WO2019104983A1 - 压缩机及具有其的空调器 - Google Patents

压缩机及具有其的空调器 Download PDF

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Publication number
WO2019104983A1
WO2019104983A1 PCT/CN2018/089962 CN2018089962W WO2019104983A1 WO 2019104983 A1 WO2019104983 A1 WO 2019104983A1 CN 2018089962 W CN2018089962 W CN 2018089962W WO 2019104983 A1 WO2019104983 A1 WO 2019104983A1
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Prior art keywords
passage
cavity
compressor
cylinder
compression portion
Prior art date
Application number
PCT/CN2018/089962
Other languages
English (en)
French (fr)
Inventor
陈圣
吴健
杨欧翔
邹鹏
柯达俊
罗惠芳
刘喜兴
Original Assignee
珠海格力节能环保制冷技术研究中心有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 珠海格力节能环保制冷技术研究中心有限公司 filed Critical 珠海格力节能环保制冷技术研究中心有限公司
Priority to EP18884749.5A priority Critical patent/EP3719324A4/en
Priority to US16/650,633 priority patent/US11614087B2/en
Publication of WO2019104983A1 publication Critical patent/WO2019104983A1/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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps with two cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/0276—Lubrication characterised by the compressor type the pump being of the reciprocating piston type, e.g. oscillating, free-piston compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • F04B39/0292—Lubrication of pistons or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the present invention relates to the field of compressors, and in particular to a compressor and an air conditioner having the same.
  • the air conditioning system has higher and higher requirements for heating capacity and energy efficiency.
  • the two-stage enhanced compressor can heat up in a low temperature environment and can adapt to the wide operating temperature range. Its application in air conditioning heat pump systems is becoming more widespread.
  • the existing two-stage enthalpy compressor (see Figure 1) often has a large amount of oil accumulation in the intermediate chamber, and the oil in the intermediate chamber cannot be discharged in time, which will cause the secondary cylinder to instantaneously inhale excessive oil accumulation, and then appear second.
  • the oil pressure phenomenon in the compression part causes the resistance torque of the second compression part of the compressor to fluctuate greatly, which makes the motor torque output unstable, causes the instantaneous current to increase, and even causes the compressor to stop.
  • the compression resistance of the second compression portion of the compressor is large, the sliding head of the second compression portion is subjected to a large force, thereby causing the sliding piece to disengage from the roller, and the sliding piece impacts the roller or the bottom hole of the groove, affecting Compressor reliability.
  • the prior art compressor includes a first compression portion 10', a second compression portion 20', an intermediate chamber 30', an intermediate passage 40', an air supply passage 50', and a first flange 60'.
  • the oil discharged from the first compression portion 10' adheres to the cavity wall of the intermediate chamber 30' to adhere and condense, and gradually accumulates; the outlet of the intermediate chamber 30' is disposed at the uppermost end (ie, the bottom port of the intermediate passage 40' is located
  • the upper portion of the intermediate chamber 30' is limited in the amount of medium pressure gas discharged from the oil reservoir after being buffered by the intermediate chamber 30'.
  • the second compressing portion 20' When the intermediate chamber 30' is full of oil, the second compressing portion 20' sucks the gas, and the total amount of the gas is reduced to generate a vacuum, thereby directly sucking the oil into the second compressing portion 20', so that an instantaneous large amount occurs.
  • the phenomenon of oil absorption Further, since the refrigerant flowing out of the first compressing portion 10' brings only the oil accumulated in the liquid surface portion of the oil accumulation to the intermediate passage, the speed at which the oil in the intermediate chamber is discharged into the intermediate chamber is low. That is, in the prior art, the oil in the intermediate chamber is discharged from the intermediate chamber to be inefficient.
  • a main object of the present invention is to provide a compressor and an air conditioner having the same.
  • the oil in the intermediate chamber is discharged out of the intermediate chamber with low efficiency.
  • a compressor comprising: a first compression portion; a second compression portion; an intermediate chamber, refrigerant flowing from the first compression portion enters the intermediate chamber;
  • the passage communicates with the inner cavity and the inner cavity of the second compression portion, and the bottom end port of the intermediate passage is located at the bottom of the intermediate cavity to convey the oil in the intermediate cavity by using the supplemental refrigerant and/or the refrigerant flowing out from the first compression portion.
  • the inner cavity of the second compression portion when only the refrigerant flowing out from the first compression portion is used to transport the oil located in the intermediate chamber into the inner cavity of the second compression portion, at least a part of the intermediate passage is located at the compressor The exterior of the housing assembly.
  • the compressor further includes a supplemental air passage for conveying the supplemental refrigerant.
  • the supplemental air passage is in communication with the intermediate chamber and is located below the intermediate chamber.
  • the compressor further includes a housing assembly, the intermediate passage is located inside the housing assembly, and the air supply passage is disposed along a radial direction of the first compression portion, and the intermediate passage is disposed along an axial direction of the first compression portion.
  • the compressor further includes an augmenting component in communication with the supplemental air channel, the supplemental air channel comprising: a first channel segment; the second channel segment, one end of the first channel segment is in communication with the augmenting component, and the first channel segment is further One end is in communication with one end of the second channel segment, and the other end of the second channel segment is in communication with the intermediate cavity, wherein an angle between a centerline of the first channel segment and a centerline of the second channel segment.
  • the compressor further includes a drainage structure disposed in the intermediate passage, one end of the drainage structure extending into the intermediate chamber.
  • the compressor further includes: a first flange disposed under the first compression portion, the lower side of the first flange has a first cavity; and the first cover plate is disposed below the first flange, A side of the cover plate facing the first flange has a second cavity, and the first cavity and the second cavity together form an intermediate cavity, and the air inlet of the air supply passage is opened on the bottom wall of the second cavity.
  • the first cover plate is further provided with a groove, and the air supply passage communicates with the second cavity through the groove.
  • the compressor further includes a drainage tube disposed in the intermediate passage, and an end of the drainage tube facing the second cavity is inclined.
  • the first compression portion includes a first cylinder
  • the second compression portion includes a second cylinder
  • the first cylinder and the second cylinder are stacked
  • the compressor further includes a partition disposed between the first cylinder and the second cylinder and A first flange located below the first cylinder, the intermediate passage being formed on the combination of the first cylinder, the second cylinder, the diaphragm, and the first flange.
  • the second cylinder is provided with a first through hole
  • the partition plate is provided with a second through hole communicating with the first through hole
  • the first cylinder is provided with a third through hole communicating with the second through hole
  • a flange is provided with a fourth through hole communicating with the third through hole, wherein the inner surfaces of the first through hole, the second through hole, the third through hole and the fourth through hole form an intermediate passage.
  • a side of the first flange remote from the first cylinder has a first cavity, and the fourth through hole is connected or isolated from the first cavity.
  • the inlet end of the intermediate passage is located at the bottom of the intermediate chamber.
  • the intermediate passage includes a first flow passage section and a second flow passage section communicating with the first flow passage section, the first flow passage section is located outside the housing assembly, and the second flow passage section is located inside the housing assembly, the first flow passage One end of the segment remote from the second flow path section communicates with the inner cavity of the second compression portion, and one end of the second flow path segment away from the first flow path segment is located at the bottom of the intermediate cavity.
  • the compressor further includes: a first flange disposed under the first compression portion, the lower side of the first flange has a first cavity; and the first cover plate is disposed below the first flange, A side of the cover plate facing the first flange has a second cavity, the first cavity and the second cavity together forming an intermediate cavity, and the inlet end of the intermediate channel is open on the bottom wall of the second cavity.
  • first cover plate is further provided with a groove, and the intermediate passage communicates with the second cavity via the groove.
  • the compressor further includes an air supply passage that communicates with the inner chamber of the intermediate passage and the second compression portion, respectively.
  • the second compression portion includes a second cylinder, and the air supply passage is opened on the second cylinder.
  • an air conditioner including a compressor which is the aforementioned compressor is provided.
