WO2022041562A1 - 静涡旋盘组件、涡旋压缩机和制冷设备 - Google Patents

静涡旋盘组件、涡旋压缩机和制冷设备 Download PDF

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Publication number
WO2022041562A1
WO2022041562A1 PCT/CN2020/134876 CN2020134876W WO2022041562A1 WO 2022041562 A1 WO2022041562 A1 WO 2022041562A1 CN 2020134876 W CN2020134876 W CN 2020134876W WO 2022041562 A1 WO2022041562 A1 WO 2022041562A1
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Prior art keywords
enthalpy
channel
injection
increasing
compression
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PCT/CN2020/134876
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English (en)
French (fr)
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杨帆
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广东美芝制冷设备有限公司
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Publication of WO2022041562A1 publication Critical patent/WO2022041562A1/zh

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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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0292—Ports or channels located in the wrap
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements

Definitions

  • the present application relates to the technical field of refrigeration devices, and in particular, to a stationary scroll assembly, a scroll compressor, and a refrigeration device.
  • Scroll compressor is a new type of positive displacement fluid machinery, mainly composed of moving and stationary scrolls, crankshaft, bracket body, anti-rotation cross slip ring and other components. Compared with traditional reciprocating, rotor, screw and other compressors, it has many excellent characteristics such as fewer parts, high volumetric efficiency, continuous and stable compression process, and low vibration and noise. in the heat pump system. As the core equipment of the refrigeration system, the performance of the scroll compressor directly determines the heat exchange effect of the system. When the external ambient temperature is constant, the traditional scroll compressor often has the phenomenon that the amount of refrigerant circulation decreases and the heating capacity is insufficient during the working process.
  • an enthalpy injection channel 112 for supplementing air is provided on the disc body 110 ′ of the fixed scroll assembly 100 ′.
  • the enthalpy increasing channel 117' to introduce the refrigerant gas from the refrigeration system into the middle pressure chamber part of the compression chamber 240' through the enthalpy increasing pipeline 210'.
  • the large displacement greatly improves the heating capacity of the scroll compressor 200'.
  • the enthalpy-increasing air flow is injected into the compression chamber 240' to achieve the effect of supplementing air; but when the enthalpy-increasing pressure is lower than the pressure in the compression chamber 240', the air flow in the compression chamber 240' It enters back into the enthalpy increasing pipeline 210' to form a backflow phenomenon. Since the pressure in the compression chamber 240' changes periodically, the supplemental gas and the backflow will alternately occur, resulting in a periodic pulsating flow effect.
  • the present application aims to improve at least one of the technical problems existing in the prior art or related technologies.
  • a first aspect of the present application proposes a fixed scroll assembly.
  • a second aspect of the present application proposes a scroll compressor.
  • a third aspect of the present application proposes a refrigeration device.
  • an embodiment of the first aspect of the present application provides a fixed scroll assembly, comprising: a disk body, the disk body is provided with a compression channel; an enthalpy increasing channel is provided on the disk body, and the enthalpy increasing channel is used for communication
  • the enthalpy increase pipeline of the scroll compressor the injection enthalpy channel is arranged on the bottom wall of the disc body, the injection enthalpy channel is connected with the compression channel and the enthalpy increase channel, and the injection enthalpy channel includes a blocking part, and the blocking part is used to block the compression channel. The gas flows back to the enthalpy increasing channel.
  • the fixed scroll assembly proposed in this embodiment includes a disk body, an enthalpy increasing channel and an injection enthalpy channel.
  • the disk body includes a bottom wall and a scroll gear arranged on the bottom wall, the bottom wall and the scroll gear enclose a compression channel, and the compression channel of the fixed scroll assembly and the compression channel of the movable scroll together form a scroll compressor the compression chamber.
  • the enthalpy increasing channel and the injection enthalpy channel are arranged on the disc body, the enthalpy increasing channel is used to communicate with the enthalpy increasing pipeline of the scroll compressor, and the injection enthalpy channel is connected with the compression channel and the enthalpy increasing channel, so that the enthalpy increasing channel can pass the refrigerant gas through
  • the enthalpy increasing pipeline of the scroll compressor is introduced from the refrigeration system into the compression chamber of the scroll compressor to realize the function of increasing the enthalpy of the jet. In this way, the temperature of the refrigerant gas in the compression chamber can be reduced, the exhaust volume can be increased, and the heating capacity of the scroll compressor can be greatly improved.
  • the enthalpy increasing airflow is injected into the compression chamber to achieve the effect of supplementing gas; but when the enthalpy increasing pressure is higher than the internal pressure of the scroll compressor.
  • the enthalpy-increasing pressure is lower than the pressure in the compression chamber, the airflow in the compression chamber flows back into the enthalpy-increasing pipeline, forming a backflow phenomenon.
  • the enthalpy injection channel includes a flow blocking part, and the blocking part is used to prevent the gas in the compression channel from flowing back into the enthalpy increasing channel, which can effectively attenuate the propagation of the gas backflow in the compression channel to the enthalpy increasing pipeline, so that the enthalpy increasing pipe
  • the pressure pulsation intensity in the pipeline is weakened, which achieves the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline, and suppresses the vibration characteristics of the enthalpy increasing pipeline and the valve plate, which solves the strong pulsation of the refrigerant gas in the enthalpy increasing pipeline in the related art.
  • the flow blocking portion of the present application can play the role of blocking the backflow of the gas in the compression channel to the enthalpy increasing channel, and it is not necessarily a complete block. In this way, it is possible to prevent a large amount of gas in the compression channel from flowing back into the enthalpy increasing channel, and at the same time, it will not excessively hinder the refrigerant gas from entering the refrigeration system through the enthalpy increasing pipeline, enthalpy increasing channel and injection enthalpy channel of the scroll compressor. In the compression chamber of the scroll compressor, the function of increasing the enthalpy of the jet is realized.
  • the enthalpy increasing channel, the injection enthalpy channel and the enthalpy increasing pipeline together form the enthalpy increasing path of the scroll compressor.
  • the enthalpy-increasing channel in the body is communicated with, and the enthalpy-increasing channel is communicated with the compression cavity formed by the movable scroll and the fixed scroll assembly through the injection enthalpy channel.
  • the enthalpy-increasing airflow passing through the flasher outlet of the scroll compressor enters into the compression chamber composed of the disc body of the stationary scroll assembly and the movable scroll through the enthalpy-increasing pipeline, the enthalpy-increasing channel and the injection enthalpy channel in turn, and then Realize the function of jet enthalpy increase.
  • the fixed scroll assembly provided according to the above technical solutions of the present application also has the following additional technical features:
  • the side wall surface of the enthalpy channel is designed as a flow choke.
  • the side wall surface of the injection enthalpy channel forms a flow blocking part, that is, the backflow of the gas in the compression channel to the enthalpy increasing channel is blocked by the side wall surface of the injection enthalpy channel.
  • the side wall surface of the enthalpy channel it is only necessary to design the side wall surface of the enthalpy channel to be suitable for blocking the backflow of gas, which reduces the number of parts and saves costs;
  • it can prevent a large amount of gas in the compression channel from flowing back into the enthalpy increasing channel, and at the same time, it will not excessively hinder the refrigerant gas from passing through the enthalpy increasing pipeline, enthalpy increasing channel and injection enthalpy channel of the scroll compressor.
  • the refrigeration system enters into the compression chamber of the scroll compressor, so as to realize the function of increasing the enthalpy of the jet.
  • the sidewall surface of the spray enthalpy channel is formed by a part of the wall surface of the disk body, that is, the spray enthalpy channel is directly opened on the disk body.
  • the enthalpy injection channel penetrates the bottom wall of the disc body at the first position, and the cross-sectional area of the enthalpy injection channel at the first position is larger than the cross-sectional area of the enthalpy injection channel at the second position.
  • the injection enthalpy channel penetrates the bottom wall of the disc body at the first position, that is, the injection enthalpy channel penetrates the wall surface of the disc body on the side facing the compression channel at the first position to communicate with the compression channel.
  • the first position is where the penetrating opening of the injection enthalpy passage penetrates the bottom wall of the disc body, so that other positions of the injection enthalpy passage are farther from the compression passage than the first position.
  • the cross-sectional area of the injection enthalpy passage at the first position is made larger than the cross-sectional area of the injection enthalpy passage at the second position.
  • the gas in the compression chamber will smoothly flow back to the enthalpy increasing channel and the enthalpy increasing pipeline. , the gas will first flow through the first position of the enthalpy channel, and then flow through the second position of the enthalpy channel, because the cross-sectional area of the enthalpy channel at the first position is larger than the cross-sectional area of the enthalpy channel at the second position. If it is large, it will increase the resistance and difficulty of the gas continuing to flow along the enthalpy channel, and reduce the impact strength of the gas.
  • the flow resistance caused by the change of the cross-sectional area of the injection enthalpy channel can effectively attenuate the strength of the gas flow in the compression channel returning to the enthalpy increasing pipe, and through the throttling effect, the transmission of the airflow pulsation in the compression channel to the enthalpy increasing pipe is weakened. It achieves the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline, thus solving the problem of cracks and valve failure at the connection between the enthalpy increasing pipeline and the shell of the scroll compressor caused by the strong pulsation of the refrigerant gas in the enthalpy increasing pipeline in the related art.
  • the problem of chip breakage is the problem of chip breakage.
  • the second position is any position in the extending direction of the injection enthalpy channel which is different from the first position. As long as it is ensured that the gas backflow through the injection enthalpy channel will be hindered by the change of the cross-sectional area caused by the change of the side wall surface of the injection enthalpy channel. Whether the cross-sectional area of the injection enthalpy channel at the first position is larger than that of other positions, or only larger than that of a part of positions, such as the second position, it is within the protection scope of the present application.
  • the cross-sectional area of the injection enthalpy channel at the second position is less than or equal to the cross-sectional area of the injection enthalpy channel at the other positions; the cross-sectional area of the injection enthalpy channel at the second position is the same as the injection enthalpy channel at the first position
  • the ratio of the cross-sectional area at a location ranges from 0.1 to 0.7.
  • the cross-sectional area of the injection enthalpy channel at the second position is smaller than the cross-sectional area of the other positions, or the cross-sectional area of the injection enthalpy channel at the second position is equal to the cross-sectional area of the partial position, but is smaller than that of the other positions.
  • the enthalpy channel has a small cross-sectional area in the first position.
  • the injection enthalpy passage may have a minimum cross-sectional area at the second position, by making the minimum cross-sectional area of the injection enthalpy passage at 10% to 70% of the cross-sectional area of the injection enthalpy passage at the first position.
  • the cross-sectional area of the injection enthalpy channel changes greatly, which can effectively attenuate the strength of the gas flow in the compression channel returning to the enthalpy increasing pipe, and through the throttling effect, the transmission of the airflow pulsation in the compression channel to the enthalpy increasing pipe is weakened, and the The technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline.
  • the cross-sectional area of the injection enthalpy channel at the second position may not be the smallest cross-sectional area, that is, the second position is not the thinnest position of the injection enthalpy channel, so that the cross-sectional area of the injection enthalpy channel at the second position
  • the technical effect described above can also be achieved for 10% to 70% of the cross-sectional area of the injection enthalpy channel at the first position.
  • the side wall surface of the injection enthalpy channel includes at least one bent portion.
  • the side wall surface of the injection enthalpy channel is made to include at least one bent portion, for example, a stepped surface of one or more steps, or a non-standard stepped surface.
  • the side wall surface of the enthalpy channel has one or more bends, which change along the axial fold line, which is beneficial to increase the resistance and difficulty of gas backflow flowing along the enthalpy channel, and reduce the impact strength of the gas.
  • the side wall surface of the spray enthalpy channel may also have a vertically extending straight section and/or an inclined extending section.
  • the side wall surface of the spray welding channel may also have a vertically extending straight section and/or an inclined extending section.
  • the side wall surface of the injection enthalpy channel includes an inclined surface inclined with respect to the horizontal plane.
  • the side wall surfaces of the enthalpy channel are made to include inclined surfaces extending obliquely with respect to the horizontal plane.
  • the enthalpy injection channel as a whole extends in a direction perpendicular to the horizontal plane, that is, along the thickness direction of the bottom wall of the disc body, which can effectively prevent the refrigerant gas from entering the enthalpy injection channel from the compression channel smoothly, and increase the gas backflow.
  • the resistance and difficulty of flow along the enthalpy channel reduces the impact strength of the gas.
  • the side wall surface of the injection enthalpy channel can be made into a conical surface or the like. It can effectively attenuate the strength of the gas flow in the compression channel returning to the enthalpy increasing pipeline, and through the throttling effect, the transmission of the airflow pulsation in the compression channel to the enthalpy increasing tube is weakened, and the technology of reducing the pressure pulsation level in the enthalpy increasing pipeline is achieved. Effect.
  • the horizontal plane in the present application refers to the plane extending in the horizontal direction when the scroll compressor is placed upright, such as the plane perpendicular to the line extending along the thickness direction of the bottom wall of the disc body.
  • the inclined surfaces in this application are the surfaces that extend obliquely when the scroll compressor is placed upright, that is, the line extending along the inclined direction of the inclined surface, and the line extending along the thickness direction of the bottom wall of the disc body with a distance between them.
  • the included angle is greater than 0°, and also has an included angle greater than 0° with the horizontal plane.
  • the side wall surface of the enthalpy channel includes an arc surface.
  • the side wall surfaces of the injection enthalpy channels are made to include arc surfaces, so that the cross-sectional areas of the injection enthalpy channels are not equal everywhere.
  • the flow resistance caused by the change of the cross-sectional area of the injection enthalpy channel is beneficial to attenuate the strength of the gas flow in the compression channel returning to the enthalpy increasing pipeline, and is beneficial to reduce the pressure pulsation level in the enthalpy increasing pipeline.
