WO2023173638A1 - 气缸、压缩机及制冷/制热系统 - Google Patents

气缸、压缩机及制冷/制热系统 Download PDF

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Publication number
WO2023173638A1
WO2023173638A1 PCT/CN2022/107017 CN2022107017W WO2023173638A1 WO 2023173638 A1 WO2023173638 A1 WO 2023173638A1 CN 2022107017 W CN2022107017 W CN 2022107017W WO 2023173638 A1 WO2023173638 A1 WO 2023173638A1
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Prior art keywords
cylinder
chamber
exhaust
wall
gas
Prior art date
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PCT/CN2022/107017
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English (en)
French (fr)
Inventor
雒应学
Original Assignee
广州市德善数控科技有限公司
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Publication date
Priority claimed from CN202210257232.XA external-priority patent/CN116792316A/zh
Priority claimed from CN202210601537.8A external-priority patent/CN114934902A/zh
Application filed by 广州市德善数控科技有限公司 filed Critical 广州市德善数控科技有限公司
Publication of WO2023173638A1 publication Critical patent/WO2023173638A1/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
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to the field of compressors, and in particular to a cylinder, a compressor and a refrigeration/heating system.
  • the purpose of the present invention is to solve at least one of the technical problems existing in the prior art.
  • the present invention proposes a cylinder that can effectively reduce the noise during compressor operation to a minimum and at the same time reduce leakage during the compression process to improve the energy efficiency ratio of the compressor.
  • An embodiment of the present invention provides a cylinder, which includes:
  • the inner wall of the cylinder serving as the compression chamber is disposed within the outer wall of the cylinder;
  • At least one cavity for sound attenuation and buffering is provided between the outer wall of the cylinder and the inner wall of the cylinder, and at least part of the cavity is composed of the inner wall of the cylinder.
  • one or more separation reinforcement ribs are provided between the outer wall of the cylinder and the inner wall of the cylinder, and the adjacent separation reinforcement ribs are in contact with the inner side of the outer wall of the cylinder and the inner wall of the cylinder.
  • the outer side surrounds the cavity, and at least part of the dividing reinforcement ribs is provided with at least one channel, and the channel communicates at least part of the cavity.
  • the channel includes an upper channel and a lower channel
  • the upper channel is disposed relatively close to or at the top of the separation reinforcement
  • the lower channel is disposed at the top of the separation reinforcement.
  • gas-liquid separation is achieved through the spacing between the upper channel and the lower channel, so that the upper channel is used to circulate gas, and the lower channel is used to circulate liquid.
  • the cylinder is provided with a general air inlet hole and a general exhaust hole
  • the inner wall of the cylinder is provided with a suction hole and an exhaust port
  • the cavity includes a suction side chamber and an exhaust side chamber.
  • each suction side chamber is arranged adjacently and connected through part of the passage.
  • Each exhaust side chamber has a plurality of exhaust side chambers. The side chambers are arranged adjacent to each other and communicate with each other through the passage in the other part.
  • a high and low pressure partition is provided between the suction side chamber and the exhaust side chamber, and a heat insulation groove is provided in the high and low pressure partition.
  • the ratio of the cross-sectional area of the cavity to the cross-sectional area of the channel is: 12.5-10:1, and the ratio of the cross-sectional area of the channel to the cross-sectional area of the exhaust port is 2 -8:1.
  • the cylinder includes an upper cylinder and a lower cylinder that can be connected to each other.
  • the upper cylinder includes an outer wall of an upper cylinder and an inner wall of an upper cylinder.
  • the lower cylinder includes an outer wall of a lower cylinder and an inner wall of a lower cylinder.
  • the upper cylinder includes an outer wall of a lower cylinder and an inner wall of a lower cylinder.
  • the outer wall of the cylinder and the outer wall of the lower cylinder together form the outer wall of the cylinder, and the inner wall of the upper cylinder and the inner wall of the lower cylinder together form the inner wall of the cylinder;
  • the suction side chamber includes an upper suction side chamber and a lower suction side chamber that are interconnected
  • the exhaust side chamber includes an upper exhaust side chamber and a lower exhaust side chamber that are interconnected
  • the upper suction side chamber and the upper exhaust side chamber are arranged between the outer wall of the upper cylinder and the inner wall of the upper cylinder
  • the lower suction side chamber and the lower exhaust side chamber are arranged between the outer wall of the upper cylinder and the inner wall of the upper cylinder.
