor cavity 110 needs to be based on the type of the body 10 and the housing 100. Material and other specific settings.
  • the depth of the groove 121 also needs to be specifically designed according to the actual situation, such as the shape of the groove 121, the distance between the groove 121 and the wall surface of the rotor cavity 110, and the like. In order to ensure a good heat exchange effect, the structural strength of the casing 100 is ensured, and the reliable operation of the body 10 is ensured.
  • the refrigerant flow passage 200 may further include a plurality of sub flow passages extending along the axial direction of the casing 100, and the plurality of sub flow passages are disposed at intervals around the rotor cavity 110.
  • the refrigerant flow channel 200 may have other structural forms, as long as it can circulate the refrigerant to achieve the purpose of heat exchange with the rotor.
  • the refrigerant flow channel 200 includes a first end 210 and a second end 220.
  • the first end 210 is in communication with the outside of the housing 100, and the second end 220 is in communication with the rotor cavity 110.
  • the flow direction of the refrigerant in the flow path 200 is from the first end 210 to the second end 220.
  • the second end 220 of the refrigerant flow channel 200 is in communication with the rotor cavity 110, specifically, it is in communication with the intermediate pressure position of the rotor cavity 110, and the intermediate pressure position generally refers to the pressure between the start of compression and the completion of compression. Big or small area.
  • the first end 210 is in communication with the outside of the casing 100, so the refrigerant flow channel 200 can introduce a low-temperature liquid refrigerant from the outside of the casing 100 through the first end 210 to perform heat exchange with the rotor. After the heat exchange, the refrigerant absorbs heat and turns into steam, which is introduced to the intermediate pressure position of the rotor cavity 110 through the second end 220, and can play a role of supplementing air, thereby effectively improving the energy efficiency of the compressor. With this design, it is convenient to realize the continuous circulation and circulation of the refrigerant, and it can play a role of supplementing gas and increasing efficiency while ensuring a good heat exchange effect.
  • the first end 210 and the second end 220 may be respectively disposed outside the male rotor cavity 111 and the female rotor cavity 112, and the flow direction of the refrigerant may be determined by
  • the male rotor cavity 111 side flows to the female rotor cavity 112 side, or the female rotor cavity 111 side can flow to the male rotor cavity 112 side.
  • the refrigerant flow channel 200 may also have a ring-shaped structure around the rotor cavity 110.
  • the groove 121 may be a groove extending in a ring shape along the circumferential direction of the rotor cavity 110. It can be understood that the groove 121 may be provided with an inlet for inputting the refrigerant and an outlet for outputting the refrigerant.
  • the body 10 further includes a first channel 130, which is disposed on a side wall of the casing 100.
  • One end of the first channel 130 communicates with the first end 210, and the other end of the first channel 130
  • the refrigerant flow passage 200 communicates with the outside of the casing 100 through the first passage 130.
  • the cross-sectional shape of the first channel 130 may be various, such as a circle, a rectangle, an oval, and the like.
  • the first channel 130 may be disposed on a sidewall of the casing 100 along a radial direction of the casing 100. In this way, the length of the first channel 130 connecting the exterior of the casing 100 and the refrigerant flow channel 200 can be made shorter, and it is convenient to quickly provide the refrigerant to the refrigerant flow channel 200.
  • the first channel 130 may be disposed on a side wall of the casing 100 at other angles with respect to the radial direction of the casing 100.
  • the first end 210 of the refrigerant flow channel 200 may also communicate with the outside of the casing 100 through a pipe inserted at the first end 210 of the refrigerant flow channel 200.
  • the tubing may be inserted through the housing 100 to the first end 210.
  • the pipeline may be inserted into the first end 210 through the exhaust bearing seat 300.
  • the body 10 further includes a second channel 140, which is disposed on a side wall of the casing 100.
  • One end of the second channel 140 communicates with the second end 220, and the other end of the second channel 140 It communicates with the rotor cavity 110, and the refrigerant flow channel 200 communicates with the rotor cavity 110 through the second passage 140.
  • the cross-sectional shape of the second channel 140 may be various, such as a circle, a rectangle, an oval, and the like.
  • the groove 121 surrounds the outside of the rotor cavity 110, and when the groove 121 is deeper, the groove 121 may be along the axial direction of the rotor cavity 110.
  • the second channel 140 can directly communicate the intermediate pressure position of the groove 121 and the rotor cavity 110.
  • the second channel 140 may be disposed along the radial direction of the casing 100, and may communicate the groove 121 and the rotor cavity 110 with the shortest distance.
  • the body 10 further includes a third channel 150.
  • the third channel 150 is disposed on a side wall of the casing 100.
  • One end of the third channel 150 is in communication with the second end 220, and the other end of the third channel 150 is in communication with the first end.
  • the two channels 140 communicate with each other, and the second channel 140 communicates with the refrigerant flow channel 200 through the third channel 150.
  • the refrigerant flow channel 200 as an example including the groove 121 provided on the exhaust end surface 120, the groove 121 surrounds the outside of the rotor cavity 110.
  • the third channel 150 can be used to communicate the refrigerant flow channel 200 with the second channel 140, and the second channel 140 is in communication with the rotor cavity 110. This enables communication between the refrigerant flow passage 200 and the rotor cavity 110.
  • the third passage 150 By providing the third passage 150 to communicate with the second passage 140, it is easy to realize the communication between the refrigerant flow passage 200 and the rotor cavity 110, and the structure is simple.
  • the second channel 140 and the third channel 150 are perpendicular to each other, the second channel 140 is disposed along a radial direction of the casing 100, and the third channel 150 is disposed along an axial direction of the casing 100.
  • the length of the second channel 140 and the third channel 150 connecting the refrigerant flow channel 200 and the rotor cavity 110 can be made shorter, and it is convenient for the refrigerant in the refrigerant flow channel 200 to enter the rotor cavity 110 after heat exchange.
  • the second channel 140 and the third channel 150 may be disposed on the sidewall of the casing 100 at other angles.