  • the side wall surface of the injection enthalpy channel includes multiple stepped surfaces, and all the stepped surfaces facing the compression channel include horizontal surfaces and/or inclined surfaces inclined relative to the horizontal surface.
  • the side wall surface of the injection enthalpy channel is made to include at least two step surfaces, and the existence of the step surface realizes that the cross-sectional area of the injection enthalpy channel is not equal everywhere.
  • the flow resistance generated by the change of the cross-sectional area of the enthalpy channel is beneficial to attenuate the strength of the gas flow in the compression channel back to the enthalpy increasing pipe, and through the throttling effect, the transmission of the airflow pulsation in the compression channel to the enthalpy increasing pipe is weakened, and the The technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline.
  • all the stepped surfaces facing the compression channel are made to be horizontal surfaces, or all of them are inclined surfaces, and the inclined surfaces are inclined relative to the horizontal surface, that is, the inclined surfaces are inclined relative to the bottom wall surface of the disc body facing the compression channel, or some of the stepped surfaces are horizontal surfaces, and some of the stepped surfaces are horizontal surfaces.
  • the step surface is an inclined surface.
  • the injection enthalpy channel includes a first channel section extending obliquely with respect to the horizontal plane, and one end of the first section channel close to the centerline of the disc body communicates with the enthalpy increasing channel.
  • the injection enthalpy channel include a first section of channel and extending the first section of channel obliquely with respect to the horizontal plane, one end of the first section of channel close to the centerline of the disc body is connected to the enthalpy-increasing channel.
  • the refrigerant gas in the compression channel needs to enter the first-stage channel through the end of the first-stage channel with a relatively long distance, which is close to the center line of the disk body, and then the refrigerant gas has a radial inward flow trend, and then the enthalpy is increased in the reverse direction. flow in the channel.
  • the included angle between the center line of the first channel and the center line of the enthalpy increasing channel is not greater than 90°. Further, less than 90°.
  • the included angle between the center line of the channel of the first section and the center line of the enthalpy increasing channel ranges from 10° to 50°.
  • the first channel has a sufficient inclination angle , which can fully attenuate the propagation of the gas backflow in the compression channel to the enthalpy increasing pipeline, thereby weakening the pressure pulsation intensity of the enthalpy increasing pipeline.
  • the distance between one end of the injection enthalpy channel away from the compression channel and the compression channel is greater than or equal to the distance between the enthalpy increasing channel and the compression channel.
  • the end of the injection enthalpy channel is further away from the compression channel than the lower edge of the enthalpy increasing channel is away from the compression channel. Since the enthalpy increasing channel is communicated with the spraying enthalpy channel, the enthalpy increasing channel can be communicated with the top of the spray welding channel, and can also be communicated with the middle position of the spraying enthalpy channel.
  • the distance between any two points on the edge of the opening of the enthalpy channel passing through the bottom wall of the disc body is less than or equal to the thickness of the spiral teeth of the disc body.
  • the distance between any two points on the edge of the opening of the opening of the enthalpy channel through the bottom wall of the disc body is less than or equal to the thickness of the spiral tooth of the disc body, that is, the transverse direction of the enthalpy channel at the first position.
  • the distance between any two points on the edge of the cross section is less than or equal to the thickness of the spiral tooth of the disc body.
  • the ratio of the distance between any two points on the edge of the opening of the enthalpy channel through the bottom wall of the disc body and the thickness of the spiral teeth of the disc body ranges from 1/2 to 10/11.
  • the distance between any two points on the edge of the cross section of the spray enthalpy channel at the first position is between 1/2 and 10/11 of the thickness of the spiral tooth of the disc body, which can effectively avoid spraying.
  • the opening of the enthalpy channel on the bottom wall of the disc body is too large, which causes the airflow in the different compression spaces in the compression chamber to move through the enthalpy increasing channel, resulting in energy loss and enthalpy increasing failure of air injection.
  • the cross section of one end of the injection enthalpy channel away from the compression channel is circular, oval, rectangular or polygonal; Ellipse or rectangle or polygon.
  • the number of injection enthalpy channels is multiple.
  • the number of injection enthalpy channels is more than one, which is beneficial to increase the effect of aeration injection enthalpy. Moreover, it is not necessary to make the cross-sectional area of each injection enthalpy channel too large, which causes the gas to easily flow back from the compression channel to the enthalpy increasing pipeline.
  • the enthalpy increasing channel communicates with a plurality of injection enthalpy channels at the same height in the thickness direction of the disk body, or the enthalpy increasing channel communicates with multiple injection enthalpy channels at different heights in the thickness direction of the disk body channel connection.
  • the enthalpy increasing channel can be communicated with multiple enthalpy injection channels at a height in the thickness direction of the disc body, which facilitates production and processing. It is also possible to make the enthalpy increasing channel communicate with a plurality of injection enthalpy channels at different heights in the thickness direction of the disc body, so that the area of the hole connecting the enthalpy injection channel and the enthalpy increasing channel has a different reduction ratio to the volume of the injection enthalpy channel. , which can effectively avoid the phenomenon of superposition of resonant frequencies caused by the same multiple holes. It is beneficial to reduce the amplitude of the specific pressure pulsation frequency, especially for the specific frequency corresponding to the rupture of the shell connection and the rupture of the valve plate.
  • Embodiments of the second aspect of the present application provide a scroll compressor, including: the fixed scroll assembly according to any one of the foregoing technical solutions.
  • the scroll compressor proposed in this embodiment has the stationary scroll assembly of any of the above-mentioned technical solutions, and further has the beneficial effects of any of the above-mentioned technical solutions, which will not be repeated here.
  • the scroll compressor further includes: a casing; a movable scroll, which is arranged in the casing and cooperates with the fixed scroll assembly; an enthalpy increasing pipeline, which passes through the casing and is connected to the enthalpy increasing. channel connection.
  • the scroll compressor also includes an enthalpy increasing pipeline, a casing and a movable scroll
  • the enthalpy increasing pipeline is communicated with the casing, and at least a part of the enthalpy increasing pipeline extends to the outside of the casing
  • the fixed scroll assembly and the movable scroll are located inside the casing
  • the fixed scroll assembly and the movable scroll are enclosed to form a compression cavity
  • the compression channel of the fixed scroll assembly is used as a part of the compression cavity.
  • the cavity can communicate with the enthalpy increasing pipeline.
  • Embodiments of the third aspect of the present application provide a refrigeration device, including: a scroll compressor according to any one of the above technical solutions.
  • the refrigeration equipment proposed in this embodiment has the scroll compressor of any of the above-mentioned technical solutions, and further has the beneficial effects of any of the above-mentioned technical solutions, which will not be repeated here.
  • the refrigeration equipment includes a condenser, an evaporator, a flasher and a scroll compressor provided in any of the above technical solutions, which are connected by pipelines.
  • the pipeline connected with the outlet of the flasher is connected to the air inlet of the enthalpy increasing pulsation damping device of the scroll compressor, so as to supply the refrigerant passing through the flasher to the booster of the scroll compressor.
  • the enthalpy pulsation damping device that is, the supply is supplied to the enthalpy channel of the fixed scroll assembly, and then enters the compression cavity of the scroll compressor.
  • the refrigeration equipment includes but is not limited to an air conditioning system.
  • FIG. 1 shows a schematic cross-sectional view of a fixed scroll assembly in the related art
  • FIG. 2 shows a schematic cross-sectional view of a scroll compressor in the related art
  • FIG. 3 shows a schematic cross-sectional view of the fixed scroll assembly of the first specific embodiment of the present application
  • FIG. 4 shows a schematic cross-sectional view of the fixed scroll assembly of the second specific embodiment of the present application
  • FIG. 5 shows a schematic cross-sectional view of the fixed scroll assembly of the third specific embodiment of the present application
  • FIG. 6 shows a schematic cross-sectional view of the fixed scroll assembly of the fourth specific embodiment of the present application.
  • FIG. 7 shows a schematic cross-sectional view of the fixed scroll assembly of the fifth specific embodiment of the present application.
  • FIG. 8 shows a schematic cross-sectional view of the fixed scroll assembly of the sixth specific embodiment of the present application.
  • FIG. 9 shows a schematic cross-sectional view of the fixed scroll assembly of the seventh specific embodiment of the present application.
  • FIG. 10 shows a schematic cross-sectional view of the fixed scroll assembly of the eighth specific embodiment of the present application.
  • FIG. 11 shows a schematic cross-sectional view of the fixed scroll assembly of the ninth specific embodiment of the present application.
  • FIG. 12 shows a schematic cross-sectional view of the fixed scroll assembly of the tenth specific embodiment of the present application
  • FIG. 13 shows a schematic cross-sectional view of a scroll compressor according to an embodiment of the present application.
  • 100' fixed scroll assembly 110' disc body, 112' injection enthalpy passage, 117' enthalpy increasing passage, 200' scroll compressor, 210' enthalpy increasing pipeline, 220' casing, 230' orbiting scroll , 240' compression chamber.
  • 100 fixed scroll assembly 110 disc body, 111 compression channel, 112 enthalpy channel, 113 side wall surface, 113a first section wall, 113b second section wall, 113c third section wall, 113d fourth section wall, 113e fifth section Section wall, 113f sixth section wall, 113g seventh section wall, 113h eighth section wall, 113j ninth section wall, 113k tenth section wall, 113m eleventh section wall, 114 bend, 115 first section channel , 116 second passage, 117 enthalpy channel, 200 scroll compressor, 210 enthalpy pipeline, 220 shell, 230 movable scroll, 240 compression chamber.
  • the fixed scroll assembly 100 , the scroll compressor 200 and the refrigeration apparatus of some embodiments of the present application are described below with reference to FIGS. 3 to 13 .
  • the fixed scroll assembly 100 includes a disk body 110 and an enthalpy increasing channel 117 and injection enthalpy channel 112.
  • the disk body 110 includes a bottom wall surface and a scroll tooth disposed on the bottom wall surface, the bottom wall surface and the scroll teeth enclose a compression channel 111 , the compression channel 111 of the fixed scroll assembly 100 and the compression channel 111 of the orbiting scroll 230 Together, the compression chambers 240 of the scroll compressor 200 are formed.
  • the enthalpy increasing channel 117 and the injection enthalpy channel 112 are provided on the disc body 110.
  • the enthalpy increasing channel 117 is used to communicate with the enthalpy increasing pipeline 210 of the scroll compressor 200, and the injection enthalpy channel 112 communicates with the compression channel 111 and the enthalpy increasing channel 117, so as to
  • the enthalpy increasing channel 117 enables the refrigerant gas to be introduced into the compression chamber 240 of the scroll compressor 200 from the refrigeration system through the enthalpy increasing pipeline 210 of the scroll compressor 200 , so as to realize the function of increasing the enthalpy by air injection. In this way, the temperature of the refrigerant gas in the compression chamber 240 can be lowered, the discharge volume can be increased, and the heating capacity of the scroll compressor 200 can be greatly improved.
  • the enthalpy injection channel 112 includes a flow blocking portion, and the flow blocking portion prevents the gas in the compression channel 111 from flowing back into the enthalpy increasing channel 117 , which can effectively attenuate the propagation of the gas flow back in the compression channel 111 to the enthalpy increasing pipeline 210 .
  • the pressure pulsation intensity in the enthalpy increasing pipeline 210 is weakened, the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline 210 is achieved, and the vibration characteristics of the enthalpy increasing pipeline 210 and the valve plate are suppressed, which solves the problem of the enthalpy increasing pipeline in the related art.
  • the strong pulsation of the refrigerant gas in the pipeline 210 leads to the problem that the connection between the enthalpy increasing pipeline 210 and the casing 220 of the scroll compressor 200 is broken and the valve plate is broken.
  • the mixing loss of the return flow and the jet flow in the enthalpy increasing pipeline 210 can also be reduced, thereby improving the energy efficiency of the scroll compressor 200 to which the fixed scroll assembly 100 is applied.
  • FIG. 1 While the cross-sectional schematic diagram of the scroll compressor 200 ′ in the related art is shown in FIG. 1 , the jet enthalpy increasing pipeline 210 ′ is divided into three parts on the compressor unit, the enthalpy increasing pipeline 210 ′ and the enthalpy increasing channel 117 .
  • the enthalpy increasing pipeline 210' enters the casing 220' through the upper hole of the casing 220', and is directly connected with the enthalpy increasing channel 117', and the enthalpy increasing channel 117' passes through the injection enthalpy channel 112' It is communicated with the compression chamber 240', so that the enthalpy-increasing gas flow passing through the outlet of the flasher enters the fixed scroll assembly 100' and the movable scroll through the enthalpy-increasing pipeline 210', the enthalpy-increasing passage 117' and the enthalpy-increasing passage 112' in turn.
  • FIG. 2 is a schematic cross-sectional view of the fixed scroll assembly 100' in the scroll compressor 200' of the related art, and the injection enthalpy passage 112' extends linearly along the thickness direction of the bottom wall of the fixed scroll assembly 100'.
  • the gas in the compression chamber 240' will smoothly flow back into the enthalpy increasing pipeline 210' through the enthalpy injection channel 112', forming a backflow phenomenon.
  • the flow blocking part of the present application can play a role of blocking the backflow of the gas in the compression channel 111 to the enthalpy increasing channel 117 , and it is not necessarily a complete block. In this way, while preventing a large amount of gas in the compression passage 111 from flowing back into the enthalpy increasing passage 117 , the passage of the refrigerant gas through the enthalpy increasing pipeline 210 , the enthalpy increasing passage 117 and the injection enthalpy passage of the scroll compressor 200 is not excessively hindered.
  • 112 enters the compression chamber 240 of the scroll compressor 200 from the refrigeration system, so as to realize the function of increasing the enthalpy of air injection.
  • the enthalpy increasing channel 117 , the injection enthalpy channel 112 and the enthalpy increasing pipeline 210 together form an enthalpy increasing path of the scroll compressor 200 , and the enthalpy increasing pipeline 210 enters the casing through the hole on the casing 220 of the scroll compressor 200 .