  • the chamber is arranged between the outer wall of the lower cylinder and the inner wall of the lower cylinder.
  • Gas enters from the main air inlet and flows through the upper suction side chamber and the lower suction side chamber, and then flows from the suction side chamber to the lower suction side chamber.
  • the air holes enter the inner wall of the cylinder, are compressed and discharged from the exhaust port, and flow through the upper exhaust side chamber, the lower exhaust side chamber, and then are sent to the main exhaust hole. .
  • An embodiment of the present invention also provides a compressor, which includes the cylinder described in any of the above embodiments.
  • the compressor further includes an oil and gas separation structure.
  • the oil and gas separation structure has a gas-liquid separation chamber.
  • the gas-liquid separation chamber Comprising a plurality of cavities, the oil and gas separation structure further includes:
  • a gap oil drainage structure which includes a mandrel and a mandrel mounting seat that cooperates with the mandrel, and a gap channel is formed between the mandrel and the mandrel mounting seat;
  • One oil passage the entrance of which is connected with the gas-liquid separation chamber, conducts oil from the gas-liquid separation chamber to the entrance of the gap channel;
  • the second oil passage is used to connect the outlet of the clearance channel and the oil pool, and introduce oil from the outlet of the clearance channel to the oil pool;
  • the oil in the gas-liquid separation chamber passes through the first oil passage, the gap passage, and the second oil passage in sequence, and is discharged to the oil pool;
  • the compressor includes:
  • a cylinder is arranged in the compressor casing, a compression chamber is provided in the cylinder, and the gas-liquid separation chamber is connected with the compression chamber;
  • a piston is disposed in the compression chamber and is drivingly connected to the driving component, and rotates in the compression chamber driven by the driving component.
  • the mandrel mounting seat is provided with an inner hole, the mandrel is assembled in the inner hole of the mandrel mounting seat, and the oil passage one and the oil passage two are misaligned with the mandrel. Distributed so as to confine the mandrel in the inner bore.
  • the oil and gas separation structure further includes a filter structure
  • the gas-liquid separation chamber is provided with an exhaust hole and an oil discharge hole
  • the filter structure is arranged in the oil discharge hole or at the oil discharge hole.
  • the inlet of the first oil passage is connected with the outlet of the filter structure.
  • the width of the gap channel is 0.001mm-0.020mm.
  • the compressor further includes:
  • a secondary bearing is provided in the compressor casing, the oil passage is provided on the secondary bearing, and the secondary bearing is provided with a hole that cooperates with the gap oil discharge structure;
  • a silencer cover is located on the lower side of the auxiliary bearing, and the second oil passage is opened on the silencer cover.
  • the gas-liquid separation chamber is connected to the main exhaust hole and the main air inlet hole;
  • the inner wall of the cylinder is provided with a suction port, and the gas enters the compression chamber through the main air inlet, gas-liquid separation chamber, and suction port in sequence;
  • An exhaust port is provided on the inner wall of the cylinder.
  • the gas in the compression chamber compressed by the piston enters the gas-liquid separation chamber through the exhaust port and is discharged from the gas-liquid separation chamber through the gas-liquid separation chamber.
  • the general exhaust hole discharges out of the cylinder.
  • An embodiment of the present invention also provides a compressor, which includes a compressor housing, a driving assembly, a main bearing, an auxiliary bearing, a piston, a sliding vane and the cylinder described in any of the above embodiments.
  • the driving assembly, main bearing, The auxiliary bearing, piston and sliding vane are all arranged in the compressor casing, the main bearing and the auxiliary bearing are respectively fixed on both sides of the cylinder, the piston is accommodated in the compression chamber, and is connected through the rotating shaft and the driving assembly.
  • the driving assembly drives the piston to rotate through the rotating shaft, and the sliding piece is movably installed in the cylinder and movablely cooperates with the piston to separate the compression chamber;
  • the cylinder includes an upper cylinder and a lower cylinder.
  • a middle partition is provided between the upper cylinder and the lower cylinder.
  • An upper compression chamber is provided on the upper cylinder.