  • the refrigerant flow channel 200 is used as an example to include the groove 121 provided on the exhaust end surface 120, and it is assumed that the depth of the groove 121 is relatively shallow.
  • a hole is drilled at the second end 220 of the groove 121 along the axial direction of the housing 100. The depth of the drilled hole is based on the middle pressure position extending to the rotor cavity 110.
  • the axial hole forms the third channel 150 described above. Calculate the end position of the aforementioned axial hole. Drill holes in the side wall of the casing 100 along the radial direction of the casing 100.
  • the radial hole and the axial hole communicate with each other, and continue to feed in the radial direction of the casing 100 to the radial hole. It penetrates into the rotor cavity 110. It can be understood that a portion of the radial hole located between the axial hole and the rotor cavity 110 forms the second channel 140 described above. The remaining part of the radial hole can be blocked with a blocking material during use.
  • An embodiment of the present application further provides a screw compressor, which includes the body 10 of any one of the above schemes. Since the above-mentioned body 10 has the above-mentioned effects, the screw compressor also has the advantages of at least a wide operating range and wide applicability.

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

Abstract

A screw compressor and a compressor body thereof. The compressor body comprises a shell (100); a rotor cavity (110) is formed inside the shell (100); the shell (100) is provided with a refrigerant flow channel (200) around the rotor cavity (110); the refrigerant flow channel (200) is close to the wall surface of the rotor cavity (110) and is used for circulating a refrigerant; and when a rotor is provided in the rotor cavity (110), the refrigerant and the rotor can conduct heat exchange by means of the wall surface of the rotor cavity (110), to cool the rotor, so that deformation of the rotor is reduced, the operating range of the compressor can be effectively widened, and the applicability of the compressor is improved.

Description

螺杆压缩机及其机体Screw compressor and its body
相关申请Related applications
本申请要求2018年08月01日申请的，申请号为201810866799.0，名称为“螺杆压缩机及其机体”的中国专利申请的优先权，在此将其全文引入作为参考。This application claims priority from a Chinese patent application filed on August 01, 2018 with an application number of 201810866799.0, entitled "Screw compressor and its body", which is hereby incorporated by reference in its entirety.
技术领域Technical field
本申请涉及压缩机技术领域，特别是涉及一种螺杆压缩机及其机体。The present application relates to the technical field of compressors, and in particular, to a screw compressor and its body.
背景技术Background technique
在螺杆压缩机转子设计中，尤其是在转子型线的设计上，通常会将阴、阳转子啮合间隙，阴转子与阴转子腔之间的间隙，以及阳转子与阳转子腔之间的间隙等设计得比较小，以防止螺杆压缩机运行时由于过多的压缩泄露而导致的能效低的现象。由于上述间隙的值设计的比较小，因此该些间隙能容纳的转子(包括阴转子和阳转子)变形的量也相应的较小。In the design of screw compressor rotors, especially in the design of the rotor profile, the female and male rotors are usually meshed with the gap, the gap between the female and female rotor cavities, and the gap between the male and male rotor cavities. The design is relatively small to prevent the low energy efficiency caused by excessive compression leakage when the screw compressor is running. Because the values of the gaps above are designed to be relatively small, the amount of deformation of the rotors (including female and male rotors) that can be accommodated by these gaps is also relatively small.
转子变形主要由转子受力变形和热变形引起。在螺杆压缩机的运行过程中，当螺杆压缩机运行至其运行范围的极限点时，转子受力变形和热变形最大。为了防止转子变形的量大于上述间隙的值而致使转子擦伤，就必须使螺杆压缩机在较窄的运行范围内运行。由此限制了螺杆压缩机的运行范围，限缩了螺杆压缩机的适用性。Rotor deformation is mainly caused by force deformation and thermal deformation of the rotor. During the operation of the screw compressor, when the screw compressor runs to the limit point of its operating range, the rotor is deformed by force and thermal deformation. In order to prevent the rotor from being deformed by an amount larger than the above-mentioned gap value, the screw compressor must be operated within a narrow operating range. This limits the operating range of the screw compressor and limits the applicability of the screw compressor.
发明内容Summary of the invention
基于此，有必要针对螺杆压缩机的运行范围受限等问题，提供一种螺杆压缩机及其机体。Based on this, it is necessary to provide a screw compressor and its body in response to problems such as a limited operation range of the screw compressor.
一种机体，包括：壳体，壳体内部设有转子腔；A machine body includes a housing, and a rotor cavity is provided inside the housing;
壳体围绕转子腔设有冷媒流道，冷媒流道靠近转子腔的壁面，冷媒流道用于流通冷媒，当转子腔中具有转子时，冷媒能够与转子通过转子腔的壁面进行热交换。The casing is provided with a refrigerant flow channel around the rotor cavity. The refrigerant flow channel is close to the wall surface of the rotor cavity. The refrigerant flow channel is used for circulating the refrigerant. When the rotor cavity has the rotor, the refrigerant can exchange heat with the rotor through the wall surface of the rotor cavity.
在其中一个实施例中，机体还包括排气轴承座，排气轴承座用于与壳体的排气端密封连接；In one embodiment, the machine body further includes an exhaust bearing seat, and the exhaust bearing seat is used for sealing connection with the exhaust end of the housing;
壳体的排气端面设置有凹槽，凹槽沿转子腔的周向延伸，排气轴承座与壳体连接时，排气轴承座覆盖凹槽，凹槽与排气轴承座之间的空间形成冷媒流道。The exhaust end face of the casing is provided with a groove, which extends in the circumferential direction of the rotor cavity. When the exhaust bearing seat is connected to the casing, the exhaust bearing seat covers the groove, and the space between the groove and the exhaust bearing seat Form refrigerant flow channels.
在其中一个实施例中，冷媒流道包括第一端和第二端，第一端与壳体的外部连通，第二端与转子腔连通，冷媒流道中的冷媒的流向由第一端至第二端。In one embodiment, the refrigerant flow path includes a first end and a second end. The first end is in communication with the outside of the housing, and the second end is in communication with the rotor cavity. The flow direction of the refrigerant in the refrigerant flow path is from the first end to the first end. Both ends.