  • the enthalpy-increasing channel 117 communicates with the compression cavity 240 formed by the movable scroll 230 and the fixed scroll assembly 100 through the injection enthalpy channel 112 .
  • the enthalpy-increasing airflow passing through the flasher outlet of the scroll compressor 200 enters the disk body 110 and the movable scroll 230 of the stationary scroll assembly 100 through the enthalpy-increasing pipeline 210 , the enthalpy-increasing passage 117 , and the injection enthalpy passage 112 in sequence.
  • the function of increasing the enthalpy of air injection is realized.
  • both the injection enthalpy channel 112 and the enthalpy increase channel 117 are arranged on the bottom wall of the disc body 110 .
  • the enthalpy increasing channel 117 may be a straight pipe disposed inside the disk body 110 , or the enthalpy increasing channel 117 may be directly formed by a channel in the disk body 110 .
  • the enthalpy increasing pipeline 210 adopts a U-shaped tube.
  • Embodiment 2 is a diagrammatic representation of Embodiment 1:
  • the side wall surface 113 of the injection enthalpy channel 112 is further formed as a flow blocking part, that is, the backflow of the gas in the compression channel 111 to the enthalpy increasing channel 117 is blocked by the side wall surface 113 of the injection enthalpy channel 112 .
  • the side wall surface 113 of the enthalpy channel 112 it is possible to prevent a large amount of gas in the compression channel 111 from flowing back into the enthalpy increasing channel 117, and at the same time, it will not excessively hinder the refrigerant gas from passing through the enthalpy increasing pipeline 210, increasing the enthalpy of the scroll compressor 200.
  • the enthalpy channel 117 and the injection enthalpy channel 112 enter the compression chamber 240 of the scroll compressor 200 from the refrigeration system, so as to realize the function of increasing the enthalpy of the injection.
  • the side wall surface 113 of the spray enthalpy channel 112 is formed by a part of the wall surface of the disk body 110 , that is, the spray enthalpy channel 112 is directly opened on the disk body 110 .
  • the injection enthalpy channel 112 is further made to penetrate the bottom wall surface of the disc body 110 at the first position, that is, the injection enthalpy passage 112 penetrates the side of the disc body 110 facing the compression channel 111 at the first position to communicate with the compression channel 111.
  • the first position is where the through opening of the injection enthalpy passage 112 penetrates the bottom wall of the disc body 110 , so other positions of the injection enthalpy passage 112 are farther from the compression passage 111 than the first position.
  • the cross-sectional area of the injection enthalpy passage 112 at the first position is made larger than the cross-sectional area of the injection enthalpy passage 112 at the second position.
  • the gas in the compression chamber 240' will smoothly flow back to the enthalpy increasing channel 117' and the enthalpy increasing pipeline 210'.
  • the gas will first flow through the first position of the enthalpy channel 112, and then flow through the second position of the enthalpy channel 112. Due to the cross section of the enthalpy channel 112 at the first position The area is larger than the cross-sectional area of the enthalpy channel 112 at the second position, which increases the resistance and difficulty of the gas continuing to flow along the enthalpy channel 112 and reduces the impact strength of the gas.
  • the flow resistance caused by the change of the cross-sectional area of the injection enthalpy channel 112 can effectively attenuate the strength of the gas flow in the compression channel 111 returning to the enthalpy increasing pipeline 210, and through the throttling effect, the gas flow in the compression channel 111 will pulsate toward the enthalpy increasing tube.
  • the transmission of the enthalpy increasing pipeline 210 is weakened, and the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline 210 is achieved, thereby solving the problem of the strong pulsation of the refrigerant gas in the enthalpy increasing pipeline 210' in the related art, which causes the enthalpy increasing pipeline 210' and the scroll compression.
  • the problem is that the connection of the casing 220' of the machine 200' is broken and the valve plate is broken.
  • the second position is any position in the extending direction of the injection enthalpy channel 112 that is different from the first position. As long as it is ensured that the gas backflow through the enthalpy channel 112 will be hindered by the change of the cross-sectional area caused by the change of the side wall surface 113 of the enthalpy channel 112 . Whether the cross-sectional area of the enthalpy channel 112 at the first position is larger than that of other positions, or is only larger than that of a part of positions, such as the second position, it is within the protection scope of the present application.
  • the cross-sectional area of the injection enthalpy channel 112 at the second position is specifically defined to be smaller than the cross-sectional area of the other positions, or the cross-sectional area of the injection enthalpy channel 112 at the second position is equal to the cross-sectional area of some positions , but smaller than the cross-sectional area of the enthalpy channel 112 at the first position.
  • the injection enthalpy channel 112 may have a minimum cross-sectional area at the second position, and at this time, by making the minimum cross-sectional area of the injection enthalpy channel 112 to be 10% of the cross-sectional area of the injection enthalpy channel 112 at the first position Up to 70%, the cross-sectional area of the injection enthalpy channel 112 changes greatly, which can effectively attenuate the strength of the gas flow in the compression channel 111 back to the enthalpy increasing pipeline 210, and make the gas flow in the compression channel 111 pulsate toward the enthalpy increase through the throttling effect.
  • the transmission of the tube is weakened, and the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline 210 is achieved.
  • the cross-sectional area of the injection enthalpy channel 112 at the second position may not be the smallest cross-sectional area, that is, the second position is not the thinnest position of the injection enthalpy channel 112, so that the injection enthalpy channel 112 at the second position
  • the above-mentioned technical effect can also be achieved when the cross-sectional area is 10% to 70% of the cross-sectional area of the enthalpy channel 112 at the first position.
  • the ratio of the cross-sectional area of the injection enthalpy passage 112 at the second position to the cross-sectional area of the injection enthalpy passage 112 at the first position is in the range of 0.2 to 0.4, even if the transverse cross-sectional area of the injection enthalpy passage 112 at the second position
  • the cross-sectional area is 20% to 40% of the cross-sectional area of the enthalpy channel 112 at the first location.
  • the cross-sectional area of the injection enthalpy channel 112 changes greatly, which can effectively attenuate the strength of the gas flow in the compression channel 111 back to the enthalpy increasing pipeline 210, and make the gas flow in the compression channel 111 pulsate toward the enthalpy increasing tube through the throttling effect.
  • the transmission is weakened, and the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline 210 is achieved.
  • the cross-sectional area of the injection enthalpy passage 112 at the second position is not very small, so that sufficient refrigerant gas is introduced into the scroll through the enthalpy increasing pipeline 210 of the scroll compressor 200 from the refrigeration system through the injection enthalpy passage 112 In the compression chamber 240 of the rotary compressor 200, the effect of increasing the enthalpy of the air jet is good.
  • the ratio of the cross-sectional area of the injection enthalpy passage 112 at the second position to the cross-sectional area of the injection enthalpy passage 112 at the first position is 0.15, 0.2, 0.35, 0.5, or 0.65, or the like.
  • the ratio of the end surface area of the end of the injection enthalpy channel 112 away from the compression channel 111 to the cross-sectional area of the injection enthalpy channel 112 at the first position is between 1/6 and 1/2.
  • Embodiment 4 is a diagrammatic representation of Embodiment 4:
  • the side wall surface 113 of the injection enthalpy channel 112 is further made to include at least one bent portion 114 , for example, a step surface of one or more steps is formed, or It is a non-standard step surface.
  • the side wall surface 113 of the enthalpy channel 112 have one or more bending parts 114 , which are changed along the axial fold line, it is beneficial to increase the resistance and difficulty of gas backflow flowing along the enthalpy channel 112 and reduce the impact strength of the gas.
  • the side wall surface 113 of the spray enthalpy channel 112 may also have a vertically extending straight section and/or an inclined extending section.
  • the side wall surface 113 of the spray welding channel may also have a vertically extending straight section and/or an inclined extending section.
  • the side wall surface 113 of the injection enthalpy channel 112 includes an inclined surface extending obliquely with respect to the horizontal surface.
  • the enthalpy injection channel 112' extends in a direction perpendicular to the horizontal plane as a whole, that is, extends along the thickness direction of the bottom wall of the disc body 110', which can effectively prevent the refrigerant gas from smoothly entering the injection enthalpy from the compression channel 111.
  • the channel 112 increases the resistance and difficulty of the gas backflow flowing along the enthalpy channel 112 and reduces the impact strength of the gas.
  • the side wall surface 113 of the injection enthalpy channel 112 can be made Conical surface, etc., can effectively attenuate the strength of the gas flow in the compression channel 111 returning to the enthalpy increasing pipe 210, and through the throttling effect, the transmission of the gas pulsation in the compression channel 111 to the enthalpy increasing pipe is weakened, so as to reduce the enthalpy increasing pipe.
  • the technical effect of the pressure pulsation level in circuit 210 is Especially when the ratio of the cross-sectional area of the injection enthalpy channel 112 at the second position to the cross-sectional area of the injection enthalpy channel 112 at the first position is between 0.1 and 0.7, the side wall surface 113 of the injection enthalpy channel 112 can be made Conical surface, etc., can effectively attenuate the strength of the gas flow in the compression channel 111 returning to the enthalpy increasing pipe 210, and through the throttling effect, the transmission of the
  • the horizontal plane in the present application refers to the plane extending in the horizontal direction when the scroll compressor 200 is placed upright, for example, the plane perpendicular to the line extending along the thickness direction of the bottom wall of the disc body 110 .
  • the inclined surfaces in this application are the surfaces that extend obliquely when the scroll compressor 200 is placed upright, that is, the line extending along the inclined direction of the inclined surface and the line extending along the thickness direction of the bottom wall surface of the disc body 110 There is an included angle greater than 0° between them, and an included angle greater than 0° with the horizontal plane.
  • the side wall surface 113 of the injection enthalpy channel 112 includes an arc surface, so that the cross-sectional area of the injection enthalpy channel 112 is not equal everywhere.
  • the flow resistance generated by the change of the cross-sectional area of the enthalpy channel 112 is beneficial to attenuate the strength of the gas flow in the compression channel 111 returning to the enthalpy increasing pipeline 210 , and is beneficial to reducing the pressure pulsation level in the enthalpy increasing pipeline 210 .
  • the sidewall surface 113 of the injection enthalpy channel 112 includes at least two step surfaces, and the existence of the step surface realizes that the cross-sectional area of the injection enthalpy channel 112 is not equal everywhere.
  • the flow resistance generated by the change of the cross-sectional area of the enthalpy channel 112 is beneficial to attenuate the strength of the gas flow in the compression channel 111 returning to the enthalpy increasing pipeline 210, and through the throttling effect, the pulsation of the gas flow in the compression channel 111 is transmitted to the enthalpy increasing tube. It is weakened, and the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline 210 is achieved.
  • all the stepped surfaces facing the compression channel 111 are horizontal or all inclined surfaces, and the inclined surface is inclined relative to the horizontal surface, that is, the inclined surface is inclined relative to the bottom wall surface of the disc body 110 facing the compression channel 111, or part of the stepped surface is Horizontal plane, part of the stepped plane is inclined plane.
  • the included angle between the two wall surfaces connected to each bending portion 114 is between 45° and 135°.
  • Embodiment 5 is a diagrammatic representation of Embodiment 5:
  • the enthalpy channel 112 is further defined to include a first channel 115 extending obliquely with respect to the horizontal plane, and the first channel 115 is close to the centerline of the disc body 110 .
  • One end communicates with the enthalpy increasing channel 117 .
  • the injection enthalpy channel 112 by making the injection enthalpy channel 112 include the first channel 115 and extending the first channel 115 obliquely with respect to the horizontal plane, the end of the first channel 115 close to the center line of the disc body 110 is connected to the enthalpy increasing channel Channel 117.
  • the refrigerant gas in the compression channel 111 needs to enter the first-stage channel 115 through the end of the first-stage channel 115 that is far away from the center line of the disk body 110, and then the refrigerant gas has a radial inward flow trend, and then reverse Flow into the enthalpy increasing channel 117 .
  • the included angle ⁇ between the centerline of the first channel 115 and the centerline of the enthalpy increasing channel 117 is not greater than 90°. Further, less than 90°.
  • the first-stage channel 115 has sufficient The angle of inclination can sufficiently attenuate the propagation of the gas backflow in the compression channel 111 into the enthalpy increasing pipeline 210 , thereby weakening the pressure pulsation intensity of the enthalpy increasing pipeline 210 .
  • the included angle ⁇ between the center line of the first channel 115 and the center line of the enthalpy increasing channel 117 in the thickness direction of the disk body 110 is 5°, 10°, 20°, 35°, 45° or 65° and so on.
  • Embodiment 6 is a diagrammatic representation of Embodiment 6
  • the end of the injection enthalpy passage 112 further away from the compression passage 111 is further away from the compression passage 111 than the lower edge of the enthalpy increasing passage 117 . Since the enthalpy increasing channel 117 is communicated with the spraying enthalpy channel 112, the enthalpy increasing channel 117 can be communicated with the top of the spray welding channel, and can also be communicated with the middle position of the spraying enthalpy channel 112.
  • Embodiment 7 is a diagrammatic representation of Embodiment 7:
  • the distance R between any two points on the edge of the opening of the opening of the bottom wall of the disk body 110 through the enthalpy channel 112 is further less than or equal to the distance R of the disk body 110 .
  • the thickness of the spiral tooth that is, the distance between any two points on the edge of the cross section of the enthalpy channel 112 at the first position is smaller than or equal to the thickness of the spiral tooth of the disk body 110 .
  • the distance between any two points on the edge of the cross section of the enthalpy channel 112 at the first position is between 1/2 and 10/11 of the thickness of the spiral teeth of the disk body 110 , which is effective. It is avoided that the opening of the injection enthalpy channel 112 on the bottom wall surface of the disc body 110 is too large, causing the airflow in different compression spaces in the compression cavity 240 to move through the enthalpy increasing channel 117, resulting in energy loss and injection enthalpy increasing failure.