  • the cavity of the upper cylinder includes an upper intake buffer chamber and an upper cylinder. Exhaust buffer chamber, the upper air intake buffer chamber and the upper exhaust buffer chamber surround the upper compression chamber; a lower compression chamber is provided on the lower cylinder, and the air intake is under the cavity of the lower cylinder Buffer chamber and lower exhaust buffer chamber, the lower intake buffer chamber and the lower exhaust buffer chamber surround the lower compression chamber; the upper intake buffer chamber and the lower intake buffer chamber are connected in series, The upper exhaust buffer chamber and the lower exhaust buffer chamber are connected in series.
  • the compressor further includes an upper silencing cover located on the upper part of the upper cylinder, and the low-pressure gas enters the lower casing through the first channel formed by the upper silencing cover, the upper cylinder and the middle partition.
  • Air inlet buffer chamber; the lower air inlet buffer chamber and the upper air inlet buffer chamber are connected through a second channel, and part of the low-pressure gas located in the lower air inlet buffer cavity enters the air inlet buffer chamber through the second channel.
  • the upper air intake buffer chamber In the upper air intake buffer chamber.
  • the compressor further includes an upper silencing cover and a lower silencing cover.
  • the upper silencing cover is located above the main bearing.
  • An upper silencing cavity is formed between the upper silencing cover and the main bearing.
  • the upper silencing cover is located above the main bearing.
  • the cavity is connected to the exhaust port of the upper cylinder, and the upper silencing chamber is also connected to the lower exhaust buffer chamber.
  • the high-pressure gas discharged from the upper cylinder is discharged to the lower row through the upper silencing chamber.
  • the lower silencing cover is located at the lower part of the auxiliary bearing.
  • a lower silencing cavity is formed between the lower silencing cover and the auxiliary bearing.
  • the lower silencing cavity is connected with the exhaust port of the lower cylinder.
  • the lower silencing cavity is connected with the exhaust port of the lower cylinder.
  • the silencing chamber is also connected to the lower exhaust buffer chamber, and the high-pressure gas discharged from the lower cylinder is discharged to the lower exhaust buffer chamber through the lower silencing chamber;
  • the lower exhaust buffer chamber is connected with the upper exhaust buffer chamber, and the high-pressure gas discharged from the upper cylinder and the lower cylinder flows to the upper exhaust buffer chamber after passing through the lower exhaust buffer chamber. And it is discharged out of the cylinder from the upper exhaust buffer chamber.
  • the upper silencing chamber and the lower silencing chamber are composed of multiple interconnected cavities, and high-pressure gas enters from one end of the upper silencing chamber or the lower silencing chamber and is discharged from the other end;
  • the lower exhaust buffer cavity is composed of a plurality of interconnected sub-exhaust buffer cavities.
  • the sub-exhaust buffer cavities located at both ends are respectively the terminal sub-exhaust buffer cavity and the front-terminal sub-exhaust buffer cavity.
  • the upper silencer cavity and The terminal sub-exhaust buffer cavity is connected, the lower muffler cavity is connected with the sub-exhaust buffer cavity adjacent to the terminal sub-exhaust buffer cavity; the front terminal exhaust buffer cavity is connected with the upper exhaust buffer cavity One end of the cavity is connected, and high-pressure gas is discharged out of the cylinder from the other end of the upper exhaust buffer cavity.
  • An embodiment of the present invention also provides a refrigeration/heating system, which includes the compressor described in any of the above embodiments, an evaporator and a condenser, and there is a refrigerant between the compressor, the evaporator, and the condenser. Circular flow.
  • cavities are provided on the outer wall and the inner wall of the cylinder, so that the inner wall of the cylinder can realize subtle force-following deformation under the action of external force during the compression process of the compressor, which can ensure that the piston rotor in the compressor is in contact with the inner wall.
  • the sealing performance of the inner wall of the cylinder can reduce leakage during the compression process and reduce the occurrence of the piston rotor getting stuck on the inner wall of the cylinder.
  • the combination of multiple cavities and their corresponding settings can also have an impact on the suction and exhaust actions of the compressor. Functions such as silencing and turbulence to minimize the noise when the compressor is running.
  • Figure 1 is a schematic structural diagram of Embodiment 1 of the present invention.