在其中一个实施例中，机体还包括第一通道，第一通道设置于壳体的侧壁，第一通道的一端与第一端连通，第一通道的另一端与壳体的外部连通，冷媒流道通过第一通道与壳体的外部连通。In one of the embodiments, the body further includes a first channel, the first channel is provided on a side wall of the casing, one end of the first channel is communicated with the first end, and the other end of the first channel is communicated with the outside of the casing. The flow passage communicates with the outside of the casing through the first passage.
在其中一个实施例中，第一通道沿壳体的径向设置于壳体的侧壁。In one embodiment, the first channel is disposed on a sidewall of the casing along a radial direction of the casing.
在其中一个实施例中，机体还包括第二通道，第二通道设置于壳体的侧壁，第二通道的一端与第二端连通，第二通道的另一端与转子腔连通，冷媒流道通过第二通道与转子腔连通。In one of the embodiments, the body further includes a second channel, the second channel is disposed on a side wall of the housing, one end of the second channel communicates with the second end, the other end of the second channel communicates with the rotor cavity, and the refrigerant flow channel It communicates with the rotor cavity through the second channel.
在其中一个实施例中，机体还包括第三通道，第三通道设置于壳体的侧壁，第三通道的一端与第二端连通，第三通道的另一端与第二通道连通，第二通道通过第三通道与冷媒流道连通。In one embodiment, the body further includes a third channel, the third channel is disposed on a side wall of the housing, one end of the third channel is in communication with the second end, the other end of the third channel is in communication with the second channel, and the second The passage communicates with the refrigerant flow passage through the third passage.
在其中一个实施例中，第二通道和第三通道相互垂直，第二通道沿壳体的径向设置，第三通道沿壳体的轴向设置。In one embodiment, the second channel and the third channel are perpendicular to each other, the second channel is disposed along a radial direction of the casing, and the third channel is disposed along an axial direction of the casing.
在其中一个实施例中，转子腔包括阳转子腔和阴转子腔，冷媒流道包围阳转子腔和阴转子腔。In one embodiment, the rotor cavity includes a male rotor cavity and a female rotor cavity, and a refrigerant flow path surrounds the male rotor cavity and the female rotor cavity.
一种螺杆压缩机，包括以上任一方案的机体。A screw compressor includes the body of any one of the above schemes.
通过在壳体上设置冷媒流道，该冷媒流道能够流通冷媒，利用冷媒与转子进行热交换可以给转子降温，从而减小了转子的变形量。当压缩机使用该机体时，可以有效拓宽压缩机的运行范围，提高压缩机的适用性。By providing a refrigerant flow channel on the casing, the refrigerant flow channel can circulate the refrigerant, and the heat exchange between the refrigerant and the rotor can cool the rotor, thereby reducing the amount of deformation of the rotor. When the compressor uses the body, it can effectively widen the operating range of the compressor and improve the applicability of the compressor.
附图说明BRIEF DESCRIPTION OF THE DRAWINGS
以下将参照附图对根据本申请的螺杆压缩机及其机体的优选实施方式进行描述。图中：Hereinafter, preferred embodiments of the screw compressor and its body according to the present application will be described with reference to the drawings. In the picture:
图1为本申请一实施例提供的机体的结构示意图；FIG. 1 is a schematic structural diagram of a body provided by an embodiment of the present application; FIG.
图2为图1所示结构中壳体的结构示意图。FIG. 2 is a schematic structural diagram of a casing in the structure shown in FIG. 1.
其中：among them:
10-机体；10-body;
100-壳体；100-shell;
110-转子腔；111-阳转子腔；112-阴转子腔；110-rotor cavity; 111-male rotor cavity; 112-female rotor cavity;
120-排气端面；121-凹槽；120- exhaust face; 121-groove;
130-第一通道；140-第二通道；150-第三通道；130-first channel; 140-second channel; 150-third channel;
200-冷媒流道；200-refrigerant flow channel;
210-第一端；220-第二端；210-first end; 220-second end;
300-排气轴承座。300-Exhaust bearing seat.
具体实施方式detailed description
为了使本申请的目的、技术方案及优点更加清楚明白，以下通过实施例，并结合附图，对本申请的螺杆压缩机及其机体进行进一步详细说明。应当理解，此处所描述的具体实施例仅用以解释本申请，并不用于限定本申请。In order to make the purpose, technical solution, and advantages of the present application clearer, the screw compressor and its body of the present application will be further described in detail below through embodiments and the accompanying drawings. It should be understood that the specific embodiments described herein are only used to explain the application, and are not used to limit the application.
需要说明的是，当元件被称为“固定于”另一个元件，它可以直接在另一个元件上或者也可以存在居中的元件。当一个元件被认为是“连接”另一个元件，它可以是直接连接到另一个元件或者可能同时存在居中元件。相反，当元件被称作“直接在”另一元件“上”时，不存在中间元件。本文所使用的术语“垂直的”、“水平的”、“左”、“右”以及类似的表述只是为了说明的目的。It should be noted that when an element is referred to as being “fixed to” another element, it may be directly on the other element or there may be a centered element. When an element is considered to be "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. In contrast, when an element is referred to as being "directly on" another element, there are no intervening elements present. The terms "vertical", "horizontal", "left", "right" and similar expressions used herein are for illustrative purposes only.
压缩机的运行范围大小决定压缩机的适用场所多样性，是控制压缩机产品竞争能力的重要因素之一。所谓压缩机的运行范围，指的是压缩机在一定范围内的蒸发/冷凝温度内都可以正常运行，该范围就是压缩机的运行范围。本申请的螺杆压缩机及其机体，能够具有较宽的运行范围。The size of the compressor's operating range determines the variety of places where the compressor can be used, and is one of the important factors controlling the competitiveness of compressor products. The so-called compressor operating range means that the compressor can operate normally within a certain range of evaporation / condensation temperature, and this range is the operating range of the compressor. The screw compressor and its body of the present application can have a wide operating range.