  • the refrigerant flowing out from the first compression portion squeezes the oil in the intermediate chamber into the intermediate passage, and the oil accumulates with the supplemental refrigerant. And/or the refrigerant flowing out of the first compression portion enters the inner cavity of the second compression portion and is discharged. Since the oil in the intermediate chamber is squeezed into the intermediate passage by the refrigerant, the refrigerant flowing out from the first compression portion in the prior art only brings part of the oil accumulation on the oil surface in the intermediate chamber into the intermediate passage.
  • the oil input into the intermediate passage is faster, and the oil in the intermediate chamber is discharged out of the intermediate chamber more efficiently; when only the refrigerant flowing out from the first compression portion is used, the oil in the intermediate chamber is delivered to the first portion.
  • the inner portion of the two compression portions is inside, at least a part of the intermediate passage is located outside the casing assembly of the compressor, and when the intermediate passage located outside the casing assembly fails, it is convenient to carry out the intermediate passage located outside the casing assembly. Clean or replace the new intermediate channel.
  • Figure 1 shows a cross-sectional view of a prior art two-stage booster compressor
  • Figure 2 is a cross-sectional view showing the compressor of the first embodiment of the present invention
  • Figure 3 is a cross-sectional view showing the assembled first piston, second cylinder, diaphragm and first flange of the compressor of Figure 2;
  • Figure 4 shows a perspective view of the first cover of Figure 3;
  • Figure 5 shows a cross-sectional view of the first cover of Figure 3
  • Figure 6 shows a front view of the first cover of Figure 3
  • Figure 7 is a perspective view showing the combination of the first cylinder, the second cylinder, the partition plate and the first flange of Figure 3;
  • Figure 8 shows a perspective view of the second cylinder of Figure 3
  • Figure 9 shows a perspective view of the first cylinder of Figure 3.
  • Figure 10 shows a perspective view of the partition of Figure 3
  • Figure 11 shows a perspective view of the first flange of Figure 3;
  • Figure 12 shows a cross-sectional view of the drainage tube of Figure 2;
  • Figure 13 is a cross-sectional view showing the compressor of the second embodiment of the present invention.
  • Figure 14 is a cross-sectional view showing the assembled first piston, second cylinder, diaphragm, first flange and the like of the compressor of Figure 13;
  • Figure 15 is a cross-sectional view showing a draft tube of a compressor of a third embodiment of the present invention.
  • Figure 16 is a cross-sectional view showing the assembly of the first cylinder, the second cylinder, the partition plate, the first flange, and the like of the compressor of the fourth embodiment of the present invention
  • Figure 17 shows a cross-sectional view of the first flange of Figure 16
  • Figure 18 shows a perspective view of the first flange of Figure 16
  • Figure 19 is a cross-sectional view showing a compressor of a fifth embodiment of the present invention.
  • Figure 20 is a cross-sectional view showing the assembly of the first cylinder, the second cylinder, the diaphragm, the first flange, and the like of the compressor of Figure 19;
  • Figure 21 is a flow chart showing the flow of refrigerant and lubricating oil of the compressor of Figure 19;
  • Figure 22 is a flow chart showing the flow of refrigerant and lubricating oil of the compressor of Figure 2.
  • a first embodiment of the present application provides a compressor.
  • the compressor includes a first compression portion 10, a second compression portion 20, an intermediate chamber 30, and an intermediate passage 40; the refrigerant flowing out of the first compression portion 10 enters the intermediate chamber 30; the intermediate passage 40 communicates with the intermediate chamber 30 and the second compression portion 20
  • the inner cavity, the bottom end port of the intermediate passage 40 is located at the bottom of the intermediate chamber 30, to transfer the oil accumulated in the intermediate chamber 30 to the second compression portion by using the supplemental refrigerant and/or the refrigerant flowing out from the first compression portion 10.
  • the pressurized refrigerant flowing from the first compression portion 10 can better squeeze the oil in the intermediate chamber 30 into the intermediate passage 40, thereby The oil accumulates with the refrigerant gas and/or the refrigerant flowing out of the first compression unit 10 into the inner cavity of the second compression unit 20 to be discharged. Since the oil in the intermediate chamber 30 is squeezed into the intermediate passage 40 by the refrigerant, the refrigerant flowing out from the first compressing portion 10 in the prior art only brings a part of the oil accumulated on the surface of the oil in the intermediate chamber into the intermediate passage.
  • the oil input into the intermediate passage 40 is faster, and the oil in the intermediate chamber 30 is discharged from the intermediate chamber 30 more efficiently.
  • the refrigerant flowing out from the first compression portion 10 it is located in the intermediate chamber 30.
  • the accumulated oil is delivered into the inner cavity of the second compression portion 20, at least a portion of the intermediate passage 40 is located outside the casing assembly 90 of the compressor, and is conveniently located when the intermediate passage located outside the casing assembly fails
  • the outer intermediate passage 40 of the housing assembly is cleaned or replaced with a new intermediate passage.
  • the accumulating refrigerant and the refrigerant flowing out from the first compression unit 10 collectively transport the oil in the intermediate chamber 30 to the second.
  • the refrigerant in the intermediate chamber 30 is simultaneously transported into the inner cavity of the second compression portion 20 by the refrigerant-filled refrigerant and the refrigerant flowing out of the first compression portion 10, and the intermediate chamber 30 is only passed through the refrigerant.
  • the oil is delivered into the inner cavity of the second compressing portion 20, and the refrigerant is transported at a relatively high speed, so that the refrigerant carrying the oil is discharged to the intermediate chamber 30 with high efficiency, that is, the oil in the intermediate chamber 30 is discharged.
  • the efficiency of the intermediate chamber 30 is high.
  • the compressor is a two-stage booster compressor.
  • the bottom port of the intermediate passage 40 refers to the port that communicates with the intermediate chamber 30.
  • the oil accumulated in the intermediate chamber 30 may be delivered into the inner cavity of the second compression portion 20 using only the supplemental refrigerant.
  • the compressor further includes a supplemental air passage 50 for conveying the supplemental refrigerant.
  • the compressor is provided with an air supply passage 50 for accumulating oil into the intermediate passage 40 to supply the insufflation refrigerant to accelerate the delivery of the oil in the intermediate chamber 30 into the inner cavity of the second compression portion 20.
  • the supplemental air passage 50 communicates with the intermediate chamber 30 and is located below the intermediate chamber 30. Since the air supply passage 50 communicates with the intermediate chamber 30 and is located below the intermediate chamber 30, when the air supply refrigerant is introduced into the intermediate chamber 30 through the air supply passage 50, the air supply refrigerant passes through the oil accumulation from the lower side of the oil accumulation. The oil is atomized. Since the fluidity of the atomized oil is greater than the oil in the liquid state, the atomized oil is transported by the refrigerant to the intermediate passage 40 at a high speed, and the atomized oil is delivered to the second compression portion 20. The efficiency in the chamber is high, and the atomized oil is discharged efficiently from the intermediate chamber 30. That is, in the present embodiment, the air supply passage 50 communicates with the intermediate chamber 30 and is located below the intermediate chamber 30, so that the efficiency of the oil accumulation oil being discharged into the intermediate chamber 30 can be improved.
  • the oil accumulated in the intermediate chamber 30' cannot be discharged in time, the oil accumulated in the intermediate chamber 30' is instantaneously sucked away by the second compressing portion 20', and the second compressing portion 20' is inhaled excessively.
  • the oil will be oiled when it is exhausted.
  • the second compression portion 20' causes a sharp increase in the force of the sliding piece when the oil is pressed, and the sliding piece is ejected and rolled. When the child is detached, the two will have an impact; at the same time, the sliding piece may also hit the bottom hole of the cylinder groove, and there is a hidden danger of the cylinder.
  • the above problem is solved because the oil accumulation in the intermediate chamber 30 can be discharged in a timely and effective manner.
  • the compressor further includes a housing assembly 90, the intermediate passage 40 is located inside the housing assembly 90, and the air supply passage 50 is arranged along the radial direction of the first compression portion 10, and the intermediate passage 40 Arranged along the axial direction of the first compressing portion 10.
  • the direction A is the axial direction of the first compression portion 10.
  • the intermediate passage 40 is located outside the casing assembly 90 with respect to the intermediate passage 40. In the present embodiment, since the intermediate passage 40 is located inside the casing assembly 90, the overall structure of the compressor is compact and the overall volume is small.