  • Figure 2 is a front view of Embodiment 1 of the present invention.
  • Figure 3 is a cross-sectional view along line A-A in Figure 2 .
  • Figure 4 is a schematic diagram of the internal structure of the second embodiment.
  • Figure 5 is an enlarged view of part A of Figure 4.
  • Figure 6 is a schematic structural diagram of the gas-liquid separation chamber in Embodiment 2.
  • Figure 7 is a schematic structural diagram of the gap oil drainage structure of Embodiment 2.
  • Figure 8 is a schematic structural diagram of the cylinder in Embodiment 2.
  • Figure 9 is a schematic structural diagram of the separation reinforcement ribs and channels in Embodiment 2.
  • Fig. 10 is a cross-sectional view of a two-cylinder compressor according to the third embodiment.
  • Figure 11 is a diagram of the air intake route and oil discharge route of the dual-cylinder compressor in Embodiment 3.
  • FIG. 12 is a cross-sectional view along the AA direction in FIG. 11 .
  • FIG. 13 is a cross-sectional view along the BB direction in FIG. 11 .
  • Figure 14 is a gas outlet route diagram of the dual-cylinder compressor of the third embodiment.
  • the cylinder of this embodiment is used in the compressor pump body. Its function is to form a seal that can withstand high pressure together with the crankshaft shell (main bearing), auxiliary bearing, crankshaft and piston/integrated rotating shaft.
  • the compression chamber 210 continuously repeats the actions of inhalation, compression and exhaust through circular motion.
  • the cylinder includes a cylinder outer wall 100 , an inner cylinder wall 200 and at least one cavity 300 .
  • the outer wall 100 of the cylinder is provided with mounting positions and openings for assembly with other parts of the compressor, such as the crankshaft shell (main bearing) of the compressor, the auxiliary bearing silencer cover, the oil control system and the gas refrigerant system, etc.; wherein the cylinder
  • the inner wall 200 serves as the compression chamber 210 and cooperates with the piston rotor/integrated rotating shaft in the compressor.
  • the inner wall 200 of the cylinder is set inside the outer wall 100 of the cylinder.
  • the inner wall 200 of the cylinder is set as a flexible structure; the cavity 300 is used for noise reduction and buffering.
  • the cavity 300 is provided between the cylinder outer wall 100 and the cylinder inner wall 200, and at least part of the cavity 300 is composed of the cylinder inner wall 200, so that the cylinder inner wall 200 can be deformed by changing the cavity 300.
  • the design of the cavity 300 combined with the compression process of the compressor can ensure that the cylinder inner wall 200 achieves subtle force-following deformation under the action of external forces. This can be ensured through flexible deformation.
  • the sealing performance between the piston rotor/integrated rotating shaft and the cylinder inner wall 200 in the compressor can reduce leakage during the compression process, and can also reduce the occurrence of the cylinder inner wall 200 blocking the piston rotor.
  • the combination and correspondence of multiple cavities 300 The setting can also have functions such as silencing and disturbing the suction and exhaust movements of the compressor, thereby minimizing the noise during compressor operation.
  • the method of changing the cavity 300 may be to make the cavity 300 concave by extrusion, or it may be to deform the cylinder inner wall 200 so that the cavity 300 extends outward.
  • the cylinder inner wall 200 As a flexible structure, it has the ability to deform, so the connection between the cylinder inner wall 200 and the piston rotor can also adapt to changes, because the hollow cavities 300 allow the cylinder inner wall 200 to undergo radial pressure from the crankshaft, piston/integrated rotating shaft It will deform under force to adapt to the trajectory profile of the crankshaft and piston when they rotate, achieving the best sealing effect.
  • the deformation ability based on the flexible structure can ensure that the matching gap between the active cooling rotor and the cylinder inner wall 200 is always maintained at a preset size during the compression process.
  • An appropriate matching gap can ensure sealing performance and avoid high-pressure refrigerant caused by an excessive gap. Leakage and energy efficiency ratio are reduced, and the piston rotor and the inner wall of the cylinder 200 are prevented from being stuck due to too small a gap.
  • one or more separation reinforcement ribs 400 are provided between the cylinder outer wall 100 and the cylinder inner wall 200 .