请参见图1和图2，本申请一实施例提供的机体10，包括：壳体100，壳体100内部设有转子腔110。转子腔110是用于容置转子的，转子可在转子腔110内绕转子轴转动。壳体100围绕转子腔110设有冷媒流道200，冷媒流道200靠近转子腔110的壁面，冷媒流道200用于流通冷媒。当转子腔110中具有转子时，冷媒能够与转子通过转子腔110的壁面进行热交换。通过设置冷媒流道200，利用冷媒流道200中流通的冷媒与转子进行热交换，从而能够降低转子的温度，从而减小的转子的热变形，进而减小了转子的变形量。当压缩机使用该机体10时，由于转子的变形量有效减小，因此压缩机的可运行范围相对增大。从而有效提高了压缩机的适用场所多样性，提升了压缩机产品的竞争能力。1 and FIG. 2, a body 10 provided by an embodiment of the present application includes a housing 100, and a rotor cavity 110 is provided inside the housing 100. The rotor cavity 110 is used for accommodating a rotor, and the rotor is rotatable about the rotor shaft in the rotor cavity 110. The casing 100 is provided with a refrigerant flow channel 200 around the rotor cavity 110. The refrigerant flow channel 200 is close to the wall surface of the rotor cavity 110. The refrigerant flow channel 200 is used for circulating the refrigerant. When a rotor is provided in the rotor cavity 110, the refrigerant can exchange heat with the rotor through the wall surface of the rotor cavity 110. By providing the refrigerant flow channel 200, the refrigerant flowing through the refrigerant flow channel 200 is used to exchange heat with the rotor, thereby reducing the temperature of the rotor, thereby reducing the thermal deformation of the rotor, and further reducing the amount of deformation of the rotor. When the compressor uses the body 10, since the amount of deformation of the rotor is effectively reduced, the operable range of the compressor is relatively enlarged. As a result, the diversity of compressor application places is effectively improved, and the competitiveness of compressor products is enhanced.
作为一种可实施的方式，转子腔110包括阳转子腔111和阴转子腔112，冷媒流道200包围阳转子腔111和阴转子腔112。可以理解，阳转子腔111的内部可以转动设置有阳转子，阴转子腔112的内部可转动设置有阴转子。冷媒流道200包围阳转子腔111和阴转子腔112，冷媒流道200中流通的冷媒能够与阳转子通过阳转子腔111的壁面进行热交换，冷媒还能够与阴转子通过阴转子腔112的壁面进行热交换。因此能够有效减小阳转子和阴 转子的变形量，进而拓宽压缩机的运行范围。As an implementable manner, the rotor cavity 110 includes a male rotor cavity 111 and a female rotor cavity 112, and a refrigerant flow channel 200 surrounds the male rotor cavity 111 and the female rotor cavity 112. It can be understood that the inside of the male rotor cavity 111 can be rotatably provided with a male rotor, and the inside of the female rotor cavity 112 can be rotatably provided with a female rotor. The refrigerant runner 200 surrounds the male rotor cavity 111 and the female rotor cavity 112. The refrigerant flowing in the refrigerant runner 200 can exchange heat with the male rotor through the wall surface of the male rotor cavity 111. The walls are heat exchanged. Therefore, the amount of deformation of the male and female rotors can be effectively reduced, and the operating range of the compressor can be widened.
冷媒流道200的结构形式可以为多种。如图1和图2所示，作为一种可实施的方式，机体10还包括排气轴承座300，排气轴承座300用于与壳体100的排气端密封连接。壳体100的排气端面120设置有凹槽121，凹槽121沿转子腔110的周向延伸，排气轴承座300与壳体100连接时，排气轴承座300覆盖凹槽121，凹槽121与排气轴承座300之间的空间形成冷媒流道200。本实施例中，冷媒流道200包括设置于壳体100的排气端面120的凹槽121，该凹槽121可利用壳体100与排气轴承座300的密封连接形成流通冷媒的冷媒流道200。如此设计，结构简单且便于加工，同时便于形成封闭的冷媒流道200。并且冷媒流道200的形成灵活利用了排气轴承座300与壳体100的密封连接，无需额外设置其他结构来形成封闭的冷媒流道200。此外，将冷媒流道200设置于排气端面120的位置，可有效针对转子热变形最大处给转子降温，由此可直接有效地减小转子的热变形，进而减小转子的变形量。The structure of the refrigerant flow channel 200 may be various. As shown in FIG. 1 and FIG. 2, as an implementable manner, the body 10 further includes an exhaust bearing seat 300, and the exhaust bearing seat 300 is used for sealing connection with the exhaust end of the housing 100. The exhaust end surface 120 of the housing 100 is provided with a groove 121, and the groove 121 extends in the circumferential direction of the rotor cavity 110. When the exhaust bearing housing 300 is connected to the housing 100, the exhaust bearing housing 300 covers the groove 121, the groove A space between 121 and the exhaust bearing housing 300 forms a refrigerant flow path 200. In this embodiment, the refrigerant flow channel 200 includes a groove 121 provided on the exhaust end surface 120 of the housing 100. The groove 121 can form a refrigerant flow channel through which the refrigerant is circulated through the sealed connection between the housing 100 and the exhaust bearing housing 300. 200. With this design, the structure is simple and easy to process, and at the same time, it is convenient to form a closed refrigerant flow channel 200. In addition, the formation of the refrigerant flow channel 200 makes flexible use of the sealed connection between the exhaust bearing seat 300 and the casing 100, and no additional structure is required to form a closed refrigerant flow channel 200. In addition, setting the refrigerant flow channel 200 at the position of the exhaust end surface 120 can effectively cool the rotor according to the maximum thermal deformation of the rotor, thereby directly and effectively reducing the thermal deformation of the rotor, thereby reducing the amount of deformation of the rotor.