  • the supplemental gas passage 50 is arranged in the direction B.
  • the compressor further includes an augmenting member 100 in communication with the supplemental passage 50
  • the supplemental passage 50 includes a first passage section 501 and a second passage section 502.
  • One end of the first channel segment 501 is in communication with the augmenting component 100
  • the other end of the first channel segment 501 is in communication with one end of the second channel segment 502
  • the other end of the second channel segment 502 is in communication with the intermediate cavity 30, wherein
  • the centerline of the channel segment 501 has an angle with the centerline of the second channel segment 502.
  • the plenum refrigerant of the reinforced component 100 passes through the first passage section 501 and the second passage section 502 and is then introduced into the intermediate chamber 30 to transport the oil accumulated in the intermediate chamber 30 into the inner cavity of the second compression portion 20.
  • the angle between the centerline of the first channel segment 501 and the centerline of the second channel segment 502 is 90°. After such setting, even if the air supply passage 50 is disposed, it is convenient to press the accumulated oil in the intermediate chamber 30 into the inner cavity of the second compression portion 20 by the supplemental refrigerant.
  • the compressor further includes a drainage structure disposed in the intermediate passage 40, and one end of the drainage structure extends into the intermediate chamber 30.
  • the provision of the drainage structure in the intermediate passage 40 in the present embodiment can increase the flow velocity of the refrigerant, thereby improving the efficiency of the oil containing the refrigerant being discharged into the intermediate chamber.
  • the oil in the intermediate chamber 30 is discharged with high efficiency.
  • the drainage structure is the drainage tube 110. Further, one end of the draft tube 110 facing the intermediate chamber 30 is inclined. Since one end of the drainage tube 110 is inclined, a part of the inclined end of the drainage tube is located below the liquid level of the oil accumulation in the intermediate chamber 30, and the refrigerant carrying the oil accumulation in the intermediate chamber 30 can enter the drainage from the inclined end of the drainage tube.
  • the tube 110 flows into the lumen of the second compression portion 20.
  • the technical solution is more convenient for the refrigerant to squeeze the oil in the intermediate chamber 30 into the drainage tube with respect to the one end of the drainage tube extending all the way to the liquid level of the oil accumulation, so that the suction resistance of the second compression portion 20 can be reduced.
  • the compressor further includes a first flange 60 and a first cover plate 70.
  • the first flange 60 is disposed below the first compression portion 10, and the lower side of the first flange 60 has a first cavity 61; the first cover plate 70 is disposed below the first flange 60, and the first cover plate 70
  • the side facing the first flange 60 has a second cavity 71.
  • the first cavity 61 and the second cavity 71 together form an intermediate cavity 30, and the air inlet of the air supply passage 50 is opened at the bottom of the second cavity 71.
  • the first cavity 61 of the first flange 60 and the second cavity 71 of the first cover plate 70 are common to the intermediate cavity 30 formed by the first cavity 61 of the first flange 60.
  • the intermediate chamber 30 is formed, and the volume of the intermediate chamber 30 is relatively large.
  • the refrigerant and the oil accumulation have a larger space fusion, so that the fusion volume of the refrigerant and the oil accumulation is larger, and more oil can be transported to the refrigerant to the refrigerant.
  • the inside of the inner cavity of the second compression portion 20 is formed, and the volume of the intermediate chamber 30 is relatively large.
  • the first cover plate 70 is further provided with a groove 72 , and the air supply passage 50 communicates with the second cavity 71 via the groove 72 .
  • the first cover plate 70 is further provided with a recess 72, the oil in the intermediate chamber 30 is concentrated in the recess 72, that is, the thickness of the oil in the recess 72 is larger than that in the intermediate chamber 30.
  • the compressor further includes a draft tube 110 disposed in the intermediate passage 40, and one end of the draft tube 110 facing the second recess 71 is inclined. Since one end of the draft tube is inclined, a portion of the inclined end of the draft tube extends into the recess 72, and the refrigerant carrying the oil in the intermediate chamber 30 can be located above the recess 72 from the inclined end of the drain tube. Part of the flow enters the drainage tube and flows into the lumen of the second compression portion 20.
  • the refrigerant in the intermediate chamber 30 needs to squeeze the oil in the recess 72 into the drainage tube, and the refrigerant in the intermediate chamber 30 can be squeezed into the drainage tube.
  • This embodiment can reduce the suction resistance of the second compression portion 20, It is advantageous for the second compression portion 20 to inhale.
  • the first compressing portion 10 includes a first cylinder 11
  • the second compressing portion 20 includes a second cylinder 21, and the first cylinder 11 and the second cylinder 21 are stacked
  • the compressor Also included is a partition 80 disposed between the first cylinder 11 and the second cylinder 21 and a first flange 60 located below the first cylinder 11, the intermediate passage 40 being formed in the first cylinder 11, the second cylinder 21, and the partition 80 and the combination of the first flange 60.
  • the intermediate passage 40 is disposed inside the casing assembly 90, the overall structure of the compressor is compact and small in volume.
  • the second cylinder 21 is provided with a first through hole 211
  • the partition 80 is provided with a second through hole 81 communicating with the first through hole 211
  • the first cylinder A third through hole 111 communicating with the second through hole 81 is disposed on the first flange 60
  • a fourth through hole 62 communicating with the third through hole 111 is disposed on the first flange 60, wherein the first through hole 211 and the second hole
  • the inner wall surface of the through hole 81, the third through hole 111, and the fourth through hole 62 forms an intermediate passage 40.
  • the air supply port of the air supply passage 50 is disposed at the bottom of the groove 72 (see FIGS. 3 to 5), and the reinforcing member (second circuit) is passed through.
  • the inflowing gas flows out from the bottom of the groove 72, enters the intermediate chamber 30 of the primary exhaust gas, and is sucked into the second cylinder 21 through the draft tube 110.
  • the groove 72 at the bottom of the intermediate chamber 30 has the function of accommodating the oil in the intermediate chamber.
  • the oil in the intermediate chamber 30 flows into the groove 72 and enters the draft tube 110 along with the refrigerant gas flowing through the intermediate chamber 30.
  • the passage 40 is drawn into the second cylinder 21 (see Fig. 2).
  • the oil discharge mode of the first embodiment the intermediate gas (ie, the supplemental refrigerant) flows out from the inside of the oil located in the groove 72, and the oil can be carried into the second cylinder 21, and the intermediate gas flow is rushed in.
  • the groove 72 causes the oil to be disturbed or bubbles, the atomization effect produces oil droplets, and the second cylinder 21 takes the oil droplets when inhaling (see Fig. 2).
  • the intermediate passage 40 is built in the pump body and placed in the drainage tube 110.
  • the lower end inlet of the drainage tube 110 is formed in a wedge shape and protrudes into the bottom of the groove 72 (see Figs. 3 and 12), and can guide the entrainment on the one hand.
  • the oil reduces the resistance of the intermediate chamber 30 gas to the second cylinder 21 for inhalation.
  • the structure of the first flange 60 is different from that of the first embodiment in that the first flange 60 has a first cavity on a side away from the first cylinder 11 . 61.
  • the fourth through hole 62 is in communication with the first cavity 61.
  • the difference between the second embodiment and the first embodiment is that the third embodiment of the second embodiment is not provided with a drainage tube.
  • the other configuration of the second embodiment is the same as that of the first embodiment, and details are not described herein again.
  • the inclined shape of the end of the drainage tube facing the first cover plate 70 is changed to a flat shape, and the end surface of the flat opening and the first flange 60 are The end faces away from the first compression portion 10 are flush.
  • the effect of eliminating the oil accumulation in the intermediate chamber 30 of the third embodiment is the same as the effect of eliminating the oil accumulation in the intermediate chamber 30 of the second embodiment.
  • the side of the first flange 60 remote from the first cylinder 11 has a first cavity 61, and the fourth through hole 62 is opposite to the first cavity 61. isolation.
  • the fourth embodiment differs from the first embodiment in that the intermediate passage 40 of the fourth embodiment is not provided with a draft tube, and the fourth through hole 62 of the first flange 60 is isolated from the first recess 61.
  • Other settings of the fourth embodiment are the same as those of the first embodiment, and are not described herein again.