  • the greater the number of the injection enthalpy channels 112 the smaller the distance R between any two points on the edge of the opening of the opening of the injection enthalpy channel 112 through the bottom wall surface of the disc body 110 .
  • the ratio of the distance R between any two points on the edge of the opening of the enthalpy channel 112 through the bottom wall of the disc body 110 and the thickness of the spiral teeth of the disc body 110 is 2/3, 3/5, 7/10 or 9/11 and so on.
  • Embodiment 8 is a diagrammatic representation of Embodiment 8
  • the number of injection enthalpy channels 112 is further increased, which is beneficial to increase the effect of gas injection enthalpy. Moreover, it is not necessary to make the cross-sectional area of each injection enthalpy channel 112 too large, which causes the gas to easily flow back from the compression channel 111 to the enthalpy increasing pipeline 210 .
  • the number of injection enthalpy channels 112 is 2 to 4. Of course, the number of injection enthalpy channels 112 may also be one.
  • the enthalpy increasing channel 117 is communicated with the plurality of enthalpy injection channels 112 at a height in the thickness direction of the disc body 110 to facilitate production and processing.
  • the enthalpy increasing channels 117 are arranged at different heights in the thickness direction of the disk body 110 to be connected with the multiple injection enthalpy channels 112 is connected, so that the area of the hole connecting the injection enthalpy channel 112 and the enthalpy increase channel 117 is different from the reduction ratio of the volume of the injection enthalpy channel 112, which can effectively avoid the phenomenon of overlapping resonance frequencies caused by the same holes. It is beneficial to reduce the amplitude of the specific pressure pulsation frequency, especially for the specific frequency corresponding to the rupture of the connection of the casing 220 and the rupture of the valve plate.
  • the fixed scroll assembly 100 of some embodiments of the present application will be described in detail below.
  • the side wall surface 113 of the enthalpy channel 112 is stepped, and three sections are formed, namely the first section wall surface 113a, the second section wall surface 113b and the third section wall surface 113c .
  • the cross-sectional area corresponding to the third wall surface 113c (the cross-sectional area of the injection enthalpy channel 112 at the second position, such as the minimum cross-sectional area) is significantly smaller than the cross-sectional area corresponding to the first wall surface 113a (the injection enthalpy channel 112 at the second position)
  • the cross-sectional area at the first position the ratio of the two is 10% to 70%, for example, the area ratio of the two is 20% to 40%, so as to realize the throttling effect caused by the change of the cross-sectional area, so that the compression
  • the transmission of pressure pulsations inside the cavity 240 to the enthalpy increasing tube is reduced.
  • the steps formed by the first wall surface 113a, the second wall surface 113b and the third wall surface 113c create flow resistance to the backflow of the airflow in the compression chamber 240 to the enthalpy increasing channel 117, which can effectively prevent the backflow and further reduce the
  • the pulsation effect produced by the alternate action of jet flow and return flow achieves the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipe, and solves the problem of the pulsation of the refrigerant in the enthalpy increasing pipe 210' in the related art, which causes the enthalpy increasing pipe 210' and the scroll compressor.
  • the 200' shell 220' joint is broken and the valve plate is broken.
  • the weakening of the reflow intensity reduces the mixing loss caused by the reflow, which is beneficial to the improvement of energy efficiency.
  • the side wall surface 113 of the enthalpy channel 112 is also stepped, and also forms three sections, which are the fourth section wall surface 113d, the fifth section wall surface 113e and the third section wall surface 113d, respectively.
  • the technical effect of the six-section wall surface 113f is similar to the technical solution shown in FIG. 3 .
  • the vertical extension of the fifth-stage wall surface 113e is changed to an inclined extension compared to the second-stage wall surface 113b.
  • the flow resistance to the backflow is slightly weakened, the throttling effect caused by the area change still exists.
  • the resistance of the jet of the passage 117 injected into the compression chamber 240 is reduced, which is beneficial to the improvement of energy efficiency.
  • the side wall surface 113 of the injection enthalpy channel 112 is still a stepped surface, so that the distance between the end of the injection enthalpy channel 112 away from the compression channel 111 and the compression channel 111 is greater than the enthalpy increase
  • the distance between the channel 117 and the compression channel 111 also means that the top of the injection enthalpy channel 112 is higher than the upper edge of the enthalpy increase channel 117 .
  • the side wall surface 113 of the spray enthalpy channel 112 forms a larger cavity, which can produce a more obvious blocking effect on the backflow ejected vertically upward, further weaken the backflow intensity, and reduce the pulsation caused by the alternate action of the jet flow and the backflow. Effect.
  • one end of the injection enthalpy channel 112 away from the compression channel 111 is located at the position from the center line of the enthalpy increasing channel 117 to the diameter of the enthalpy increasing channel 117 above.
  • the cross section of one end of the injection enthalpy channel 112 away from the compression channel 111 is circular, oval, rectangular or polygonal, and/or the edge of the opening of the injection enthalpy channel 112 passing through the bottom wall of the disc body 110 is circular or Ellipse or rectangle or polygon, for example, all circles.
  • the side wall surface 113 of the injection enthalpy channel 112 is a three-stage stepped surface, which is divided into 5 stages, which are the seventh-stage wall surface 113g, the eighth-stage wall surface 113h, the ninth-stage wall surface 113h, and the Section wall 113j, tenth section wall 113k and eleventh section wall 113m, the three-stage steps will form stronger flow resistance, which will have a stronger blocking effect on the backflow, and further reduce the pulsation effect caused by the alternating action of jet flow and backflow. .
  • the side wall surface 113 of the injection enthalpy channel 112 is truncated or conical, the side wall surface 113 extends obliquely, and the end surface of the injection enthalpy channel 112 away from the compression channel 111 corresponds to
  • the cross-sectional area is the smallest, which is significantly smaller than the cross-sectional area of the enthalpy channel 112 at the first position, so that the throttling effect caused by the area change is realized, and the transmission of the pressure pulsation inside the compression chamber 240 to the enthalpy increasing pipeline 210 is weakened.
  • the truncated or conical sidewall surface 113 gradually expands the area for the jet flow and gradually reduces the area for the backflow, which is not only beneficial to the jet flow but also produces flow resistance to the backflow, which can reduce the alternation of the jet flow and the backflow.
  • the pulsation effect generated by the action achieves the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline 210 and suppresses the vibration characteristics of the enthalpy increasing pipeline 210 and the valve plate.
  • the refrigerant in the enthalpy-increasing pipeline 210' is pulsated, which causes the connection between the enthalpy-increasing pipeline 210' and the casing 220' of the scroll compressor 200' to break and the valve plate to break.
  • the weakening of the reflow intensity reduces the mixing loss caused by the reflow, which is beneficial to the improvement of energy efficiency.
  • the number of injection enthalpy channels 112 is multiple, and one end of the multiple injection enthalpy channels 112 away from the compression channel 111 is at different heights in the thickness direction of the disc body 110 .
  • the enthalpy increasing channel 117 is communicated with the plurality of injection enthalpy channels 112 at different heights in the thickness direction of the disc body 110 , so that the area of the hole where the injection enthalpy channel 112 communicates with the enthalpy increasing channel 117 is equal to the volume of the injection enthalpy channel 112
  • the reduction ratio is different, which can effectively avoid the phenomenon of superposition of resonance frequencies caused by the same holes. It is beneficial to reduce the amplitude of the specific pressure pulsation frequency, especially for the specific frequency corresponding to the rupture of the connection of the casing 220 and the rupture of the valve plate.
  • the enthalpy channel 112 is provided as an obliquely extending hole, such as the first-stage channel 115 , and the bottom-to-top direction of the first-stage channel 115 is radially inward,
  • the included angle ⁇ between the center line of the first channel 115 and the center line of the enthalpy increasing channel 117 is not greater than 90°, for example, between 10° and 50°.
  • the radially inward first passage 115 causes the backflow to generate a radially inward velocity, and the propagation of the backflow of the airflow in the compression chamber 240 to the enthalpy increasing pipeline 210 can be effectively attenuated by generating a radially inward velocity of the backflow airflow. Therefore, the pressure pulsation intensity of the enthalpy increasing pipeline 210 is weakened, the technical effect of reducing the pressure pulsation level in the enthalpy increasing pipeline 210 is achieved, and the vibration characteristics of the enthalpy increasing pipeline 210 and the valve plate are suppressed.
  • the obliquely extending first passage 115 also causes the jet to generate radial velocity, so that the jet obliquely jets into the compression chamber 240 and collides with the movable scroll 230 , which is not conducive to the stability of the movable scroll 230 .
  • a combination of a first-stage channel 115 at the top and a second-stage channel 116 at the bottom is used, that is, the sidewall surface 113 of the enthalpy channel 112 is divided into oblique line segments and straight line segments , wherein the straight line segment extends along the thickness direction of the disc body 110 .
  • the jet flow is ejected perpendicular to the bottom wall of the disc body 110 and the backflow generates a radially inward velocity, which not only prevents the jet flow from colliding with the movable scroll 230 laterally, but also effectively attenuates the backflow direction of the airflow in the compression chamber 240 . Propagation of the enthalpy increasing line 210 .
  • the number of injection enthalpy channels 112 may be 3 or 4 or 1 or even more, for example, the number of injection enthalpy channels 112 2 to 4.
  • the cross-sectional area of the enthalpy channel 112 is too large, the airflows in different compression spaces are connected through the enthalpy channel 112 , resulting in energy loss and the failure of the enthalpy increase.
  • the distance R between any two points on the edge is not greater than the thickness of the spiral tooth, for example, the distance between any two points on the edge of the opening of the opening through which the enthalpy channel 112 penetrates the bottom wall of the disc body 110, and the distance between the spiral tooth of the disc body 110.
  • the thickness ratio ranges from 1/2 to 10/11, and the greater the number of injection enthalpy passages 112, the distance R between any two points on the edge of the opening of the injection enthalpy passage 112 through the bottom wall surface of the disc body 110 considers the corresponding decrease.
  • Embodiment 9 is a diagrammatic representation of Embodiment 9:
  • an embodiment of the second aspect of the present application provides a scroll compressor 200 , comprising: the fixed scroll assembly 100 according to any one of the foregoing embodiments.
  • the scroll compressor 200 proposed in this embodiment has the fixed scroll assembly 100 of any of the above-mentioned embodiments, it further has the beneficial effects of any of the above-mentioned embodiments, which will not be repeated here.
  • the scroll compressor 200 further includes an enthalpy increasing pipeline 210, a casing 220 and a movable scroll 230, the enthalpy increasing pipeline 210 is communicated with the casing 220, and at least a part of the enthalpy increasing pipeline 210 extends to the casing Outside the 220, the fixed scroll assembly 100 and the orbiting scroll 230 are located inside the casing 220, and the fixed scroll assembly 100 and the orbiting scroll 230 are enclosed to form a compression chamber 240, and the fixed scroll assembly 100
  • the compression channel 111 is a part of the compression chamber 240 , and the compression chamber 240 can communicate with the enthalpy increasing pipeline 210 .
  • the scroll compressor 200 includes a casing 220, a fixed scroll assembly 100 disposed in the casing 220, a movable scroll 230 capable of rotating relative to the fixed scroll, the fixed scroll assembly 100 and the orbiting scroll
  • the rotary disk 230 forms a compression cavity 240
  • the fixed scroll assembly 100 is provided with an enthalpy-increasing internal straight pipe (a kind of enthalpy-increasing channel 117 ) and an enthalpy-increasing nozzle (enthalpy-increasing channel) leading to the compression cavity 240 .
  • the enthalpy increasing nozzle of the fixed scroll assembly 100 communicates with the internal straight pipe of the enthalpy increasing fixed scroll and the compression cavity 240, and the internal straight pipe of the enthalpy increasing fixed scroll is connected with the enthalpy increasing nozzle and the compression chamber 240.
  • the enthalpy outer U-shaped pipe (a kind of enthalpy increasing pipeline 210 ) communicates with each other.
  • a third aspect of the present application provides a refrigeration apparatus, including: the scroll compressor 200 according to any one of the foregoing embodiments.
  • the refrigeration equipment proposed in this embodiment has the scroll compressor 200 of any of the above-mentioned embodiments, and further has the beneficial effects of any of the above-mentioned embodiments, which will not be repeated here.
  • the refrigeration equipment includes a condenser, an evaporator, a flasher, and the scroll compressor 200 provided in any of the above embodiments, which are connected by pipelines.
  • the pipeline connected with the outlet of the flasher is connected to the air inlet of the enthalpy increasing pulsation damping device of the scroll compressor 200 to supply the refrigerant passing through the flasher to the scroll compressor 200
  • the enthalpy increasing and pulsation damping device that is, it is supplied to the injection enthalpy channel 112 of the fixed scroll assembly 100 , and then enters the compression cavity 240 of the scroll compressor 200 .
  • the refrigeration equipment includes but is not limited to an air conditioning system.