以双转子结构的机体10为例，可以理解，转子包括阴转子和阳转子。由于阴转子齿形关系，阴转子的变形量都会比阳转子大，因此，主要针对阴转子的变形量进行分析。经过仿真实验分析，阴转子变形最大点集中在阴转子靠近排气端的齿顶位置。并且，阴转子在同一极限范围点运行时，从受力与热两方面进行耦合分析可知，热力耦合后的阴转子变形量增大了许多，变形最大值依旧在排气端面120附近，但变形量大的位置明显增多。综合可知，热变形对转子变形量的影响较大，且转子热变形最大位置是靠近排气端面120附近的转子齿顶位置。可以理解，转子齿顶靠近转子腔110的壁面。因此通过设置流通冷媒的冷媒流道200，可有效与转子进行热交换，降低转子的温度，减小转子的变形。且冷媒流道200设置于机体10的排气端面120，可直接有效地对转子变形最大位置进行降温，从根源上使转子发热降低，从而减小转子变形，保证压缩机在较宽运行范围内的可靠运行。Taking the body 10 with a dual rotor structure as an example, it can be understood that the rotor includes a female rotor and a male rotor. Due to the tooth shape of the female rotor, the amount of deformation of the female rotor is greater than that of the male rotor. Therefore, the analysis is mainly performed on the amount of deformation of the female rotor. After the simulation experiment analysis, the maximum deformation point of the female rotor is concentrated on the tooth top position of the female rotor near the exhaust end. In addition, when the female rotor is operating at the same limit range point, it is known from the coupling analysis of the force and heat that the deformation of the female rotor after thermal coupling has increased a lot, and the maximum deformation is still near the exhaust end face 120, but the deformation Significantly increased the number of locations. In general, it can be known that the thermal deformation has a large effect on the amount of deformation of the rotor, and the maximum position of the rotor thermal deformation is the position of the rotor tooth near the exhaust end face 120. It can be understood that the rotor crest is close to the wall surface of the rotor cavity 110. Therefore, by providing the refrigerant flow channel 200 for circulating the refrigerant, heat exchange with the rotor can be effectively performed, the temperature of the rotor can be reduced, and the deformation of the rotor can be reduced. Moreover, the refrigerant flow channel 200 is arranged on the exhaust end surface 120 of the body 10, which can directly and effectively cool the maximum position of the rotor deformation, reduce the heating of the rotor from the root cause, thereby reducing the rotor deformation and ensuring that the compressor operates in a wide operating range. Reliable operation.
凹槽121的截面形状可以为多种，例如矩形、U形等等。从理论上来说，冷媒流道200越靠近转子腔110的壁面越好，如此可充分与转子热交换。但是从实际角度出发，以冷媒流道200为包括设置于排气端面120的凹槽121为例，凹槽121与转子腔110的壁面之间的距离需要根据机体10的类型，以及壳体100的材质等具体设置。凹槽121的深度也需要根据实际情况，比如凹槽121的形状、凹槽121与转子腔110的壁面之间的距离等来具体设计。以保证在具有良好的换热效果的同时，保证壳体100的结构强度，保证机体10的可靠运行。The cross-sectional shape of the groove 121 may be various, such as rectangular, U-shaped, and the like. Theoretically, the closer the refrigerant flow path 200 is to the wall surface of the rotor cavity 110, the better, so that it can fully exchange heat with the rotor. However, from a practical perspective, taking the refrigerant runner 200 as an example of the groove 121 provided on the exhaust end surface 120, the distance between the groove 121 and the wall surface of the rotor cavity 110 needs to be based on the type of the body 10 and the housing 100. Material and other specific settings. The depth of the groove 121 also needs to be specifically designed according to the actual situation, such as the shape of the groove 121, the distance between the groove 121 and the wall surface of the rotor cavity 110, and the like. In order to ensure a good heat exchange effect, the structural strength of the casing 100 is ensured, and the reliable operation of the body 10 is ensured.
在其他实施例中，冷媒流道200还可以包括多个沿着壳体100的轴向延伸的子流道，多个子流道围绕转子腔110间隔设置。或者冷媒流道200还可以为其他结构形式，只要其 能够流通冷媒，以实现与转子热交换的目的即可。In other embodiments, the refrigerant flow passage 200 may further include a plurality of sub flow passages extending along the axial direction of the casing 100, and the plurality of sub flow passages are disposed at intervals around the rotor cavity 110. Alternatively, the refrigerant flow channel 200 may have other structural forms, as long as it can circulate the refrigerant to achieve the purpose of heat exchange with the rotor.
参见图2，作为一种可实施的方式，冷媒流道200包括第一端210和第二端220，第一端210与壳体100的外部连通，第二端220与转子腔110连通，冷媒流道200中的冷媒的流向由第一端210至第二端220。需要说明的是，冷媒流道200的第二端220与转子腔110连通，具体指的是与转子腔110的中间压力位置连通，中间压力位置一般是指开始压缩到压缩完成之间的压力不大也不小的区域。而第一端210与壳体100的外部连通，因此冷媒流道200可通过第一端210自壳体100的外部引入低温液态冷媒，以与转子进行热交换。换热后的冷媒吸热变为蒸汽，通过第二端220引入至转子腔110的中间压力位置，可起到补气的作用，从而有效提升压缩机的能效。通过如此设计，便于实现冷媒的不断循环流通，在保证良好的换热效果的同时可起到补气增效的作用。在转子腔110包括阳转子腔111和阴转子腔112时，第一端210、第二端220可分别设置于阳转子腔111的外侧和阴转子腔112的外侧，而冷媒的流向可以是由阳转子腔111一侧流向阴转子腔112一侧，也可以是由阴转子腔111一侧流向阳转子腔112一侧。Referring to FIG. 2, as an implementable manner, the refrigerant flow channel 200 includes a first end 210 and a second end 220. The first end 210 is in communication with the outside of the housing 100, and the second end 220 is in communication with the rotor cavity 110. The flow direction of the refrigerant in the flow path 200 is from the first end 210 to the second end 220. It should be noted that the second end 220 of the refrigerant flow channel 200 is in communication with the rotor cavity 110, specifically, it is in communication with the intermediate pressure position of the rotor cavity 110, and the intermediate pressure position generally refers to the pressure between the start of compression and the completion of compression. Big or small area. The first end 210 is in communication with the outside of the casing 100, so the refrigerant flow channel 200 can introduce a low-temperature liquid refrigerant from the outside of the casing 100 through the first end 210 to perform heat exchange with the rotor. After the heat exchange, the refrigerant absorbs heat and turns into steam, which is introduced to the intermediate pressure position of the rotor cavity 110 through the second end 220, and can play a role of supplementing air, thereby effectively improving the energy efficiency of the compressor. With this design, it is convenient to realize the continuous circulation and circulation of the refrigerant, and it can play a role of supplementing gas and increasing efficiency while ensuring a good heat exchange effect. When the rotor cavity 110 includes a male rotor cavity 111 and a female rotor cavity 112, the first end 210 and the second end 220 may be respectively disposed outside the male rotor cavity 111 and the female rotor cavity 112, and the flow direction of the refrigerant may be determined by The male rotor cavity 111 side flows to the female rotor cavity 112 side, or the female rotor cavity 111 side can flow to the male rotor cavity 112 side.