  • the fourth through hole 62 of the first flange 60 is separated from the first cavity 61, the first through hole 211, the second through hole 81, and the third
  • the inner wall surface of the through hole 111 and the fourth through hole 62 forms an intermediate passage 40 which projects into the recess 72, thereby improving the efficiency of the oil in the intermediate chamber 30 being discharged out of the intermediate chamber 30 without setting in the intermediate passage.
  • the drainage tube has a simple structure.
  • the fifth embodiment is different from the first embodiment in that a part of the intermediate passage 40 is located outside the casing assembly 90, and an inlet end of the intermediate passage 40 is located at the bottom of the intermediate chamber 30.
  • a portion of the intermediate passage is disposed outside of the housing assembly 90 to facilitate cleaning and replacement of the intermediate passage.
  • the refrigerant flowing out of the first compression portion 10 squeezes the oil accumulated in the intermediate chamber 30 into the inlet of the intermediate passage 40, entering from the middle.
  • the passage 40 is delivered into the inner cavity of the second compression portion 20, so that the present embodiment can effectively discharge the oil accumulation in the intermediate chamber 30.
  • the intermediate passage 40 includes a first flow passage section 401 and a second flow passage section 402 communicating with the first flow passage section 401, and the first flow passage section 401 is located in the casing.
  • the second flow path section 402 is located outside the assembly 90, and the end of the first flow path section 401 away from the second flow path section 402 communicates with the inner cavity of the second compression part 20, and the second flow path section One end of the 402 that is away from the first flow path section 401 is located at the bottom of the intermediate chamber 30.
  • the first flow path section 401 is disposed outside the housing assembly 90, when the first flow path section 401 is blocked or damaged, it can be easily replaced or cleaned without disassembling the housing assembly 90.
  • the first flow path segment 401 since the first flow path section 401 is disposed outside the housing assembly 90, when the first flow path section 401 is blocked or damaged, it can be easily replaced or cleaned without disassembling the housing assembly 90.
  • the first flow path segment 401 since the first flow path section 401 is disposed outside the housing assembly 90
  • the compressor further includes a first flange 60 and a first cover plate 70.
  • the first flange 60 is disposed below the first compression portion 10, and the lower side of the first flange 60 has a first cavity 61; the first cover plate 70 is disposed below the first flange 60, and the first cover plate 70
  • the side facing the first flange 60 has a second cavity 71, and the first cavity 61 and the second cavity 71 together form an intermediate cavity 30.
  • Another difference between the fifth embodiment and the first embodiment is that the inlet end of the intermediate passage 40 is opened on the bottom wall of the second recess 71.
  • the first cover plate 70 is further provided with a recess 72, and the intermediate passage 40 communicates with the second recess 71 via the recess 72. Since the first cover plate 70 is provided with the recess 72, the oil in the intermediate chamber 30 is concentrated in the recess 72. The refrigerant flowing out of the first compressing portion 10 presses the oil into the inlet of the intermediate passage 40 at the groove 72. In the process, the oil in the intermediate chamber is automatically concentrated in the recess 72 to be squeezed by the refrigerant. The inlet into the intermediate passage 40 is circulated in such a manner as to accelerate the speed at which the oil in the intermediate chamber 30 is squeezed into the intermediate passage 40, thereby improving the efficiency in which the accumulated oil in the intermediate chamber is discharged.
  • the compressor further includes a supplemental air passage 50 that communicates with the inner passages of the intermediate passage 40 and the second compression portion 20, respectively.
  • the air supply passage 50 communicates with one end of the first flow path section 401 that is away from the second flow path section 402, and the supplemental refrigerant is merged with the refrigerant flowing out of the first flow path section 401, and then sent to the second compression part.
  • the accumulation of oil in the intermediate chamber 30 is accelerated into the inner cavity of the second compression portion 20.
  • the difference from the first embodiment is that the air supply passage 50 is opened on the second cylinder 21, and is disposed at other positions with respect to the air supply passage 50.
  • the length of the air supply passage 50 is short, and the refrigerant has the lowest speed loss on the air supply passage 50, that is, the refrigerant carrying the oil accumulation can be delivered to the inner cavity of the second compression portion 20 at the fastest speed, thereby improving The efficiency with which the oil is discharged into the intermediate chamber.
  • the refrigerant gas in the intermediate chamber 30 When the refrigerant gas in the intermediate chamber 30 is discharged through the bottom of the groove 72, it will carry the oil together into the first flow path section 401 and the second flow path section 402 of the intermediate passage 40, or the oil accumulation is preferentially discharged into the intermediate flow passage, and then After being mixed with the supplemental refrigerant supplied from the augmenting member, it is sucked into the second cylinder 21 to prevent accumulation of oil in the intermediate chamber.
  • the second flow path section 402 of the intermediate passage 40 is disposed outside the compressor casing by means of a pipeline and communicates with the reinforced gas supply line.
  • the application also provides an air conditioner comprising a compressor, the compressor being the aforementioned compressor.
  • the second compression portion 20 can be prevented from being pressed with oil, the compressor can be operated smoothly, and the sliding piece of the second compression portion 20 can be prevented from hitting the roller or the bottom hole of the groove, thereby improving the operational reliability of the compressor.
  • FIG. 21 is a flow chart showing the flow of the refrigerant and the lubricating oil of the compressor of FIG. 19. As shown in FIG. 21, solid arrows indicate the flow direction of the refrigerant, and hollow arrows indicate the flow direction of the lubricating oil. As shown in FIG. 21, the low-pressure refrigerant sucked from the air intake port enters the intermediate chamber 30 via the first compressing portion 10, and then is mixed with the intermediate-pressure refrigerant supplied from the augmenting member 100 via the intermediate passage 40 to enter the second cylinder 21, The mixed gas is discharged through the exhaust pipe through the second cylinder 21.
  • Fig. 22 is a flow chart showing the flow of the refrigerant and the lubricating oil of the compressor of Fig. 2. As shown in Fig. 22, solid arrows indicate the flow direction of the refrigerant, and hollow arrows indicate the flow direction of the lubricating oil.
  • the above-described embodiments of the present invention achieve the following technical effects: since the bottom end port of the intermediate passage is located at the bottom of the intermediate chamber, the refrigerant flowing out from the first compression portion will be in the intermediate chamber.
  • the oil accumulates into the intermediate passage, and the oil accumulates with the refrigerant gas and/or the refrigerant flowing out of the first compression portion into the inner cavity of the second compression portion. Since the oil in the intermediate chamber is squeezed into the intermediate passage by the refrigerant, the refrigerant flowing out from the first compression portion in the prior art only brings part of the oil accumulation on the oil surface in the intermediate chamber into the intermediate passage.
  • the oil input into the intermediate passage is faster, and the oil in the intermediate chamber is discharged out of the intermediate chamber more efficiently; when only the refrigerant flowing out from the first compression portion is used, the oil in the intermediate chamber is delivered to the first portion.
  • the inner portion of the two compression portions is inside, at least a part of the intermediate passage is located outside the casing assembly of the compressor, and when the intermediate passage located outside the casing assembly fails, it is convenient to carry out the intermediate passage located outside the casing assembly. Clean or replace the new intermediate channel.