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Abstract

一种静涡旋盘组件（100）、涡旋压缩机（200）和制冷设备。其中，静涡旋盘组件（100）包括：盘本体（110），盘本体（110）设置有压缩通道（111）；增焓通道（117），设置于盘本体（110），增焓通道（117）用于连通涡旋压缩机（200）的增焓管路（210）；喷焓通道（112），设置于盘本体（110）的底壁，喷焓通道（112）连通压缩通道（111）和增焓通道（117），喷焓通道（112）包括阻流部，阻流部用于阻碍压缩通道（111）内的气体回流至增焓通道（117）。通过阻流部来阻碍压缩通道（111）内的气体回流至增焓通道（117）内，可以有效衰减压缩通道（111）内气流回流向增焓管路（210）的传播，使得增焓管路（210）内的压力脉动强度减弱，达到降低增焓管路（210）内压力脉动水平的技术效果，解决了增焓管路（210）中冷媒气体产生强烈脉动而导致增焓管路（210）与涡旋压缩机（200）的壳体连接处断裂和阀片断裂的问题。

Description

静涡旋盘组件、涡旋压缩机和制冷设备
本申请要求于2020年08月31日提交到中国国家知识产权局、申请号为“202010900240.2”、发明名称为“静涡旋盘组件、涡旋压缩机和制冷设备”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及制冷装置技术领域，具体而言，涉及一种静涡旋盘组件、一种涡旋压缩机和一种制冷设备。
背景技术
涡旋压缩机是一种新型容积式流体机械，主要由动、静涡旋盘、曲轴、支架体、防自转的十字滑环等部件组成。与传统的往复式、转子式、螺杆式等压缩机相比，其具有零件数少、容积效率高、压缩过程连续且平稳、振动噪音小等诸多优良特性，目前被广泛应用于多联机空调及热泵系统中。作为制冷系统的核心设备，涡旋压缩机的性能直接决定系统的换热效果。当外界环境温度恒定，传统的涡旋压缩机在工作过程中常会出现冷媒循环量下降、制热能力不足的现象。
为解决这一问题，在传统涡旋压缩机上设置喷气增焓的结构，如图1和图2所示，在静涡旋盘组件100’的盘本体110’上设置补气的喷焓通道112’和增焓通道117’，将冷媒气体通过增焓管路210’从制冷系统引入压缩腔240’的中压腔室部分，通过这种方式，可降低压缩腔240’室中介质温度、增大排气量，大幅提高涡旋压缩机200’的制热能力。
但是，由于设置在静涡旋盘组件100’上的喷焓通道112’、增焓通道117’的位置是固定不动的，而与喷焓通道112’连通的压缩腔240’中的压力是随着曲轴转动周期性变化的，并且随着动涡旋盘230’的运动，压缩腔240’与增焓管路210’周期性地连通、闭合，造成冷媒气体通过增焓管路210’流入涡旋压缩机200’的过程实际上处于一个脉动形式。当增焓压力高于压缩腔240’内压力时，增焓气流喷入压缩腔240’，达到补气效 果；但是当增焓压力低于压缩腔240’内压力时，压缩腔240’内气流回进入到增焓管路210’中，形成回流现象。由于压缩腔240’内的压力是周期性变化，所以补气和回流会交替发生，产生周期性脉动式的流动效果，这种周期性脉动会对增焓管路210’和节流阀等产生周期性激振力，当低阶激振力频率与增焓管路210’和节流阀阀片低阶频率等接近时，造成增焓管路210’和节流阀阀片强烈振动，并伴随产生较大的噪音，甚至导致增焓管路210’和节流阀阀片断裂，严重影响涡旋压缩机200’的可靠性。
发明内容
本申请旨在至少改善现有技术或相关技术中存在的技术问题之一。
为此，本申请的第一方面提出了一种静涡旋盘组件。
本申请的第二方面提出了一种涡旋压缩机。
本申请的第三方面提出了一种制冷设备。
有鉴于此，本申请的第一个方面实施例提供了一种静涡旋盘组件，包括：盘本体，盘本体设置有压缩通道；增焓通道，设置于盘本体，增焓通道用于连通涡旋压缩机的增焓管路；喷焓通道，设置于盘本体的底壁，喷焓通道连通压缩通道和增焓通道，喷焓通道包括阻流部，阻流部用于阻碍压缩通道内的气体回流至增焓通道。
本实施例提出的静涡旋盘组件包括盘本体、增焓通道和喷焓通道。其中，盘本体包括底壁和设置在底壁上的涡齿，底壁和涡齿围合形成压缩通道，静涡旋盘组件的压缩通道与动涡旋盘的压缩通道共同形成涡旋压缩机的压缩腔。增焓通道和喷焓通道设置在盘本体上，增焓通道用于连通涡旋压缩机的增焓管路，喷焓通道连通压缩通道和增焓通道，以使增焓通道能够将冷媒气体通过涡旋压缩机的增焓管路从制冷系统引入涡旋压缩机的压缩腔中，实现喷气增焓的功能。通过这种方式，可降低压缩腔中的冷媒气体温度，增大排气量，大幅提高涡旋压缩机的制热能力。具体地，由于设置在盘本体上的增焓通道和喷焓通道的位置是固定不动的，随着动涡旋盘的运动，压缩腔与增焓管路周期性地连通、闭合，造成冷媒气体通过增焓管路流入涡旋压缩机的过程实际上处于一个脉动形式，当增焓压力高于涡 旋压缩机的内压力时，增焓气流喷入压缩腔，达到补气效果；但是当增焓压力低于压缩腔内压力时，压缩腔内气流回流进入到增焓管路中，形成回流现象。而本申请使喷焓通道包括阻流部，通过阻流部来阻碍压缩通道内的气体回流至增焓通道内，可以有效衰减压缩通道内气流回流向增焓管路的传播，使得增焓管路内的压力脉动强度减弱，达到降低增焓管路内压力脉动水平的技术效果，并抑制增焓管路和阀片的振动特性，解决了相关技术中增焓管路中冷媒气体产生强烈脉动而导致增焓管路与涡旋压缩机的壳体连接处断裂和阀片断裂的问题。另外，还可以减弱增焓管路中的回流与喷流等的掺混损失，从而提高应用该静涡旋盘组件的涡旋压缩机的能效。
需要说明的是，本申请的阻流部能够起到阻碍压缩通道内的气体回流至增焓通道的作用即可，不一定是完全阻隔。由此，可以在避免压缩通道内的大量气体回流到增焓通道内的同时，不会过度阻碍冷媒气体通过涡旋压缩机的增焓管路、增焓通道、喷焓通道从制冷系统进入到涡旋压缩机的压缩腔中，从而实现喷气增焓的功能。
另外，增焓通道、喷焓通道和增焓管路共同形成涡旋压缩机的增焓路径，增焓管路通过涡旋压缩机的壳体上的孔位进入壳体中，并与位于盘本体内部的增焓通道连通，增焓通道又通过喷焓通道与动涡旋盘和静涡旋盘组件形成的压缩腔连通。使得通过涡旋压缩机的闪蒸器出口的增焓气流依次通过增焓管路、增焓通道、喷焓通道进入到静涡旋盘组件的盘本体和动涡旋盘组成的压缩腔中，进而实现喷气增焓的功能。
另外，根据本申请上述技术方案提供的静涡旋盘组件，还具有如下附加技术特征：
在一种可能的设计中，喷焓通道的侧壁面构造成阻流部。
在该设计中，使喷焓通道的侧壁面形成阻流部，也即通过喷焓通道的侧壁面来阻碍压缩通道内的气体回流到增焓通道内。一方面无需额外的阻流部件，只需将喷焓通道的侧壁面设计成适用于阻碍气体回流即可，减少零部件，节约成本；另一方面与相关技术中在喷焓通道的内部设置阻流塞等方案相比，可以在避免压缩通道内的大量气体回流到增焓通道内的同时，不会过度阻碍冷媒气体通过涡旋压缩机的增焓管路、增焓通道、喷焓通道 从制冷系统进入到涡旋压缩机的压缩腔中，从而实现喷气增焓的功能。
在一些实施例中，喷焓通道的侧壁面由盘本体的一部分壁面构造而成，也即直接在盘本体上开设出喷焓通道。
在一种可能的设计中，喷焓通道在第一位置贯穿盘本体的底壁面，喷焓通道在第一位置的横截面面积大于喷焓通道在第二位置的横截面面积。
在该设计中，使喷焓通道在第一位置贯穿盘本体的底壁面，也即喷焓通道在第一位置穿透盘本体的朝向压缩通道的一侧的壁面来与压缩通道连通。该第一位置为喷焓通道贯穿盘本体的底壁面的贯穿口所在位置，从而喷焓通道的其他位置相较于第一位置会远离压缩通道。使喷焓通道在第一位置的横截面面积比喷焓通道在第二位置的横截面面积大。与相关技术中喷焓通道各处的横截面面积相同，压缩腔内的气体会顺畅回流至增焓通道和增焓管路内相比，在压缩通道内的气体回流流经喷焓通道的过程中，气体会先流经喷焓通道的第一位置，而后流经喷焓通道的第二位置，由于喷焓通道在第一位置的横截面面积比喷焓通道在第二位置的横截面面积大，会增加气体继续沿喷焓通道流动的阻力与难度，减小气体的冲击强度。也即喷焓通道的横截面面积变化产生的流动阻力可以有效衰减压缩通道内气体流回流到增焓管路的强度，并通过节流效应使得压缩通道内气流脉动向增焓管的传递减弱，达到了降低增焓管路内压力脉动水平的技术效果，从而解决了相关技术中增焓管路中冷媒气体产生强烈脉动而导致增焓管路与涡旋压缩机的壳体连接处断裂和阀片断裂的问题。
其中，需要说明的是，第二位置为区别于第一位置的喷焓通道延伸方向上的任意位置。只要保证气体回流流经喷焓通道的过程中，会受到喷焓通道的侧壁面变化所带来的横截面面积变化所带来的阻碍即可。无论是喷焓通道在第一位置的横截面面积比其余位置的横截面面积均大，还是仅比一部分位置，例如第二位置的横截面面积大，均在本申请的保护范围内。
在一种可能的设计中，喷焓通道在第二位置的横截面面积小于或等于喷焓通道在其余位置的横截面面积；喷焓通道在第二位置的横截面面积与喷焓通道在第一位置的横截面面积的比值范围为0.1至0.7。
在该设计中，具体限定喷焓通道在第二位置的横截面面积比其余位置 的横截面面积均小，或者喷焓通道在第二位置的横截面面积等于部分位置的横截面面积，但是比喷焓通道在第一位置的横截面面积小。此时，喷焓通道在第二位置可以具有最小的横截面面积，此时，通过使喷焓通道的最小横截面面积为喷焓通道在第一位置处的横截面面积的10％至70％，喷焓通道的横截面面积变化较大，可以有效衰减压缩通道内气体流回流到增焓管路的强度，并通过节流效应使得压缩通道内气流脉动向增焓管的传递减弱，达到了降低增焓管路内压力脉动水平的技术效果。
当然，喷焓通道在第二位置处的横截面面积也可以不是最小的横截面面积，也即第二位置不是喷焓通道最细的位置，使喷焓通道在第二位置处的横截面面积为喷焓通道在第一位置处的横截面面积的10％至70％，也可以达到上述技术效果。
在一种可能的设计中，喷焓通道的侧壁面包括至少一弯折部。
在该设计中，使喷焓通道的侧壁面包括至少一个弯折部，例如形成一级或多级台阶面，或者为非标准台阶面。通过使喷焓通道的侧壁面具有一个或多个弯折部，沿轴向折线变化，有利于增加气体回流沿喷焓通道流动的阻力与难度，减小气体的冲击强度。有利于改变喷焓通道的横截面面积，从而可以有效衰减压缩通道内气体流回流到增焓管路的强度，并通过节流效应使得压缩通道内气流脉动向增焓管的传递减弱，达到了降低增焓管路内压力脉动水平的技术效果。
当然，在喷焓通道的侧壁面包括至少一弯折部的情况下，喷焊通道的侧壁面还可以具有竖向延伸的直线段和/或倾斜延伸段。例如，相邻两个竖向延伸的直线段之间具有至少两个弯折部，或者一个竖向延伸的直线段与相邻的一个倾斜延伸段之间具有一个弯折部，或者相邻的两个倾斜延伸段之间具有一个弯折部。
在一种可能的设计中，喷焓通道的侧壁面包括相对于水平面倾斜的倾斜面。
在该设计中，使喷焓通道的侧壁面包括相对于水平面倾斜延伸的倾斜面。与相关技术中，喷焓通道整体沿垂直于水平面的方向延伸，也即沿盘本体的底壁的厚度方向延伸相比，可有效避免冷媒气体顺畅地从压缩通道 进入喷焓通道，增加气体回流沿喷焓通道流动的阻力与难度，减小气体的冲击强度。尤其在结合喷焓通道在第二位置的横截面面积与喷焓通道在第一位置的横截面面积的比值在0.1至0.7之间的情况下，可以使喷焓通道的侧壁面呈圆锥面等等，可以有效衰减压缩通道内气体流回流到增焓管路的强度，并通过节流效应使得压缩通道内气流脉动向增焓管的传递减弱，达到降低增焓管路内压力脉动水平的技术效果。
其中，需要说明的是，本申请中的水平面，均为涡旋压缩机正立放置时水平方向延伸的面，例如与沿盘本体的底壁的厚度方向延伸的线向垂直的面。本申请中的倾斜面，均为涡旋压缩机正立放置时倾斜延伸的面，也即沿倾斜面的倾斜方向延伸的线，与沿盘本体的底壁的厚度方向延伸的线之间具有大于0°的夹角，并与水平面之间也具有大于0°的夹角。
在一种可能的设计中，喷焓通道的侧壁面包括弧面。
在该设计中，使喷焓通道的侧壁面包括弧面，使得喷焓通道的横截面面积不会处处相等。喷焓通道的横截面面积变化产生的流动阻力有利于衰减压缩通道内气体流回流到增焓管路的强度，有利于降低增焓管路内压力脉动水平。
在一种可能的设计中，喷焓通道的侧壁面包括多级台阶面，全部面向压缩通道的台阶面包括水平面和/或相对于水平面倾斜的倾斜面。
在该设计中，具体使喷焓通道的侧壁面包括至少两级台阶面，台阶面的存在，实现了喷焓通道的横截面面积不处处相等。喷焓通道的横截面面积变化产生的流动阻力有利于衰减压缩通道内气体流回流到增焓管路的强度，并通过节流效应使得压缩通道内气流脉动向增焓管的传递减弱，达到了降低增焓管路内压力脉动水平的技术效果。
具体地，使面向压缩通道的台阶面全部为水平面，或者全部为倾斜面，倾斜面相对于水平面倾斜，也即倾斜面相对于盘本体的朝向压缩通道的底壁面倾斜，或者部分台阶面为水平面，部分台阶面为倾斜面。