在其他实施例中，冷媒流道200还可以是围绕转子腔110呈环形的结构。以冷媒流道200为包括设置于排气端面120的凹槽121为例，凹槽121可以是沿转子腔110周向延伸呈环形的凹槽。可以理解，凹槽121可设有用于输入冷媒的进口，以及输出冷媒的出口。In other embodiments, the refrigerant flow channel 200 may also have a ring-shaped structure around the rotor cavity 110. Taking the refrigerant flow passage 200 as an example including the groove 121 provided on the exhaust end surface 120, the groove 121 may be a groove extending in a ring shape along the circumferential direction of the rotor cavity 110. It can be understood that the groove 121 may be provided with an inlet for inputting the refrigerant and an outlet for outputting the refrigerant.
前述第一端210与壳体100的外部连通的方式有多种。作为一种可实施的方式，机体10还包括第一通道130，第一通道130设置于壳体100的侧壁，第一通道130的一端与第一端210连通，第一通道130的另一端与壳体100的外部连通，冷媒流道200通过第一通道130与壳体100的外部连通。第一通道130的横截面形状可以为多种，例如圆形、矩形、椭圆形等等。通过设置第一通道130，可便于连通冷媒流道200和壳体100的外部，以便于向冷媒流道200供给冷媒。There are various ways for the first end 210 to communicate with the outside of the housing 100. As an implementable manner, the body 10 further includes a first channel 130, which is disposed on a side wall of the casing 100. One end of the first channel 130 communicates with the first end 210, and the other end of the first channel 130 The refrigerant flow passage 200 communicates with the outside of the casing 100 through the first passage 130. The cross-sectional shape of the first channel 130 may be various, such as a circle, a rectangle, an oval, and the like. By providing the first channel 130, the refrigerant flow channel 200 and the outside of the casing 100 can be easily communicated, so that the refrigerant is supplied to the refrigerant flow channel 200.
在一个实施例中，第一通道130可以沿壳体100的径向设置于壳体100的侧壁。如此设计，可使得连通壳体100的外部和冷媒流道200的第一通道130的长度较短，便于快速地向冷媒流道200提供冷媒。或者，第一通道130还可以是以相对于壳体100的径向呈其它角度设置于壳体100的侧壁。In one embodiment, the first channel 130 may be disposed on a sidewall of the casing 100 along a radial direction of the casing 100. In this way, the length of the first channel 130 connecting the exterior of the casing 100 and the refrigerant flow channel 200 can be made shorter, and it is convenient to quickly provide the refrigerant to the refrigerant flow channel 200. Alternatively, the first channel 130 may be disposed on a side wall of the casing 100 at other angles with respect to the radial direction of the casing 100.
当然，在其他实施例中，冷媒流道200的第一端210还可以是通过***至冷媒流道200的第一端210处的管路与壳体100的外部连通。该管路可以是穿过壳体100***至第一端210。或者，该管路还可以是穿过排气轴承座300***至第一端210。Of course, in other embodiments, the first end 210 of the refrigerant flow channel 200 may also communicate with the outside of the casing 100 through a pipe inserted at the first end 210 of the refrigerant flow channel 200. The tubing may be inserted through the housing 100 to the first end 210. Alternatively, the pipeline may be inserted into the first end 210 through the exhaust bearing seat 300.
前述第二端220与转子腔110连通的方式有多种。作为一种可实施的方式，机体10还包括第二通道140，第二通道140设置于壳体100的侧壁，第二通道140的一端与第二 端220连通，第二通道140的另一端与转子腔110连通，冷媒流道200通过第二通道140与转子腔110连通。第二通道140的横截面形状可以为多种，例如圆形、矩形、椭圆形等等。以冷媒流道200为包括设置于排气端面120的凹槽121为例，凹槽121围绕于转子腔110外侧，在凹槽121深度较深时，凹槽121沿转子腔110的轴向可延伸到转子腔110的中间压力位置，利用第二通道140可直接连通凹槽121和转子腔110的中间压力位置。第二通道140可以是沿壳体100的径向设置，可实现以最短的距离连通凹槽121和转子腔110。通过设置第二通道140，易于实现冷媒流道200与转子腔110的连通，结构简单。There are various ways for the second end 220 to communicate with the rotor cavity 110. As an implementable manner, the body 10 further includes a second channel 140, which is disposed on a side wall of the casing 100. One end of the second channel 140 communicates with the second end 220, and the other end of the second channel 140 It communicates with the rotor cavity 110, and the refrigerant flow channel 200 communicates with the rotor cavity 110 through the second passage 140. The cross-sectional shape of the second channel 140 may be various, such as a circle, a rectangle, an oval, and the like. Taking the refrigerant flow channel 200 as an example including the groove 121 provided on the exhaust end surface 120, the groove 121 surrounds the outside of the rotor cavity 110, and when the groove 121 is deeper, the groove 121 may be along the axial direction of the rotor cavity 110. Extending to the intermediate pressure position of the rotor cavity 110, the second channel 140 can directly communicate the intermediate pressure position of the groove 121 and the rotor cavity 110. The second channel 140 may be disposed along the radial direction of the casing 100, and may communicate the groove 121 and the rotor cavity 110 with the shortest distance. By providing the second passage 140, it is easy to realize the communication between the refrigerant flow passage 200 and the rotor cavity 110, and the structure is simple.