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Abstract

一种压缩机及具有其的空调器，压缩机包括：第一压缩部（10）、第二压缩部（20）、中间腔（30）和中间通道（40）；从第一压缩部（10）流出的冷媒进入中间腔（30），中间通道（40）连通中间腔（30）与第二压缩部（20）的内腔，中间通道（40）的底端端口位于中间腔（30）的底部，以利用补气冷媒和/或从第一压缩部（10）流出的冷媒将位于中间腔（30）内的积油输送至第二压缩部（20）的内腔内，当仅利用从第一压缩部（10）流出的冷媒将位于中间腔（30）内的积油输送至第二压缩部（20）的内腔时，至少一部分的中间通道（40）位于压缩机的壳体组件（90）的外部，提高了中间腔（30）中的积油被排出中间腔（30）的效率。

Description

压缩机及具有其的空调器 技术领域
本发明涉及压缩机领域，具体而言，涉及一种压缩机及具有其的空调器。
背景技术
随着人们生活质量提高，以及对环保的重视，在冬季采暖更多使用空调热泵等环境友好型取暖方式，因此，空调低温制热能力和能效也越来越受到关注。为适应北方寒冷地区的采暖，空调系统对制热能力和能效的要求也越来越高，双级增焓压缩机在低温环境下能大制热量，以及能适应运行温度范围宽的特性，使其在空调热泵系统中的应用越趋广泛。
现有双级增焓压缩机(见图1)，经常会在中间腔内出现大量积油，中间腔内的积油不能及时排出，将引起二级缸瞬时吸入过量积油，进而出现第二压缩部压油现象，导致压缩机的第二压缩部的阻力矩波动大，使电机力矩输出不平稳，引起瞬时电流增大，甚至导致压缩机停机。同时，由于压缩机的第二压缩部的压缩阻力大，因而第二压缩部的滑片头部受力大，进而导致滑片与滚子脱离，出现滑片撞击滚子或槽底孔，影响压缩机可靠性。
如图1所示，现有技术中的压缩机包括第一压缩部10’、第二压缩部20’、中间腔30’、中间通道40’、补气通道50’、第一法兰60’、第一盖板70’、隔板80’、壳体组件90’与增焓部件100’。其中，第一压缩部10’排出的积油在与中间腔30’的腔壁接触就会附着凝结，逐渐堆积；中间腔30’的出口设置在最上端(即中间通道40’的底部端口位于中间腔30’的上部)，积油随经过中间腔30’缓冲后的中压气体排出的量有限。当中间腔30’积满油时，第二压缩部20’抽吸气体，气体的总量减少而产生真空，进而直接将积油吸入第二压缩部20’中，因此就会出现瞬间的大量吸油的现象。另外，由于第一压缩部10’流出的冷媒只将积油的液面部分的积油带到中间通道，因而中间腔中的积油被排出中间腔的速度低。即现有技术中，中间腔中的积油被排出中间腔的效率较低。
发明内容
本发明的主要目的在于提供一种压缩机及具有其的空调器。以解决现有技术中，中间腔中的积油被排出中间腔的效率低的问题。
为了实现上述目的，根据本发明的一个方面，提供了一种压缩机，包括：第一压缩部；第二压缩部；中间腔，从第一压缩部流出的冷媒进入中间腔；中间通道，中间通道连通中间腔与第二压缩部的内腔，中间通道的底端端口位于中间腔的底部，以利用补气冷媒和/或从第一压缩部流出的冷媒将位于中间腔内的积油输送至第二压缩部的内腔内，当仅利用从第一压缩部流出的冷媒将位于中间腔内的积油输送至第二压缩部的内腔内时，至少一部分的中间通道位于压缩机的壳体组件的外部。
进一步地，压缩机还包括用于输送补气冷媒的补气通道。
进一步地，补气通道与中间腔连通且位于中间腔的下方。
进一步地，压缩机还包括壳体组件，中间通道位于壳体组件的内部，补气通道沿第一压缩部的径向布置，中间通道沿第一压缩部的轴向布置。
进一步地，压缩机还包括与补气通道连通的增焓部件，补气通道包括：第一通道段；第二通道段，第一通道段的一端与增焓部件连通，第一通道段的另一端与第二通道段的一端连通，第二通道段的另一端与中间腔连通，其中，第一通道段的中心线与第二通道段的中心线之间具有夹角。
进一步地，压缩机还包括设置在中间通道内的引流结构，引流结构的一端伸入至中间腔内。
进一步地，压缩机还包括：第一法兰，设置在第一压缩部的下方，第一法兰的下侧具有第一凹腔；第一盖板，设置在第一法兰的下方，第一盖板的朝向第一法兰的一侧具有第二凹腔，第一凹腔和第二凹腔共同形成中间腔，补气通道的补气口开设在第二凹腔的底壁上。
进一步地，第一盖板上还设有凹槽，补气通道经凹槽与第二凹腔连通。
进一步地，压缩机还包括设置在中间通道内的引流管，引流管的朝向第二凹腔的一端设为倾斜状。
进一步地，第一压缩部包括第一气缸，第二压缩部包括第二气缸，第一气缸和第二气缸叠置，压缩机还包括设置在第一气缸和第二气缸之间的隔板以及位于第一气缸下方的第一法兰，中间通道形成在第一气缸、第二气缸、隔板和第一法兰的组合体上。
进一步地，第二气缸上设有第一通孔，隔板上设有与第一通孔连通的第二通孔，第一气缸上设有与第二通孔连通的第三通孔，第一法兰上设有与第三通孔连通的第四通孔，其中，第一通孔、第二通孔、第三通孔与第四通孔的内壁面形成中间通道。
进一步地，第一法兰的远离第一气缸的一侧具有第一凹腔，第四通孔与第一凹腔连通或者相隔离。
进一步地，中间通道的入口端位于中间腔的底部。
进一步地，中间通道包括第一流道段和与第一流道段连通的第二流道段，第一流道段位于壳体组件的外部，第二流道段位于壳体组件的内部，第一流道段的远离第二流道段的一端与第二压缩部的内腔连通，第二流道段的远离第一流道段的一端位于中间腔的底部。
进一步地，压缩机还包括：第一法兰，设置在第一压缩部的下方，第一法兰的下侧具有第一凹腔；第一盖板，设置在第一法兰的下方，第一盖板的朝向第一法兰的一侧具有第二凹腔，第一凹腔和第二凹腔共同形成中间腔，中间通道的入口端开设在第二凹腔的底壁上。
进一步地，第一盖板上还设有凹槽，中间通道经凹槽与第二凹腔连通。
进一步地，压缩机还包括补气通道，补气通道分别与中间通道和第二压缩部的内腔连通。
进一步地，第二压缩部包括第二气缸，补气通道开设在第二气缸上。
根据本发明的另一方面，提供了一种空调器，包括压缩机，压缩机为前述的压缩机。
应用本发明的技术方案，由于中间通道的底端端口位于中间腔的底部，因而，从第一压缩部流出的冷媒将中间腔中的积油挤压入中间通道，进而积油随补气冷媒和/或从第一压缩部流出的冷媒进入第二压缩部的内腔内而被排出。由于中间腔中的积油被冷媒挤压入中间通道中，相对于现有技术中从第一压缩部流出的冷媒只将中间腔中的积油表面的部分积油带入中间通道而言，本申请中积油输入中间通道的速度较快，中间腔中的积油被排出中间腔的效率较高；当仅利用从第一压缩部流出的冷媒将位于中间腔内的积油输送至第二压缩部的内腔内时，至少一部分的中间通道位于压缩机的壳体组件的外部，当位于壳体组件的外部的中间通道发生故障时，方便对位于壳体组件的外部的中间通道进行清理或者更换新的中间通道。
附图说明
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：
图1示出了现有技术的双级增焓压缩机的剖视图；
图2示出了本发明的实施例一的压缩机的剖视图；
图3示出了图2的压缩机的第一气缸、第二气缸、隔板和第一法兰等部件装配后的剖视图；
图4示出了图3的第一盖板的立体图；
图5示出了图3的第一盖板的剖视图；
图6示出了图3的第一盖板的主视图；
图7示出了图3的第一气缸、第二气缸、隔板和第一法兰的组合体的立体图；
图8示出了图3的第二气缸的立体图；
图9示出了图3的第一气缸的立体图；
图10示出了图3的隔板的立体图；
图11示出了图3的第一法兰的立体图；
图12示出了图2的引流管的剖视图；
图13示出了本发明的实施例二的压缩机的剖视图；
图14示出了图13的压缩机的第一气缸、第二气缸、隔板和第一法兰等部件装配后的剖视图；
图15示出了本发明的实施例三的压缩机的引流管的剖视图；
图16示出了本发明的实施例四的压缩机的第一气缸、第二气缸、隔板和第一法兰等部件装配后的剖视图；