在一种可能的设计中，喷焓通道包括相对于水平面倾斜延伸的第一段通道，第一段通道靠近盘本体的中心线的一端与增焓通道连通。
在该设计中，通过使喷焓通道包括第一段通道，并使第一段通道相对 于水平面倾斜延伸，使第一段通道靠近盘本体的中心线的一端连通增焓通道。使得压缩通道内的冷媒气体需经较远距离的第一段通道靠近盘本体的中心线的一端进入第一段通道，而后使冷媒气体具有径向向内流动的趋势，再反向向增焓通道内流动。可以有效衰减压缩通道内气体回流向增焓管路内的传播，从而使得增焓管路的压力脉动强度减弱，由此减小涡旋压缩机运行过程中增焓管路内的压力脉动水平并抑制增焓管路和节流阀的阀片的振动特性，解决相关技术中增焓管路中冷媒产生强烈脉动而导致增焓管路与压缩机的壳体连接处断裂和阀片断裂的问题。还可减弱增焓通道中的回流与喷流等的掺混损失，提高能效。
在一种可能的设计中，在盘本体的底壁的厚度方向上，第一段通道的中心线与增焓通道的中心线的夹角不大于90°。进一步地，小于90°。
进一步地，在盘本体的底壁的厚度方向上，第一段通道的中心线与增焓通道的中心线的夹角范围为10°至50°。
在该设计中，通过使第一段通道的中心线与增焓通道的中心线在盘本体的厚度方向上的夹角在10°至50°之间，使得第一段通道具有足够的倾斜角度，能够充分衰减压缩通道内气体回流向增焓管路内的传播，从而使得增焓管路的压力脉动强度减弱。
在一种可能的设计中，喷焓通道远离压缩通道的一端与压缩通道的间距，大于等于增焓通道与压缩通道的间距。
在该设计中，使喷焓通道远离压缩通道的一端相较于增焓通道的下边缘远离压缩通道。由于增焓通道与喷焓通道连通，使得增焓通道可以与喷焊通道的顶部连通，也可以与喷焓通道的中部位置连通。
在一种可能的设计中，喷焓通道贯穿盘本体的底壁面的开口的边缘上任意两点之间的距离，小于等于盘本体的涡齿的厚度。
在该设计中，使喷焓通道贯穿盘本体的底壁面的开口的边缘上任意两点之间的距离均小于或等于盘本体的涡齿的厚度，也即喷焓通道在第一位置的横截面的边缘上任意两点之间的距离均小于或等于盘本体的涡齿的厚度。可有效避免喷焓通道在盘本体的底壁面上的开口过大，导致压缩腔内不同的压缩空间内气流通过增焓通道窜动，而造成能量损失和喷气增焓失 效。
在一种可能的设计中，喷焓通道贯穿盘本体的底壁面的开口的边缘上任意两点之间的距离，与盘本体的涡齿的厚度的比值范围为1/2至10/11。
在该设计中，具体使喷焓通道在第一位置的横截面的边缘上任意两点之间的距离为盘本体的涡齿的厚度的1/2至10/11之间，可有效避免喷焓通道在盘本体的底壁面上的开口过大，导致压缩腔内不同的压缩空间内气流通过增焓通道窜动，而造成能量损失和喷气增焓失效。
在一种可能的设计中，喷焓通道远离压缩通道的一端的横截面呈圆形或椭圆形或矩形或多边形；和/或喷焓通道贯穿盘本体的底壁面的开口的边缘呈圆形或椭圆形或矩形或多边形。
在一种可能的设计中，喷焓通道的数量为多个。
在该设计中，使喷焓通道的数量为多个，有利于增加增气喷焓效果。而且无需使每个喷焓通道横截面面积过大，导致气体易从压缩通道内回流至增焓管路。
在一种可能的设计中，增焓通道在盘本体的厚度方向上的同一高度处与多个喷焓通道连通，或增焓通道在盘本体的厚度方向上的不同高度处与多个喷焓通道连通。
在该设计中，在喷焓通道的数量为多个的情况下，可以使增焓通道在盘本体的厚度方向上的一个高度处与多个喷焓通道连通，方便生产加工。也可以使增焓通道在盘本体的厚度方向上的不同高度处与多个喷焓通道连通，使得喷焓通道与增焓通道相连通的孔的面积，与喷焓通道的容积的缩减比不同，可有效避免多个孔相同造成共振频率叠加的现象。有利于降低特定压力脉动频率的幅值，尤其是对于壳体连接处断裂和阀片断裂所对应的特定频率。
本申请的第二方面实施例提供了一种涡旋压缩机，包括：如上述技术方案中任一项的静涡旋盘组件。
本实施例提出的涡旋压缩机，由于具有上述任一技术方案的静涡旋盘组件，进而具有上述任一技术方案的有益效果，在此不一一赘述。
在一种可能的设计中，涡旋压缩机还包括：壳体；动涡旋盘，设置于 壳体内，并与静涡旋盘组件相配合；增焓管路，穿过壳体与增焓通道连通。
在该设计中，进一步说明了涡旋压缩机还包括增焓管路、壳体和动涡旋盘，增焓管路与壳体相连通，增焓管路的至少一部分延伸到壳体的外部，静涡旋盘组件和动涡旋盘位于壳体的内部，并且，静涡旋盘组件与动涡旋盘围合形成压缩腔，静涡旋盘组件的压缩通道作为压缩腔的一部分，压缩腔能够与增焓管路相连通。
本申请的第三方面实施例提供了一种制冷设备，包括：如上述技术方案中任一项的涡旋压缩机。
本实施例提出的制冷设备，由于具有上述任一技术方案的涡旋压缩机，进而具有上述任一技术方案的有益效果，在此不一一赘述。
进一步地，制冷设备包括通过管路连接的冷凝器、蒸发器、闪蒸器以及上述任一技术方案中所提供的涡旋压缩机。
进一步地，在该制冷设备中，与闪蒸器的出口连接的管路连接至涡旋压缩机的增焓脉动衰减装置的进气口，以将经过闪蒸器的冷媒供应到涡旋压缩机的增焓脉动衰减装置中，也即供应到静涡旋盘组件的喷焓通道中，然后进入涡旋压缩机的压缩腔内。当然，也可以设置将从冷凝器或蒸发器出来的冷媒供应到涡旋压缩机内。
进一步地，制冷设备包括但不限于空调系统。
本申请的附加方面和优点将在下面的描述部分中变得明显，或通过本申请的实践了解到。
附图说明
图1示出了相关技术中静涡旋盘组件的剖视示意图；
图2示出了相关技术中涡旋压缩机的剖视示意图；
图3示出了本申请的第一个具体实施例的静涡旋盘组件的剖视示意图；
图4示出了本申请的第二个具体实施例的静涡旋盘组件的剖视示意图；
图5示出了本申请的第三个具体实施例的静涡旋盘组件的剖视示意 图；
图6示出了本申请的第四个具体实施例的静涡旋盘组件的剖视示意图；
图7示出了本申请的第五个具体实施例的静涡旋盘组件的剖视示意图；
图8示出了本申请的第六个具体实施例的静涡旋盘组件的剖视示意图；
图9示出了本申请的第七个具体实施例的静涡旋盘组件的剖视示意图；
图10示出了本申请的第八个具体实施例的静涡旋盘组件的剖视示意图；
图11示出了本申请的第九个具体实施例的静涡旋盘组件的剖视示意图；
图12示出了本申请的第十个具体实施例的静涡旋盘组件的剖视示意图；
图13示出了本申请的一个实施例的涡旋压缩机的剖视示意图。
其中，图1和图2中的附图标记与部件名称之间的对应关系为：
100’静涡旋盘组件，110’盘本体，112’喷焓通道，117’增焓通道，200’涡旋压缩机，210’增焓管路，220’壳体，230’动涡旋盘，240’压缩腔。
图3至图13中的附图标记与部件名称之间的对应关系为：
100静涡旋盘组件，110盘本体，111压缩通道，112喷焓通道，113侧壁面，113a第一段壁面，113b第二段壁面，113c第三段壁面，113d第四段壁面，113e第五段壁面，113f第六段壁面，113g第七段壁面，113h第八段壁面，113j第九段壁面，113k第十段壁面，113m第十一段壁面，114弯折部，115第一段通道，116第二段通道，117增焓通道，200涡旋压缩机，210增焓管路，220壳体，230动涡旋盘，240压缩腔。
具体实施方式
为了可以更清楚地理解本申请的上述目的、特征和优点，下面结合附图和具体实施方式对本申请进行进一步的详细描述。需要说明的是，在不冲突的情况下，本申请的实施例及实施例中的特征可以相互组合。
在下面的描述中阐述了很多具体细节以便于充分理解本申请，但是，本申请还可以采用其他不同于在此描述的其他方式来实施，因此，本申请的保护范围并不受下面公开的具体实施例的限制。
下面参照图3至图13描述本申请的一些实施例的静涡旋盘组件100、涡旋压缩机200和制冷设备。
实施例一：
如图3、图7、图8和图9所示，本申请的第一个方面实施例提供了一种静涡旋盘组件100，静涡旋盘组件100包括盘本体110、增焓通道117和喷焓通道112。其中，盘本体110包括底壁面和设置在底壁面上的涡齿，底壁面和涡齿围合形成压缩通道111，静涡旋盘组件100的压缩通道111与动涡旋盘230的压缩通道111共同形成涡旋压缩机200的压缩腔240。增焓通道117和喷焓通道112设置在盘本体110上，增焓通道117用于连通涡旋压缩机200的增焓管路210，喷焓通道112连通压缩通道111和增焓通道117，以使增焓通道117能够将冷媒气体通过涡旋压缩机200的增焓管路210从制冷系统引入涡旋压缩机200的压缩腔240中，实现喷气增焓的功能。通过这种方式，可降低压缩腔240中的冷媒气体温度，增大排气量，大幅提高涡旋压缩机200的制热能力。具体地，由于设置在盘本体110上的增焓通道117和喷焓通道112的位置是固定不动的，随着动涡旋盘230的运动，压缩腔240与增焓管路210周期性地连通、闭合，造成冷媒气体通过增焓管路210流入涡旋压缩机200的过程实际上处于一个脉动形式，当增焓压力高于涡旋压缩机200的内压力时，增焓气流喷入压缩腔240，达到补气效果；但是当增焓压力低于压缩腔240内压力时，压缩腔240内气流回流进入到增焓管路210中，形成回流现象。而本申请使喷焓通道112包括阻流部，通过阻流部来阻碍压缩通道111内的气体回流至增焓通道117内，可以有效衰减压缩通道111内气流回流向增焓管路210的 传播，使得增焓管路210内的压力脉动强度减弱，达到降低增焓管路210内压力脉动水平的技术效果，并抑制增焓管路210和阀片的振动特性，解决了相关技术中增焓管路210中冷媒气体产生强烈脉动而导致增焓管路210与涡旋压缩机200的壳体220连接处断裂和阀片断裂的问题。另外，还可以减弱增焓管路210中的回流与喷流等的掺混损失，从而提高应用该静涡旋盘组件100的涡旋压缩机200的能效。
而相关技术中的涡旋压缩机200’的剖视示意图如图1所示，喷气增焓管路210’在压缩机单体上分为三部分，增焓管路210’、增焓通道117’和喷焓通道112’，增焓管路210’通过壳体220’上孔位进入壳体220’中，并与增焓通道117’直接连通，增焓通道117’通过喷焓通道112’与压缩腔240’连通，使得通过闪蒸器出口的增焓气流依次通过增焓管路210’、增焓通道117’和喷焓通道112’进入到静涡旋盘组件100’和动涡旋盘230’组成的压缩腔240’中(如图1中箭头所示)，实现了喷气增焓的功能。图2为相关技术的涡旋压缩机200’中静涡旋盘组件100’的剖视示意图，喷焓通道112’沿静涡旋盘组件100’的底壁面的厚度方向上直线延伸。当增焓压力低于压缩腔240’内压力时，压缩腔240’内气体会很顺利地经喷焓通道112’回流进入到增焓管路210’中，形成回流现象。
需要说明的是，本申请的阻流部能够起到阻碍压缩通道111内的气体回流至增焓通道117的作用即可，不一定是完全阻隔。由此，可以在避免压缩通道111内的大量气体回流到增焓通道117内的同时，不会过度阻碍冷媒气体通过涡旋压缩机200的增焓管路210、增焓通道117、喷焓通道112从制冷系统进入到涡旋压缩机200的压缩腔240中，从而实现喷气增焓的功能。
另外，增焓通道117、喷焓通道112和增焓管路210共同形成涡旋压缩机200的增焓路径，增焓管路210通过涡旋压缩机200的壳体220上的孔位进入壳体220中，并与位于盘本体110内部的增焓通道117连通，增焓通道117又通过喷焓通道112与动涡旋盘230和静涡旋盘组件100形成的压缩腔240连通。使得通过涡旋压缩机200的闪蒸器出口的增焓气流依次通过增焓管路210、增焓通道117、喷焓通道112进入到静涡旋盘组件 100的盘本体110和动涡旋盘230组成的压缩腔240中，进而实现喷气增焓的功能。
在具体应用中，喷焓通道112和增焓通道117均设置在盘本体110的底壁面上。增焓通道117可以为设置在盘本体110内部的直管，也可以由盘本体110内的通道直接形成增焓通道117。增焓管路210采用U形管。
实施例二：
在上述实施例一的基础上，进一步使喷焓通道112的侧壁面113形成阻流部，也即通过喷焓通道112的侧壁面113来阻碍压缩通道111内的气体回流到增焓通道117内。一方面无需额外的阻流部件，只需将喷焓通道112的侧壁面113设计成适用于阻碍气体回流即可，减少零部件，节约成本；另一方面与相关技术中在喷焓通道112的内部设置阻流塞等方案相比，可以在避免压缩通道111内的大量气体回流到增焓通道117内的同时，不会过度阻碍冷媒气体通过涡旋压缩机200的增焓管路210、增焓通道117、喷焓通道112从制冷系统进入到涡旋压缩机200的压缩腔240中，从而实现喷气增焓的功能。
在具体应用中，喷焓通道112的侧壁面113由盘本体110的一部分壁面构造而成，也即直接在盘本体110上开设出喷焓通道112。
实施例三：