在一个实施例中，机体10还包括第三通道150，第三通道150设置于壳体100的侧壁，第三通道150的一端与第二端220连通，第三通道150的另一端与第二通道140连通，第二通道140通过第三通道150与冷媒流道200连通。以冷媒流道200为包括设置于排气端面120的凹槽121为例，凹槽121围绕于转子腔110外侧。在凹槽121的深度不足以到达转子腔110的中间压力位置时，可利用第三通道150将冷媒流道200与第二通道140连通，而第二通道140与转子腔110是连通的，由此能够实现冷媒流道200和转子腔110的连通。通过设置第三通道150与第二通道140连通，易于实现冷媒流道200与转子腔110的连通，结构简单。In one embodiment, the body 10 further includes a third channel 150. The third channel 150 is disposed on a side wall of the casing 100. One end of the third channel 150 is in communication with the second end 220, and the other end of the third channel 150 is in communication with the first end. The two channels 140 communicate with each other, and the second channel 140 communicates with the refrigerant flow channel 200 through the third channel 150. Taking the refrigerant flow channel 200 as an example including the groove 121 provided on the exhaust end surface 120, the groove 121 surrounds the outside of the rotor cavity 110. When the depth of the groove 121 is not enough to reach the intermediate pressure position of the rotor cavity 110, the third channel 150 can be used to communicate the refrigerant flow channel 200 with the second channel 140, and the second channel 140 is in communication with the rotor cavity 110. This enables communication between the refrigerant flow passage 200 and the rotor cavity 110. By providing the third passage 150 to communicate with the second passage 140, it is easy to realize the communication between the refrigerant flow passage 200 and the rotor cavity 110, and the structure is simple.
在一个实施例中，第二通道140和第三通道150相互垂直，第二通道140沿壳体100的径向设置，第三通道150沿壳体100的轴向设置。如此设计，可使得连通冷媒流道200和转子腔110的第二通道140和第三通道150的长度较短，便于快速地使冷媒流道200中换热后的冷媒进入到转子腔110。或者，第二通道140、第三通道150还可以是以其它角度设置于壳体100的侧壁。In one embodiment, the second channel 140 and the third channel 150 are perpendicular to each other, the second channel 140 is disposed along a radial direction of the casing 100, and the third channel 150 is disposed along an axial direction of the casing 100. In this way, the length of the second channel 140 and the third channel 150 connecting the refrigerant flow channel 200 and the rotor cavity 110 can be made shorter, and it is convenient for the refrigerant in the refrigerant flow channel 200 to enter the rotor cavity 110 after heat exchange. Alternatively, the second channel 140 and the third channel 150 may be disposed on the sidewall of the casing 100 at other angles.
实际在加工第二通道140和第三通道150时，以冷媒流道200为包括设置于排气端面120的凹槽121为例，假设凹槽121深度比较浅。在凹槽121的第二端220沿壳体100的轴向钻孔，钻孔深度以延伸到转子腔110的中间压力位置为准，该轴向的孔形成上述的第三通道150。计算前述轴向孔的末端位置，在壳体100侧壁沿壳体100径向钻孔，至径向的孔与轴向孔相互连通，继续沿壳体100径向进给直至径向的孔贯穿到转子腔110内。可以理解，该径向的孔位于轴向孔和转子腔110之间的部分形成上述的第二通道140。而径向孔的其余部分在使用时可利用封堵材料进行封堵。Actually, when the second channel 140 and the third channel 150 are processed, the refrigerant flow channel 200 is used as an example to include the groove 121 provided on the exhaust end surface 120, and it is assumed that the depth of the groove 121 is relatively shallow. A hole is drilled at the second end 220 of the groove 121 along the axial direction of the housing 100. The depth of the drilled hole is based on the middle pressure position extending to the rotor cavity 110. The axial hole forms the third channel 150 described above. Calculate the end position of the aforementioned axial hole. Drill holes in the side wall of the casing 100 along the radial direction of the casing 100. The radial hole and the axial hole communicate with each other, and continue to feed in the radial direction of the casing 100 to the radial hole. It penetrates into the rotor cavity 110. It can be understood that a portion of the radial hole located between the axial hole and the rotor cavity 110 forms the second channel 140 described above. The remaining part of the radial hole can be blocked with a blocking material during use.
本申请一实施例还提供了一种螺杆压缩机，包括以上任一方案的机体10。由于上述机体10具有上述效果，该螺杆压缩机也至少具有运行范围宽，适用性广的优点。An embodiment of the present application further provides a screw compressor, which includes the body 10 of any one of the above schemes. Since the above-mentioned body 10 has the above-mentioned effects, the screw compressor also has the advantages of at least a wide operating range and wide applicability.
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛 盾，都应当认为是本说明书记载的范围。The technical features of the embodiments described above can be arbitrarily combined. In order to simplify the description, all possible combinations of the technical features in the above embodiments have not been described. However, as long as there is no contradiction in the combination of these technical features, It should be considered as the scope described in this specification.
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对申请专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请专利的保护范围应以所附权利要求为准。The above-mentioned embodiments only express several implementation manners of the present application, and their descriptions are more specific and detailed, but they cannot be understood as a limitation on the scope of patent application. It should be noted that, for those of ordinary skill in the art, without departing from the concept of the present application, several modifications and improvements can be made, which all belong to the protection scope of the present application. Therefore, the protection scope of this application patent shall be subject to the appended claims.

Claims (10)

  1. 一种机体，其特征在于，包括：壳体(100)，所述壳体(100)内部设有转子腔(110)；A machine body, comprising: a housing (100), wherein a rotor cavity (110) is provided inside the housing (100);
    所述壳体(100)围绕所述转子腔(110)设有冷媒流道(200)，所述冷媒流道(200)靠近所述转子腔(110)的壁面，所述冷媒流道(200)用于流通冷媒，当所述转子腔(110)中具有转子时，所述冷媒能够与所述转子通过所述转子腔(110)的壁面进行热交换。The casing (100) is provided with a refrigerant flow path (200) around the rotor cavity (110), the refrigerant flow path (200) is close to a wall surface of the rotor cavity (110), and the refrigerant flow path (200) ) Is used for circulating a refrigerant, and when a rotor is provided in the rotor cavity (110), the refrigerant can perform heat exchange with the rotor through a wall surface of the rotor cavity (110).