图17示出了图16的第一法兰的剖视图；
图18示出了图16的第一法兰的立体图；
图19示出了本发明的实施例五的压缩机的剖视图；
图20示出了图19的压缩机的第一气缸、第二气缸、隔板和第一法兰等部件装配后的剖视图；
图21示出了图19的压缩机的冷媒和润滑油的流动示意图；以及
图22示出了图2的压缩机的冷媒和润滑油的流动示意图。
其中，上述附图包括以下附图标记：
10、第一压缩部；11、第一气缸；111、第三通孔；20、第二压缩部；21、第二气缸；211、第一通孔；30、中间腔；40、中间通道；401、第一流道段；402、第二流道段；50、补气通道；501、第一通道段；502、第二通道段；60、第一法兰；61、第一凹腔；62、第四通孔；70、第一盖板；71、第二凹腔；72、凹槽；80、隔板；81、第二通孔；90、壳体组件；100、增焓部件；110、引流管。
具体实施方式
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。
实施例一
如图2和图3所示，本申请的实施例一提供了一种压缩机。压缩机包括第一压缩部10、第二压缩部20、中间腔30与中间通道40；从第一压缩部10流出的冷媒进入中间腔30；中间通道40连通中间腔30与第二压缩部20的内腔，中间通道40的底端端口位于中间腔30的底部，以利用补气冷媒和/或从第一压缩部10流出的冷媒将位于中间腔30内的积油输送至第二压缩部20的内腔内，当仅利用从第一压缩部10流出的冷媒将位于中间腔30内的积油输送至第二压缩部20的内腔内时，至少一部分的中间通道40位于压缩机的壳体组件90的外部。
由于中间通道40的底端端口位于中间腔30的底部，因而，从第一压缩部10流出的带有压力的冷媒能够更好地将中间腔30中的积油挤压入中间通道40，进而积油随补气冷媒和/或 从第一压缩部10流出的冷媒进入第二压缩部20的内腔内而被排出。由于中间腔30中的积油被冷媒挤压入中间通道40中，相对于现有技术中从第一压缩部10流出的冷媒只将中间腔中的积油表面的部分积油带入中间通道，本申请中积油输入中间通道40的速度较快，中间腔30中的积油被排出中间腔30的效率较高，当仅利用从第一压缩部10流出的冷媒将位于中间腔30内的积油输送至第二压缩部20的内腔内时，至少一部分的中间通道40位于压缩机的壳体组件90的外部，当位于壳体组件的外部的中间通道发生故障时，方便对位于壳体组件的外部的中间通道40进行清理或者更换新的中间通道。
优选地，如图2所示，为了加快排出积油的速度，本实施例中，利用补气冷媒和从第一压缩部10流出的冷媒共同将位于中间腔30内的积油输送至第二压缩部20的内腔内。该技术方案中，通过补气冷媒和从第一压缩部10流出的冷媒同时将中间腔30内的积油输送至第二压缩部20的内腔内，相对于只通过冷媒将中间腔30内的积油输送至第二压缩部20的内腔内，冷媒被输送的速度较快，进而携带有积油的冷媒被排出中间腔30的效率较高，即中间腔30中的积油被排出中间腔30的效率较高。具体地，该压缩机为双级增焓压缩机。
在附图未示出的替代实施例中，当压缩机中不含增焓部件时，当采用图19所示的中间通道40时，即中间通道40的底端端口位于中间腔30的底部时，可以仅利用从第一压缩部10流出的冷媒将位于中间腔30内的积油输送至第二压缩部20的内腔内。
需要注意的是，在图19所示的结构中，中间通道40的底端端口指的是与中间腔30相连通的那个端口。
在其它的实施例中，也可以仅利用补气冷媒将位于中间腔30内的积油输送至第二压缩部20的内腔内。
如图2和图3所示，本实施例中，压缩机还包括用于输送补气冷媒的补气通道50。压缩机设置补气通道50以向中间通道40积油通入补气冷媒，以加快将中间腔30内的积油输送至第二压缩部20的内腔内。
如图2和图3所示，本实施例中，补气通道50与中间腔30连通且位于中间腔30的下方。由于补气通道50与中间腔30连通且位于中间腔30的下方，因此通过补气通道50向中间腔30通入补气冷媒时，补气冷媒从积油的下方穿出积油，使积油发生雾化。由于发生雾化的积油的流动性大于液体状态的积油，因此，雾化的积油被冷媒输送至中间通道40的速度快，雾化的积油被输送至第二压缩部20的内腔内的效率高，雾化的积油被排出中间腔30的效率高。即本实施例中补气通道50与中间腔30连通且位于中间腔30的下方，能提高积油积油被排出中间腔30的效率。
现有技术中，由于中间腔30’内的积油不能及时排出，积聚在中间腔30’内的积油会瞬时被第二压缩部20’吸走，而第二压缩部20’吸入过量冷冻油会在排气时出现压油现象，因液体的可压缩性小于气体的可压缩性，因此第二压缩部20’压油时导致滑片受力急剧增大，滑片被弹出，与滚子脱离，两者将产生撞击；同时，滑片还可能撞击气缸槽底孔，存在气缸断裂隐患。
采用本技术方案，由于能及时有效地排出中间腔30内的积油，因此解决了上述问题。
如图2所示，在实施例一中，压缩机还包括壳体组件90，中间通道40位于壳体组件90的内部，补气通道50沿第一压缩部10的径向布置，中间通道40沿第一压缩部10的轴向布置。
如图2所示，方向A为第一压缩部10的轴向。相对于中间通道40位于壳体组件90的外部，本实施例中，由于中间通道40位于壳体组件90的内部，因而压缩机的整体结构较紧凑，整体体积较小。
优选地，补气通道50沿方向B布置。
如图2与图3所示，实施例一中，压缩机还包括与补气通道50连通的增焓部件100，补气通道50包括第一通道段501和第二通道段502。第一通道段501的一端与增焓部件100连通，第一通道段501的另一端与第二通道段502的一端连通，第二通道段502的另一端与中间腔30连通，其中，第一通道段501的中心线与第二通道段502的中心线之间具有夹角。增焓部件100的补气冷媒经过第一通道段501和第二通道段502后被通入中间腔30，以将位于中间腔30内的积油输送至第二压缩部20的内腔内。
优选地，第一通道段501的中心线与第二通道段502的中心线之间的夹角为90°。这样设置之后，即便于布置补气通道50，又便于利用补气冷媒将位于中间腔30内的积油压入第二压缩部20的内腔中。
如图2与图3所示，实施例一中，压缩机还包括设置在中间通道40内的引流结构，引流结构的一端伸入至中间腔30内。
由于冷媒在引流结构中的流动时受到的阻力小，因此，本实施例在中间通道40内设置引流结构能够提高冷媒的流动速度，进而提高携带有冷媒的积油被排出中间腔的效率，因此，中间腔30中的积油被排出的效率较高。
具体地，引流结构为引流管110。且引流管110的朝向中间腔30的一端设为倾斜状。由于引流管110的一端设为倾斜状，因此引流管的倾斜端的一部分位于中间腔30内的积油的液面以下，中间腔30中的携带积油的冷媒可从引流管的倾斜端进入引流管110，进而流至第二压缩部20的内腔内。相对于引流管的一端全部伸入积油的液面以下，本技术方案更便于冷媒把中间腔30内的油液挤压入引流管，从而可减小第二压缩部20的吸气阻力。
如图2与图3所示，实施例一中，压缩机还包括第一法兰60和第一盖板70。第一法兰60设置在第一压缩部10的下方，第一法兰60的下侧具有第一凹腔61；第一盖板70设置在第一法兰60的下方，第一盖板70的朝向第一法兰60的一侧具有第二凹腔71，第一凹腔61和第二凹腔71共同形成中间腔30，补气通道50的补气口开设在第二凹腔71的底壁上。
相对于只有第一法兰60的第一凹腔61构成的中间腔30，本技术方案中，由于第一法兰60的第一凹腔61和第一盖板70的第二凹腔71共同形成中间腔30，中间腔30的容积较大， 在中间腔30中，冷媒与积油具有更大空间融合，因而冷媒与积油的融合体积较大，更多的积油能被冷媒输送至第二压缩部20的内腔内。