在上述实施例二的基础上，进一步使喷焓通道112在第一位置贯穿盘本体110的底壁面，也即喷焓通道112在第一位置穿透盘本体110的朝向压缩通道111的一侧的壁面来与压缩通道111连通。该第一位置为喷焓通道112贯穿盘本体110的底壁面的贯穿口所在位置，从而喷焓通道112的其他位置相较于第一位置会远离压缩通道111。使喷焓通道112在第一位置的横截面面积比喷焓通道112在第二位置的横截面面积大。与相关技术中喷焓通道112’各处的横截面面积相同，压缩腔240’内的气体会顺畅回流至增焓通道117’和增焓管路210’内相比，在压缩通道111内的气体回流流经喷焓通道112的过程中，气体会先流经喷焓通道112的第一位置，而后流经喷焓通道112的第二位置，由于喷焓通道112在第一位置的横截面面积比喷焓通道112在第二位置的横截面面积大，会增加气体继续沿喷 焓通道112流动的阻力与难度，减小气体的冲击强度。也即喷焓通道112的横截面面积变化产生的流动阻力可以有效衰减压缩通道111内气体流回流到增焓管路210的强度，并通过节流效应使得压缩通道111内气流脉动向增焓管的传递减弱，达到了降低增焓管路210内压力脉动水平的技术效果，从而解决了相关技术中增焓管路210’中冷媒气体产生强烈脉动而导致增焓管路210’与涡旋压缩机200’的壳体220’连接处断裂和阀片断裂的问题。
其中，需要说明的是，第二位置为区别于第一位置的喷焓通道112延伸方向上的任意位置。只要保证气体回流流经喷焓通道112的过程中，会受到喷焓通道112的侧壁面113变化所带来的横截面面积变化所带来的阻碍即可。无论是喷焓通道112在第一位置的横截面面积比其余位置的横截面面积均大，还是仅比一部分位置，例如第二位置的横截面面积大，均在本申请的保护范围内。
在一些实施例中，具体限定喷焓通道112在第二位置的横截面面积比其余位置的横截面面积均小，或者喷焓通道112在第二位置的横截面面积等于部分位置的横截面面积，但是比喷焓通道112在第一位置的横截面面积小。此时，喷焓通道112在第二位置可以具有最小的横截面面积，此时，通过使喷焓通道112的最小横截面面积为喷焓通道112在第一位置处的横截面面积的10％至70％，喷焓通道112的横截面面积变化较大，可以有效衰减压缩通道111内气体流回流到增焓管路210的强度，并通过节流效应使得压缩通道111内气流脉动向增焓管的传递减弱，达到了降低增焓管路210内压力脉动水平的技术效果。
当然，喷焓通道112在第二位置处的横截面面积也可以不是最小的横截面面积，也即第二位置不是喷焓通道112最细的位置，使喷焓通道112在第二位置处的横截面面积为喷焓通道112在第一位置处的横截面面积的10％至70％，也可以达到上述技术效果。
进一步地，使喷焓通道112在第二位置的横截面面积与喷焓通道112在第一位置的横截面面积的比值范围为0.2至0.4，也即使喷焓通道112在第二位置处的横截面面积为喷焓通道112在第一位置处的横截面面积的 20％至40％。一方面喷焓通道112的横截面面积变化较大，可以有效衰减压缩通道111内气体流回流到增焓管路210的强度，并通过节流效应使得压缩通道111内气流脉动向增焓管的传递减弱，达到了降低增焓管路210内压力脉动水平的技术效果。另一方面使得喷焓通道112在第二位置的横截面面积不会很小，从而有利于充足的冷媒气体通过涡旋压缩机200的增焓管路210从制冷系统经喷焓通道112引入涡旋压缩机200的压缩腔240中，喷气增焓效果好。
在具体应用中，喷焓通道112在第二位置的横截面面积与喷焓通道112在第一位置的横截面面积的比值为0.15、0.2、0.35、0.5或0.65等等。
在一些实施例中，喷焓通道112远离压缩通道111的一端的端面面积与喷焓通道112在第一位置的横截面面积的比值在1/6至1/2之间。
实施例四：
在上述实施例三的基础上，如图3、图4和图5所示，进一步使喷焓通道112的侧壁面113包括至少一个弯折部114，例如形成一级或多级台阶面，或者为非标准台阶面。通过使喷焓通道112的侧壁面113具有一个或多个弯折部114，沿轴向折线变化，有利于增加气体回流沿喷焓通道112流动的阻力与难度，减小气体的冲击强度。有利于改变喷焓通道112的横截面面积，从而可以有效衰减压缩通道111内气体流回流到增焓管路210的强度，并通过节流效应使得压缩通道111内气流脉动向增焓管的传递减弱，达到了降低增焓管路210内压力脉动水平的技术效果。
当然，在喷焓通道112的侧壁面113包括至少一弯折部114的情况下，喷焊通道的侧壁面113还可以具有竖向延伸的直线段和/或倾斜延伸段。例如，相邻两个竖向延伸的直线段之间具有至少两个弯折部114，或者一个竖向延伸的直线段与相邻的一个倾斜延伸段之间具有一个弯折部114，或者相邻的两个倾斜延伸段之间具有一个弯折部114。
进一步地，使喷焓通道112的侧壁面113包括相对于水平面倾斜延伸的倾斜面。与相关技术中，喷焓通道112’整体沿垂直于水平面的方向延伸，也即沿盘本体110’的底壁面的厚度方向延伸相比，可有效避免冷媒气体顺畅地从压缩通道111进入喷焓通道112，增加气体回流沿喷焓通道 112流动的阻力与难度，减小气体的冲击强度。尤其在结合喷焓通道112在第二位置的横截面面积与喷焓通道112在第一位置的横截面面积的比值在0.1至0.7之间的情况下，可以使喷焓通道112的侧壁面113呈圆锥面等等，可以有效衰减压缩通道111内气体流回流到增焓管路210的强度，并通过节流效应使得压缩通道111内气流脉动向增焓管的传递减弱，达到降低增焓管路210内压力脉动水平的技术效果。
其中，需要说明的是，本申请中的水平面，均为涡旋压缩机200正立放置时水平方向延伸的面，例如与沿盘本体110的底壁面的厚度方向延伸的线向垂直的面。本申请中的倾斜面，均为涡旋压缩机200正立放置时倾斜延伸的面，也即沿倾斜面的倾斜方向延伸的线，与沿盘本体110的底壁面的厚度方向延伸的线之间具有大于0°的夹角，并与水平面之间也具有大于0°的夹角。
进一步地，使喷焓通道112的侧壁面113包括弧面，使得喷焓通道112的横截面面积不会处处相等。喷焓通道112的横截面面积变化产生的流动阻力有利于衰减压缩通道111内气体流回流到增焓管路210的强度，有利于降低增焓管路210内压力脉动水平。
在一些实施例中，具体使喷焓通道112的侧壁面113包括至少两级台阶面，台阶面的存在，实现了喷焓通道112的横截面面积不处处相等。喷焓通道112的横截面面积变化产生的流动阻力有利于衰减压缩通道111内气体流回流到增焓管路210的强度，并通过节流效应使得压缩通道111内气流脉动向增焓管的传递减弱，达到了降低增焓管路210内压力脉动水平的技术效果。
具体地，使面向压缩通道111的台阶面全部为水平面，或者全部为倾斜面，倾斜面相对于水平面倾斜，也即倾斜面相对于盘本体110的朝向压缩通道111的底壁面倾斜，或者部分台阶面为水平面，部分台阶面为倾斜面。
在一些实施例中，使喷焓通道112的侧壁面113中，与每个弯折部114相连的两段壁面之间的夹角在45°至135°之间。
实施例五：
在上述实施例二的基础上，如图9和图10所示，进一步限定喷焓通道112包括相对于水平面倾斜延伸的第一段通道115，第一段通道115靠近盘本体110的中心线的一端与增焓通道117连通。
在该实施例中，通过使喷焓通道112包括第一段通道115，并使第一段通道115相对于水平面倾斜延伸，使第一段通道115靠近盘本体110的中心线的一端连通增焓通道117。使得压缩通道111内的冷媒气体需经较远距离的第一段通道115靠近盘本体110的中心线的一端进入第一段通道115，而后使冷媒气体具有径向向内流动的趋势，再反向向增焓通道117内流动。可以有效衰减压缩通道111内气体回流向增焓管路210内的传播，从而使得增焓管路210的压力脉动强度减弱，由此减小涡旋压缩机200运行过程中增焓管路210内的压力脉动水平并抑制增焓管路210和节流阀的阀片的振动特性，解决相关技术中增焓管路210’中冷媒产生强烈脉动而导致增焓管路210’与涡旋压缩机200’的壳体220’连接处断裂和阀片断裂的问题。还可减弱增焓通道117中的回流与喷流等的掺混损失，提高能效。
在一些实施例中，如图9所示，在盘本体110的底壁面的厚度方向上，第一段通道115的中心线与增焓通道117的中心线的夹角θ不大于90°。进一步地，小于90°。
进一步地，通过使第一段通道115的中心线与增焓通道117的中心线在盘本体110的厚度方向上的夹角θ在10°至50°之间，使得第一段通道115具有足够的倾斜角度，能够充分衰减压缩通道111内气体回流向增焓管路210内的传播，从而使得增焓管路210的压力脉动强度减弱。
在具体应用中，使第一段通道115的中心线与增焓通道117的中心线在盘本体110的厚度方向上的夹角θ为5°、10°、20°、35°、45°或65°等等。
实施例六：
在上述任一实施例的基础上，如图8所示，进一步使喷焓通道112远离压缩通道111的一端相较于增焓通道117的下边缘远离压缩通道111。由于增焓通道117与喷焓通道112连通，使得增焓通道117可以与喷焊通 道的顶部连通，也可以与喷焓通道112的中部位置连通。
实施例七：
在上述任一实施例的基础上，如图3所示，进一步使喷焓通道112贯穿盘本体110的底壁面的开口的边缘上任意两点之间的距离R均小于或等于盘本体110的涡齿的厚度，也即喷焓通道112在第一位置的横截面的边缘上任意两点之间的距离均小于或等于盘本体110的涡齿的厚度。可有效避免喷焓通道112在盘本体110的底壁面上的开口过大，导致压缩腔240内不同的压缩空间内气流通过增焓通道117窜动，而造成能量损失和喷气增焓失效。
在一些实施例中，使喷焓通道112在第一位置的横截面的边缘上任意两点之间的距离为盘本体110的涡齿的厚度的1/2至10/11之间，可有效避免喷焓通道112在盘本体110的底壁面上的开口过大，导致压缩腔240内不同的压缩空间内气流通过增焓通道117窜动，而造成能量损失和喷气增焓失效。
具体地，喷焓通道112的数量越多，喷焓通道112贯穿盘本体110的底壁面的开口的边缘上任意两点之间的距离R越小。
在具体应用中，喷焓通道112贯穿盘本体110的底壁面的开口的边缘上任意两点之间的距离R，与盘本体110的涡齿的厚度的比值为2/3、3/5、7/10或9/11等等。
实施例八：
在上述任一实施例的基础上，如图11和图12所示，进一步使喷焓通道112的数量为多个，有利于增加增气喷焓效果。而且无需使每个喷焓通道112横截面面积过大，导致气体易从压缩通道111内回流至增焓管路210。
在具体应用中，喷焓通道112的数量为2个至4个。当然，喷焓通道112的数量也可以为一个。
在一些实施例中，在喷焓通道112的数量为多个的情况下，使增焓通道117在盘本体110的厚度方向上的一个高度处与多个喷焓通道112连通，方便生产加工。
在另一些实施例中，如图8所示，在喷焓通道112的数量为多个的情 况下，使增焓通道117在盘本体110的厚度方向上的不同高度处与多个喷焓通道112连通，使得喷焓通道112与增焓通道117相连通的孔的面积，与喷焓通道112的容积的缩减比不同，可有效避免多个孔相同造成共振频率叠加的现象。有利于降低特定压力脉动频率的幅值，尤其是对于壳体220连接处断裂和阀片断裂所对应的特定频率。
以下详细介绍本申请的一些实施例的静涡旋盘组件100。
在第一个具体实施例中，如图3所示，喷焓通道112的侧壁面113为台阶状，形成了三段，分别为第一段壁面113a、第二段壁面113b和第三段壁面113c。第三段壁面113c所对应的横截面面积(喷焓通道112在第二位置处的横截面面积，例如最小横截面面积)明显小于第一段壁面113a所对应的横截面面积(喷焓通道112在第一位置处的横截面面积)，两者之比为10％至70％，例如两者的面积比为20％至40％，从而实现了横截面面积变化所造成的节流效应，使得压缩腔240内部的压力脉动向增焓管的传递减弱。同时，第一段壁面113a、第二段壁面113b和第三段壁面113c所形成的台阶对于压缩腔240内的气流向增焓通道117的回流产生了流动阻力，可以有效阻止回流的产生，进一步降低喷流和回流交替作用产生的脉动效果，达到降低增焓管内压力脉动水平的技术效果，解决相关技术中增焓管路210’中冷媒产生脉动而导致增焓管路210’与涡旋压缩机200’的壳体220’连接处断裂和阀片断裂的问题。而且，回流强度的减弱使得回流产生的掺混损失减小，对有利于能效提升。
在第二个具体的实施例中，如图4所示，喷焓通道112的侧壁面113也为台阶状，也形成了三段，分别为第四段壁面113d、第五段壁面113e和第六段壁面113f，其技术效果类似于图3所示的技术方案。其中，第五段壁面113e相较于第二段壁面113b的竖向延伸改为倾斜延伸，虽然对回流的流动阻力稍有减弱，但是面积改变造成的节流效应依然存在，而且对于从增焓通道117喷入压缩腔240的喷流的阻力减小，有利于能效提升。
在第三个具体的实施例中，如图5所示，喷焓通道112的侧壁面113仍然为台阶面，使喷焓通道112远离压缩通道111的一端与压缩通道111的间距，大于增焓通道117与压缩通道111的间距，也即使喷焓通道112 的顶端高于增焓通道117的上边缘。则喷焓通道112的侧壁面113围合形成了较大的空腔，可以对垂直向上喷出的回流产生更加明显的阻滞效果，进一步减弱回流强度，降低喷流和回流交替作用产生的脉动效果。