  2. 根据权利要求1所述的机体，其特征在于，还包括排气轴承座(300)，所述排气轴承座(300)用于与所述壳体(100)的排气端密封连接；The body according to claim 1, further comprising an exhaust bearing housing (300), which is used for sealing connection with an exhaust end of the housing (100);
    所述壳体(100)的排气端面(120)设置有凹槽(121)，所述凹槽(121)沿所述转子腔(110)的周向延伸，所述排气轴承座(300)与所述壳体(100)连接时，所述排气轴承座(300)覆盖所述凹槽(121)，所述凹槽(121)与所述排气轴承座(300)之间的空间形成所述冷媒流道(200)。An exhaust end surface (120) of the housing (100) is provided with a groove (121), the groove (121) extends in a circumferential direction of the rotor cavity (110), and the exhaust bearing housing (300) ) When connected to the housing (100), the exhaust bearing housing (300) covers the groove (121), and the space between the groove (121) and the exhaust bearing housing (300) The space forms the refrigerant flow path (200).
  3. 根据权利要求1或2所述的机体，其特征在于，所述冷媒流道(200)包括第一端(210)和第二端(220)，所述第一端(210)与所述壳体(100)的外部连通，所述第二端(220)与所述转子腔(110)连通，所述冷媒流道(200)中的冷媒的流向由所述第一端(210)至所述第二端(220)。The airframe according to claim 1 or 2, wherein the refrigerant channel (200) comprises a first end (210) and a second end (220), and the first end (210) and the shell The body (100) communicates with the outside, the second end (220) communicates with the rotor cavity (110), and the flow direction of the refrigerant in the refrigerant flow path (200) is from the first end (210) to the Said second end (220).
  4. 根据权利要求3所述的机体，其特征在于，还包括第一通道(130)，所述第一通道(130)设置于所述壳体(100)的侧壁，所述第一通道(130)的一端与所述第一端(210)连通，所述第一通道(130)的另一端与所述壳体(100)的外部连通，所述冷媒流道(200)通过所述第一通道(130)与所述壳体(100)的外部连通。The body according to claim 3, further comprising a first channel (130), the first channel (130) being disposed on a side wall of the housing (100), and the first channel (130) ) Is in communication with the first end (210), the other end of the first channel (130) is in communication with the outside of the casing (100), and the refrigerant flow path (200) passes through the first The channel (130) communicates with the outside of the casing (100).
  5. 根据权利要求3所述的机体，其特征在于，所述第一通道(130)沿所述壳体(100)的径向设置于所述壳体(100)的侧壁。The body according to claim 3, wherein the first channel (130) is provided on a side wall of the casing (100) along a radial direction of the casing (100).
  6. 根据权利要求3所述的机体，其特征在于，还包括第二通道(140)，所述第二通道(140)设置于所述壳体(100)的侧壁，所述第二通道(140)的一端与所述第二端(220)连通，所述第二通道(140)的另一端与所述转子腔(110)连通，所述冷媒流道(200)通过所述第二通道(140)与所述转子腔(110)连通。The body according to claim 3, further comprising a second channel (140), which is disposed on a side wall of the casing (100), and the second channel (140) ) Is in communication with the second end (220), the other end of the second channel (140) is in communication with the rotor cavity (110), and the refrigerant passage (200) passes through the second channel ( 140) is in communication with the rotor cavity (110).
  7. 根据权利要求6所述的机体，其特征在于，还包括第三通道(150)，所述第三通道(150)设置于所述壳体(100)的侧壁，所述第三通道(150)的一端与所述第二端(220)连通，所述第三通道(150)的另一端与所述第二通道(140)连通，所述第二通道(140)通过所述第三通道(150)与所述冷媒流道(200)连通。The body according to claim 6, further comprising a third channel (150), the third channel (150) being disposed on a side wall of the casing (100), and the third channel (150) ) Is in communication with the second end (220), the other end of the third passage (150) is in communication with the second passage (140), and the second passage (140) passes through the third passage (150) communicates with the refrigerant flow path (200).
  8. 根据权利要求7所述的机体，其特征在于，所述第二通道(140)和所述第三通道(150)相互垂直，所述第二通道(140)沿所述壳体(100)的径向设置，所述第三通道(150)沿所述壳体(100)的轴向设置。The body according to claim 7, characterized in that the second channel (140) and the third channel (150) are perpendicular to each other, and the second channel (140) runs along the housing (100). Radially disposed, the third channel (150) is disposed along the axial direction of the casing (100).
  9. 根据权利要求1所述的机体，其特征在于，所述转子腔(110)包括阳转子腔(111)和阴转子腔(112)，所述冷媒流道(200)包围所述阳转子腔(111)和所述阴转子腔(112)。The airframe according to claim 1, wherein the rotor cavity (110) comprises a male rotor cavity (111) and a female rotor cavity (112), and the refrigerant flow channel (200) surrounds the male rotor cavity (200). 111) and the female rotor cavity (112).
  10. 一种螺杆压缩机，包括如权利要求1-9任一项所述的机体(10)。A screw compressor comprising the body (10) according to any one of claims 1-9.
PCT/CN2018/120602 2018-08-01 2018-12-12 Screw compressor and compressor body thereof WO2020024514A1 (en)

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CN108843568B (en) * 2018-08-01 2024-05-17 珠海格力电器股份有限公司 Screw compressor and machine body thereof
CN111255695A (en) * 2020-02-10 2020-06-09 嘉兴学院 Screw air compressor
CN111878403B (en) * 2020-08-24 2024-04-23 珠海格力电器股份有限公司 Compressor air supplementing mechanism, compressor and compressor air supplementing method

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