如图2至图6所示，本申请中，第一盖板70上还设有凹槽72，补气通道50经凹槽72与第二凹腔71连通。该方案中，由于第一盖板70上还设有凹槽72，因而中间腔30内的积油都会集中在凹槽72中，即凹槽72中的积油厚度尺寸大于中间腔30中其它位置的积油厚度尺寸，并且由于补气通道50经凹槽72与第二凹腔71连通，因而补气冷媒被通入中间腔30时，穿出积油的厚度尺寸较大，积油被雾化的程度较大，进而积油被被排出中间腔30的效率较大。
如图2、图3与图12所示，实施例一中，压缩机还包括设置在中间通道40内的引流管110，引流管110的朝向第二凹腔71的一端设为倾斜状。由于引流管的一端设为倾斜状，因此引流管倾斜状的一端的部分伸入凹槽72，中间腔30中的携带积油的冷媒可从引流管倾斜状的一端的位于凹槽72上方的部分进入引流管，进而流至第二压缩部20的内腔内。相对于引流管的一端全部伸入凹槽72内，中间腔30中的冷媒需要把凹槽72内油液挤压入引流管，本实施例可减小第二压缩部20的吸气阻力,有利于第二压缩部20吸气。
如图2至图11所示，实施例一中，第一压缩部10包括第一气缸11，第二压缩部20包括第二气缸21，第一气缸11和第二气缸21叠置，压缩机还包括设置在第一气缸11和第二气缸21之间的隔板80以及位于第一气缸11下方的第一法兰60，中间通道40形成在第一气缸11、第二气缸21、隔板80和第一法兰60的组合体上。
采用本技术方案，由于中间通道40设在壳体组件90内部，因而压缩机的整体结构较紧凑、体积较小。
如图2至图11所示，实施例一中，第二气缸21上设有第一通孔211，隔板80上设有与第一通孔211连通的第二通孔81，第一气缸11上设有与第二通孔81连通的第三通孔111，第一法兰60上设有与第三通孔111连通的第四通孔62，其中，第一通孔211、第二通孔81、第三通孔111与第四通孔62的内壁面形成中间通道40。
上述设置中间通道40的方式较为简单，便于加工。
实施例一的冷媒和积油的流动过程：本技术方案中，将补气通道50的补气口设置在凹槽72的底部(见图3至图5)，经过增焓部件(第二回路)流入的气体从凹槽72的底部流出，进入一级排气的中间腔30，再经过引流管110被吸入第二气缸21中。中间腔30底部的凹槽72具有容纳中间腔积油的作用，中间腔30内的积油流入凹槽72，并跟随补气冷媒和流经中间腔30的冷媒一起进入引流管110，经中间通道40被吸入第二气缸21中(见图2)。实施例一的积油排出方式：中间补气气体(即补气冷媒)从位于凹槽72的积油内部流出，可将积油携带进入第二气缸21中，同时，中间补气气流冲入凹槽72时使积油出现扰动或气泡而产生雾化效果出现油滴，第二气缸21吸气时将油滴带走(见图2)。将中间通道40内置于泵体上，并置入引流管110，引流管110的下端入口设置成楔形，伸入凹槽72的底部(见图3和图12)，一方面可引导带走积油，另一方面减小中间腔30气体流出到第二气缸21吸气的阻力。
实施例二
如图13和图14所示，实施例二中，第一法兰60的结构与实施例一的不同之处在于：第一法兰60的远离第一气缸11的一侧具有第一凹腔61，第四通孔62与第一凹腔61连通。
另外，实施例二与实施例一的区别为，实施例二的中间通道40中没有设置引流管，实施例二的其它设置与实施例一相同，这里不再赘述。
实施例三
在实施例一的基础上，如图15所示，实施例三中，将引流管的朝向第一盖板70的一端的倾斜状更改为平口状，该平口的端面与第一法兰60的远离第一压缩部10的端面平齐。实施例三的排除中间腔30内的积油的效果与实施例二的排除中间腔30内的积油的效果相同。
实施例四
如图16、图17与图18所示，实施例四中，第一法兰60的远离第一气缸11的一侧具有第一凹腔61，第四通孔62与第一凹腔61相隔离。实施例四与实施例一的区别是，实施例四的中间通道40中没有设置引流管，且第一法兰60的第四通孔62与第一凹腔61相隔离。实施例四的其它设置与实施例一相同，这里不再赘述。
相对于实施例一，实施例四的技术方案中，由于第一法兰60的第四通孔62与第一凹腔61相隔离，因而第一通孔211、第二通孔81、第三通孔111与第四通孔62的内壁面形成中间通道40伸入凹槽72内，进而在提高中间腔30内的积油被排出中间腔30的效率的同时，不需要在中间通道内设置引流管，结构简单。
实施例五
如图19和图20所示，实施例五与实施例一的不同之处在于，中间通道40的一部分位于壳体组件90的外部，中间通道40的入口端位于中间腔30的底部。
该实施例中，将中间通道的一部分设置在壳体组件90的外部，方便对中间通道的清理与更换。本实施例中，由于中间通道40的入口端位于中间腔30的底部，因而从第一压缩部10流出的冷媒将位于中间腔30内的积油挤压入中间通道40的入口，进入从中间通道40输送至第二压缩部20的内腔内，因此，本方案能有效的排出中间腔30内的积油。
具体地，如图19和图20所示，实施例五中，中间通道40包括第一流道段401和与第一流道段401连通的第二流道段402，第一流道段401位于壳体组件90的外部，第二流道段402位于壳体组件90的内部，第一流道段401的远离第二流道段402的一端与第二压缩部20的内腔连通，第二流道段402的远离第一流道段401的一端位于中间腔30的底部。本实施例中，由于将第一流道段401设置在壳体组件90的外部，因而当第一流道段401堵塞或者损坏时，在不需要拆卸壳体组件90的基础上，可以方便更换或者清理第一流道段401。
如图19和图20所示，实施例五中，压缩机还包括第一法兰60和第一盖板70。第一法兰60设置在第一压缩部10的下方，第一法兰60的下侧具有第一凹腔61；第一盖板70设置在 第一法兰60的下方，第一盖板70的朝向第一法兰60的一侧具有第二凹腔71，第一凹腔61和第二凹腔71共同形成中间腔30。实施例五与实施例一的另一个不同之处在于，中间通道40的入口端开设在第二凹腔71的底壁上。
如图19和图20所示，实施例五中，第一盖板70上还设有凹槽72，中间通道40经凹槽72与第二凹腔71连通。由于第一盖板70上设置有凹槽72，因而中间腔30中的积油集中在凹槽72中。从第一压缩部10流出的冷媒在凹槽72处将积油挤压入中间通道40的入口，在此过程中，中间腔中的积油自动集中在凹槽72中，以被冷媒挤压入中间通道40的入口，如此循环，加快了中间腔30中的积油被挤压入中间通道40的速度，进而提高了中间腔内的积油被排出的效率。
如图19和图20所示，实施例五中，压缩机还包括补气通道50，补气通道50分别与中间通道40和第二压缩部20的内腔连通。本实施例中，补气通道50与第一流道段401的远离第二流道段402的一端连通，补气冷媒与从第一流道段401流出的冷媒汇合后，被输送至第二压缩部20的内腔内，加快将中间腔30内的积油输送至第二压缩部20的内腔内。
如图19和图20所示，实施例五中，与实施例一的不同之处在于，补气通道50开设在第二气缸21上，相对于补气通道50设置在其它的位置，本实施例中的补气通道50的长度较短，冷媒在补气通道50上的速度损耗最低，即携带积油的冷媒能以最快的速度被输送至第二压缩部20的内腔内，提高了积油被排出中间腔的效率。
下面对图19和图20中的压缩机的排出中间腔30内的积油的过程进行描述：
中间腔30内的冷媒气体经凹槽72底部排出时将携带积油一起进入中间通道40的第一流道段401和第二流道段402内，或积油被优先排入中间流道，后与增焓部件提供的补气冷媒混合后被吸入第二气缸21，防止中间腔积油聚集。中间通道40的第二流道段402采用管路的方式设在压缩机壳体外部，并与增焓补气管路连通。
本申请还提供了一种空调器，该空调机包括压缩机，压缩机为前述的压缩机。
本申请的技术方案具有以下的技术效果：
采用本发明的压缩机，可防止第二压缩部20压油，使压缩机运行平稳，防止第二压缩部20的滑片撞击滚子或槽底孔，提升了压缩机运行可靠性。