进一步地，使喷焓通道112远离压缩通道111的一端，位于增焓通道117的中心线所在位置到上方的一倍增焓通道117的直径位置处。
进一步地，使喷焓通道112远离压缩通道111的一端的横截面呈圆形或椭圆形或矩形或多边形，和/或喷焓通道112贯穿盘本体110的底壁面的开口的边缘呈圆形或椭圆形或矩形或多边形，例如，均为圆形。
在第四个具体的实施例中，如图6所示，喷焓通道112的侧壁面113为三段台阶面，分成5段，分别为第七段壁面113g、第八段壁面113h、第九段壁面113j、第十段壁面113k和第十一段壁面113m，三段台阶会形成更加强的流动阻力，进而对回流产生更强阻滞效果，进一步降低喷流和回流交替作用产生的脉动效果。
在第五个具体的实施例中，如图7所示，喷焓通道112的侧壁面113为棱台形或圆锥形，侧壁面113倾斜延伸，喷焓通道112远离压缩通道111的端面所对应的横截面面积最小，明显小于喷焓通道112在第一位置的横截面面积，从而实现了面积变化所造成的节流效应，使得压缩腔240内部的压力脉动向增焓管路210的传递减弱。同时，棱台形或圆锥形的侧壁面113对于喷流是面积逐渐扩张而对于回流是面积逐渐减小，既能有利于喷流喷出也能对回流产生流动阻力，可以降低喷流和回流交替作用产生的脉动效果，达到降低增焓管路210内压力脉动水平的技术效果并抑制增焓管路210和阀片的振动特性。解决相关技术中增焓管路210’中冷媒产生脉动而导致增焓管路210’与涡旋压缩机200’的壳体220’连接处断裂和阀片断裂的问题。同时，回流强度的减弱使得回流产生的掺混损失减小，有利于能效提升。
在第六个具体的实施例中，如图8所示，喷焓通道112的数量为多个，多个喷焓通道112远离压缩通道111的一端在盘本体110的厚度方向上的不同高度处。使增焓通道117在盘本体110的厚度方向上的不同高度处与多个喷焓通道112连通，使得喷焓通道112与增焓通道117相连通的孔的 面积，与喷焓通道112的容积的缩减比不同，可有效避免多个孔相同造成共振频率叠加的现象。有利于降低特定压力脉动频率的幅值，尤其是对于壳体220连接处断裂和阀片断裂所对应的特定频率。
在第七个具体的实施例中，如图9所示，喷焓通道112设置为倾斜延伸的孔，例如第一段通道115，且第一段通道115的底部到顶部方向径向向内，第一段通道115的中心线与增焓通道117的中心线的夹角θ不大于90°，例如10°至50°之间。径向向内的第一段通道115使得回流产生了径向向内的速度，通过让回流气流产生径向向里的速度可以有效衰减压缩腔240内气流回流向增焓管路210的传播，从而使得增焓管路210的压力脉动强度减弱，达到降低增焓管路210内压力脉动水平的技术效果并抑制增焓管路210和阀片的振动特性。由此解决相关技术中增焓管路210’中冷媒产生脉动而导致增焓管路210’与涡旋压缩机200’的壳体220’连接处断裂和阀片断裂的问题。由于倾斜延伸的第一段通道115也会造成喷流产生径向速度，使得喷流斜喷到压缩腔240而与动涡旋盘230发生撞击，不利于动涡旋盘230稳定。
在第八个具体的实施例中，如图10所示，使用顶部为第一段通道115和底部为第二段通道116的组合，即喷焓通道112的侧壁面113分成斜线段和直线段，其中，直线段沿盘本体110的厚度方向延伸。从而使得喷流垂直盘本体110的底壁面喷出而回流产生了径向向内的速度，既能避免喷流与动涡旋盘230发生侧向撞击，又能效衰减压缩腔240内气流回流向增焓管路210的传播。
在第九个和第十个具体的实施例中，如图11和图12所示，喷焓通道112的数量可为3个或者4个或者1个甚至更多，例如喷焓通道112的数量为2个至4个。为了避免由于喷焓通道112的横截面面积过大，不同压缩空间内气流通过喷焓通道112串通，造成能量损失和喷气增焓失效，限制喷焓通道112贯穿盘本体110的底壁面的开口的边缘上任意两点之间的距离R不大于涡齿的厚度，例如喷焓通道112贯穿盘本体110的底壁面的开口的边缘上任意两点之间的距离，与盘本体110的涡齿的厚度的比值范围为1/2至10/11，而且喷焓通道112的数量越多，喷焓通道112贯穿盘本 体110的底壁面的开口的边缘上任意两点之间的距离R考虑相应的减小。
实施例九：
如图13所示，本申请的第二方面实施例提供了一种涡旋压缩机200，包括：如上述实施例中任一项的静涡旋盘组件100。
本实施例提出的涡旋压缩机200，由于具有上述任一实施例的静涡旋盘组件100，进而具有上述任一实施例的有益效果，在此不一一赘述。
进一步地，涡旋压缩机200还包括增焓管路210、壳体220和动涡旋盘230，增焓管路210与壳体220相连通，增焓管路210的至少一部分延伸到壳体220的外部，静涡旋盘组件100和动涡旋盘230位于壳体220的内部，并且，静涡旋盘组件100与动涡旋盘230围合形成压缩腔240，静涡旋盘组件100的压缩通道111作为压缩腔240的一部分，压缩腔240能够与增焓管路210相连通。
具体地，涡旋压缩机200包括壳体220、设置于壳体220内的静涡旋盘组件100和能够相对静涡旋盘转动的动涡旋盘230，静涡旋盘组件100和动涡旋盘230形成压缩腔240，静涡旋盘组件100上设置有通向压缩腔240的增焓静涡旋盘内部直管(增焓通道117的一种)和增焓喷管(喷焓通道112的一种)，静涡旋盘组件100的增焓喷管与增焓静涡旋盘内部直管和压缩腔240连通，以及增焓静涡旋盘内部直管与增焓喷管和增焓外部U形管(增焓管路210的一种)连通。
举例地，在ARI(American Air-Conditioning and Refrigeration Institute，美国空调与制冷学会)标准工况下，采用如图5所示的静涡旋盘组件100，分别在30Hz、60Hz、90Hz和120Hz所对应的四个转速下进行试验得到压力脉动幅值。压力脉动幅值平均值由156.0Kpa降低到99.3Kpa，降低幅度约为36.3％，获得相应的实验数据，如下表1。
表1
Figure PCTCN2020134876-appb-000001
通过以上测试，可知，通过本申请所限定的技术方案，测试得到的压力脉动幅值相比于相关技术的技术方案降低了36.3％，达到了降低位于涡旋压缩机200的外部的增焓管路210内压力脉动水平的技术效果并抑制增焓管路210和阀片的振动特性，由此解决了相关技术中增焓管路210’中冷媒产生强烈脉动而导致增焓管路210’与涡旋压缩机200’的壳体220’连接处断裂和阀片断裂的问题。
实施例十：
本申请的第三方面实施例提供了一种制冷设备，包括：如上述实施例中任一项的涡旋压缩机200。本实施例提出的制冷设备，由于具有上述任一实施例的涡旋压缩机200，进而具有上述任一实施例的有益效果，在此不一一赘述。
具体地，制冷设备包括通过管路连接的冷凝器、蒸发器、闪蒸器以及上述任一实施例中所提供的涡旋压缩机200。
进一步地，在该制冷设备中，与闪蒸器的出口连接的管路连接至涡旋压缩机200的增焓脉动衰减装置的进气口，以将经过闪蒸器的冷媒供应到涡旋压缩机200的增焓脉动衰减装置中，也即供应到静涡旋盘组件100的喷焓通道112中，然后进入涡旋压缩机200的压缩腔240内。当然，也可以设置将从冷凝器或蒸发器出来的冷媒供应到涡旋压缩机200内。
进一步地，制冷设备包括但不限于空调系统。
在本申请中，术语“第一”、“第二”、“第三”仅用于描述的目的，而不能理解为指示或暗示相对重要性；术语“多个”则指两个或两个以上，除非另有明确的限定。术语“安装”、“相连”、“连接”、“固定”等术语均应做广义理解，例如，“连接”可以是固定连接，也可以是可拆卸连接，或一体地连接；“相连”可以是直接相连，也可以通过中间媒介间接相连。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
本申请的描述中，需要理解的是，术语“上”、“下”、“左”、“右”、“前”、“后”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请和简化描述，而不是指示或暗示所指的装置 或单元必须具有特定的方向、以特定的方位构造和操作，因此，不能理解为对本申请的限制。
在本说明书的描述中，术语“一个实施例”、“一些实施例”、“具体实施例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或实例。而且，描述的具体特征、结构、材料或特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
以上仅为本申请的优选实施例而已，并不用于限制本申请，对于本领域的技术人员来说，本申请可以有各种更改和变化。凡在本申请的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本申请的保护范围之内。

Claims (16)

  1. 一种静涡旋盘组件，其中，包括：
    盘本体，所述盘本体设置有压缩通道；
    增焓通道，设置于所述盘本体，所述增焓通道用于连通涡旋压缩机的增焓管路；
    喷焓通道，设置于所述盘本体的底壁，所述喷焓通道连通所述压缩通道和所述增焓通道，所述喷焓通道包括阻流部，所述阻流部用于阻碍所述压缩通道内的气体回流至所述增焓通道。
  2. 根据权利要求1所述的静涡旋盘组件，其中，
    所述喷焓通道的侧壁面构造成所述阻流部。
  3. 根据权利要求2所述的静涡旋盘组件，其中，
    所述喷焓通道在第一位置贯穿所述盘本体的底壁面，所述喷焓通道在第一位置的横截面面积大于所述喷焓通道在第二位置的横截面面积。
  4. 根据权利要求3所述的静涡旋盘组件，其中，
    所述喷焓通道在第二位置的横截面面积小于或等于所述喷焓通道在其余位置的横截面面积；
    所述喷焓通道在第二位置的横截面面积与所述喷焓通道在第一位置的横截面面积的比值范围为0.1至0.7。
  5. 根据权利要求2至4中任一项所述的静涡旋盘组件，其中，
    所述喷焓通道的侧壁面包括至少一弯折部；和/或
    所述喷焓通道的侧壁面包括相对于水平面倾斜的倾斜面；和/或
    所述喷焓通道的侧壁面包括弧面。
  6. 根据权利要求2至4中任一项所述的静涡旋盘组件，其中，
    所述喷焓通道的侧壁面包括多级台阶面，全部面向所述压缩通道的台阶面包括水平面和/或相对于水平面倾斜的倾斜面。
  7. 根据权利要求2所述的静涡旋盘组件，其中，
    所述喷焓通道包括相对于水平面倾斜延伸的第一段通道，所述第一段通道靠近所述盘本体的中心线的一端与所述增焓通道连通。
  8. 根据权利要求7所述的静涡旋盘组件，其中，
    在所述盘本体的底壁的厚度方向上，所述第一段通道的中心线与所述增焓通道的中心线的夹角小于90°。
  9. 根据权利要求8所述的静涡旋盘组件，其中，
    在所述盘本体的底壁的厚度方向上，所述第一段通道的中心线与所述增焓通道的中心线的夹角范围为10°至50°。
  10. 根据权利要求1至4、7至9中任一项所述的静涡旋盘组件，其中，
    所述喷焓通道远离所述压缩通道的一端与所述压缩通道的间距，大于等于所述增焓通道与所述压缩通道的间距。
  11. 根据权利要求1至4、7至9中任一项所述的静涡旋盘组件，其中，
    所述喷焓通道贯穿所述盘本体的底壁面的开口的边缘上任意两点之间的距离，小于等于所述盘本体的涡齿的厚度。
  12. 根据权利要求11所述的静涡旋盘组件，其中，
    所述喷焓通道贯穿所述盘本体的底壁面的开口的边缘上任意两点之间的距离，与所述盘本体的涡齿的厚度的比值范围为1/2至10/11。
  13. 根据权利要求1至4、7至9中任一项所述的静涡旋盘组件，其中，
    所述喷焓通道的数量为多个；
    所述增焓通道在所述盘本体的厚度方向上的同一高度处与多个所述喷焓通道连通，或
    所述增焓通道在所述盘本体的厚度方向上的不同高度处与多个所述喷焓通道连通。
  14. 一种涡旋压缩机，其中，包括：
    如权利要求1至13中任一项所述的静涡旋盘组件。
  15. 根据权利要求14所述的涡旋压缩机，其中，所述涡旋压缩机还包括：
    壳体；
    动涡旋盘，设置于所述壳体内，并与所述静涡旋盘组件相配合；
    增焓管路，穿过所述壳体与所述增焓通道连通。
  16. 一种制冷设备，其中，包括：
    如权利要求14或15所述的涡旋压缩机。
PCT/CN2020/134876 2020-08-31 2020-12-09 静涡旋盘组件、涡旋压缩机和制冷设备 WO2022041562A1 (zh)

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