其中，图21示出了图19的压缩机的冷媒和润滑油的流动示意图，如图21所示，实心箭头表示冷媒的流动方向，空心箭头表示润滑油的流动方向。如图21所示，自吸气口吸入的低压冷媒经第一压缩部10进入中间腔30内，然后经中间通道40与增焓部件100提供的中压冷媒混合后进入第二气缸21，上述混合气体经第二气缸21后经排气管排出。
图22示出了图2的压缩机的冷媒和润滑油的流动示意图，如图22所示，实心箭头表示冷媒的流动方向，空心箭头表示润滑油的流动方向。
从以上的描述中，可以看出，本发明上述的实施例实现了如下技术效果：由于中间通道的底端端口位于中间腔的底部，因而，从第一压缩部流出的冷媒将中间腔中的积油挤压入中间通道，进而积油随补气冷媒和/或从第一压缩部流出的冷媒进入第二压缩部的内腔内而被排出。由于中间腔中的积油被冷媒挤压入中间通道中，相对于现有技术中从第一压缩部流出的冷媒只将中间腔中的积油表面的部分积油带入中间通道而言，本申请中积油输入中间通道的速度较快，中间腔中的积油被排出中间腔的效率较高；当仅利用从第一压缩部流出的冷媒将位于中间腔内的积油输送至第二压缩部的内腔内时，至少一部分的中间通道位于压缩机的壳体组件的外部，当位于壳体组件的外部的中间通道发生故障时，方便对位于壳体组件的外部的中间通道进行清理或者更换新的中间通道。
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (19)

  1. 一种压缩机，其特征在于，包括：
    第一压缩部(10)；
    第二压缩部(20)；
    中间腔(30)，从所述第一压缩部(10)流出的冷媒进入所述中间腔(30)；
    中间通道(40)，所述中间通道(40)连通所述中间腔(30)与所述第二压缩部(20)的内腔，所述中间通道(40)的底端端口位于所述中间腔(30)的底部，以利用补气冷媒和/或从所述第一压缩部(10)流出的冷媒将位于所述中间腔(30)内的积油输送至所述第二压缩部(20)的内腔内，当仅利用从所述第一压缩部(10)流出的冷媒将位于所述中间腔(30)内的积油输送至所述第二压缩部(20)的内腔内时，至少一部分的所述中间通道(40)位于压缩机的壳体组件(90)的外部。
  2. 根据权利要求1所述的压缩机，其特征在于，所述压缩机还包括用于输送补气冷媒的补气通道(50)。
  3. 根据权利要求2所述的压缩机，其特征在于，所述补气通道(50)与所述中间腔(30)连通且位于所述中间腔(30)的下方。
  4. 根据权利要求2或3所述的压缩机，其特征在于，所述压缩机还包括壳体组件(90)，所述中间通道(40)位于所述壳体组件(90)的内部，所述补气通道(50)沿所述第一压缩部(10)的径向布置，所述中间通道(40)沿所述第一压缩部(10)的轴向布置。
  5. 根据权利要求4所述的压缩机，其特征在于，所述压缩机还包括与所述补气通道(50)连通的增焓部件(100)，所述补气通道(50)包括：
    第一通道段(501)；
    第二通道段(502)，所述第一通道段(501)的一端与所述增焓部件(100)连通，所述第一通道段(501)的另一端与所述第二通道段(502)的一端连通，所述第二通道段(502)的另一端与所述中间腔(30)连通，其中，所述第一通道段(501)的中心线与所述第二通道段(502)的中心线之间具有夹角。
  6. 根据权利要求4所述的压缩机，其特征在于，所述压缩机还包括设置在所述中间通道(40)内的引流结构，所述引流结构的一端伸入至所述中间腔(30)内。
  7. 根据权利要求3所述的压缩机，其特征在于，所述压缩机还包括：
    第一法兰(60)，设置在所述第一压缩部(10)的下方，所述第一法兰(60)的下侧具有第一凹腔(61)；
    第一盖板(70)，设置在所述第一法兰(60)的下方，所述第一盖板(70)的朝向所述第一法兰(60)的一侧具有第二凹腔(71)，所述第一凹腔(61)和所述第二凹腔(71) 共同形成所述中间腔(30)，所述补气通道(50)的补气口开设在所述第二凹腔(71)的底壁上。
  8. 根据权利要求7所述的压缩机，其特征在于，所述第一盖板(70)上还设有凹槽(72)，所述补气通道(50)经所述凹槽(72)与所述第二凹腔(71)连通。
  9. 根据权利要求7所述的压缩机，其特征在于，所述压缩机还包括设置在所述中间通道(40)内的引流管(110)，所述引流管(110)的朝向所述第二凹腔(71)的一端设为倾斜状。
  10. 根据权利要求4所述的压缩机，其特征在于，所述第一压缩部(10)包括第一气缸(11)，所述第二压缩部(20)包括第二气缸(21)，所述第一气缸(11)和所述第二气缸(21)叠置，所述压缩机还包括设置在所述第一气缸(11)和所述第二气缸(21)之间的隔板(80)以及位于所述第一气缸(11)下方的第一法兰(60)，所述中间通道(40)形成在所述第一气缸(11)、所述第二气缸(21)、所述隔板(80)和所述第一法兰(60)的组合体上。
  11. 根据权利要求10所述的压缩机，其特征在于，所述第二气缸(21)上设有第一通孔(211)，所述隔板(80)上设有与所述第一通孔(211)连通的第二通孔(81)，所述第一气缸(11)上设有与所述第二通孔(81)连通的第三通孔(111)，所述第一法兰(60)上设有与所述第三通孔(111)连通的第四通孔(62)，其中，所述第一通孔(211)、第二通孔(81)、第三通孔(111)与第四通孔(62)的内壁面形成所述中间通道(40)。
  12. 根据权利要求11所述的压缩机，其特征在于，所述第一法兰(60)的远离所述第一气缸(11)的一侧具有第一凹腔(61)，所述第四通孔(62)与所述第一凹腔(61)连通或者相隔离。
  13. 根据权利要求1所述的压缩机，其特征在于，所述中间通道(40)的入口端开设在所述中间腔(30)的底部。
  14. 根据权利要求13所述的压缩机，其特征在于，所述中间通道(40)包括第一流道段(401)和与所述第一流道段(401)连通的第二流道段(402)，所述第一流道段(401)位于所述壳体组件(90)的外部，所述第二流道段(402)位于所述壳体组件(90)的内部，所述第一流道段(401)的远离所述第二流道段(402)的一端与所述第二压缩部的内腔连通，所述第二流道段(402)的远离所述第一流道段(401)的一端位于所述中间腔(30)的底部。
  15. 根据权利要求13或14所述的压缩机，其特征在于，所述压缩机还包括：
    第一法兰(60)，设置在所述第一压缩部(10)的下方，所述第一法兰(60)的下侧具有第一凹腔(61)；
    第一盖板(70)，设置在所述第一法兰(60)的下方，所述第一盖板(70)的朝向所述第一法兰(60)的一侧具有第二凹腔(71)，所述第一凹腔(61)和所述第二凹腔(71) 共同形成所述中间腔(30)，所述中间通道(40)的入口端开设在所述第二凹腔(71)的底壁上。
  16. 根据权利要求15所述的压缩机，其特征在于，所述第一盖板(70)上还设有凹槽(72)，所述中间通道(40)经所述凹槽(72)与所述第二凹腔(71)连通。
  17. 根据权利要求13或14所述的压缩机，其特征在于，所述压缩机还包括补气通道(50)，所述补气通道(50)分别与所述中间通道(40)和所述第二压缩部(20)的内腔连通。
  18. 根据权利要求17所述的压缩机，其特征在于，所述第二压缩部(20)包括第二气缸(21)，所述补气通道(50)开设在所述第二气缸(21)上。
  19. 一种空调器，包括压缩机，其特征在于，所述压缩机为权利要求1至18中任一项所述的压缩机。
PCT/CN2018/089962 2017-11-30 2018-06-05 压缩机及具有其的空调器 WO2019104983A1 (zh)

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