  • the adjacent separation reinforcement ribs 400 are in contact with the inner side of the cylinder outer wall 100 and the cylinder inner wall.
  • the outside of 200 forms a cavity 300 .
  • the cylinder outer wall 100 and the cylinder inner wall 200 are respectively connected by the separating reinforcement ribs 400, so that the cavity 300 provided between the cylinder outer wall 100 and the cylinder inner wall 200 is divided into a high-pressure cavity 300 and a low-pressure cavity 300.
  • the separating reinforcement ribs 400 form multiple high-pressure cavities 300 and/or multiple low-pressure cavities 300, thereby improving the suction and exhaust process of the cylinder and making the noise reduction more obvious.
  • the separation reinforcement ribs 400 connecting the cylinder outer wall 100 and the cylinder inner wall 200 can also improve the strength of the cylinder and extend its service life.
  • At least part of the partition reinforcement 400 is provided with at least one channel 410, and the channel 410 connects at least part of the cavity 300.
  • the channel 410 is used to communicate with adjacent cavities 300, such as multiple high-pressure cavities 300 or multiple low-pressure cavities 300, but the high-pressure cavities 300 and the low-pressure cavities 300 are not connected.
  • a high and low pressure separation part 130 is provided between the suction side chamber 301 and the exhaust side chamber 302.
  • a heat insulation groove 131 is provided in the high and low pressure separation part 130, which can effectively reduce the gap between the high pressure and high temperature zone and the low pressure and low temperature zone. The heat is transferred directly to avoid directly causing the suction temperature to be too high.
  • the high and low pressure partition 130 can be a reinforced rib structure, but no channel 410 is provided on it.
  • the end surface of the high and low pressure partition 130 can also be processed to be horizontal.
  • the high-pressure cavity 300 and the low-pressure cavity 300 are stably separated to realize the liquid separation and silencing functions on the suction side of the cylinder and the liquid separation and silencing functions on the exhaust side respectively.
  • the separation reinforcement ribs 400 are respectively connected to the cylinder outer wall 100 and the cylinder inner wall 200 through two ends in the length direction, and the openings at both ends of the channel 410 are respectively provided on both sides of the width direction of the separation reinforcement ribs 400.
  • the opening area at both ends of the channel 410 is usually relatively smaller than the area of the cavity 300, thus forcing the flow rate of the fluid refrigerant to change to disrupt the flow direction and flow.
  • This structure of the channel 410 can effectively eliminate suction noise.
  • gaps are formed on the separation reinforcement ribs 400, and the gaps are connected to adjacent cavities 300 respectively, and the gaps are defined as channels 410.
  • the channel 410 includes an upper channel 411 and a lower channel 412 .
  • the upper channel 411 is disposed relatively close to or at the top of the separation reinforcement 400
  • the lower channel 412 Disposed at the bottom end of the dividing reinforcement rib 400, gas-liquid separation is achieved through the spacing between the upper channel 411 and the lower channel 412, so that the upper channel 411 is used to circulate gas, and the lower channel 412 is used to circulate liquid.
  • the low-temperature gaseous refrigerant mixed with lubricating oil can be settled for the first time, achieving gas-liquid separation, improving the energy efficiency ratio, and further eliminating emissions. Air noise effect.
  • the high-pressure cavity 300 and the low-pressure cavity 300 are respectively provided with an upper channel 411 and a lower channel 412 to achieve primary gas-liquid separation on the low-pressure side and primary gas-liquid separation on the high-pressure side, and the gas-liquid separation effect is remarkable.
  • the lower channel 412 is provided at the bottom end of the partition reinforcement 400, and the channel 410 is used to communicate with multiple high-pressure cavities 300 or multiple low-pressure cavities 300, the lower channel 412 is used to communicate with the bottom of the high-pressure cavity 300, The lower channel 412 is used to connect the bottom of the low-pressure cavity 300.
  • the settled oil will be evenly distributed to each cavity 300. Setting the corresponding lubricating oil return channel 410 can provide convenience for subsequent oil filtering and return, improving the performance of the compressor. better.
  • the cylinder is provided with a total intake hole 110 and a total exhaust hole 120
  • the inner wall 200 of the cylinder is provided with a suction hole 220 and an exhaust port 230
  • the chamber includes a suction side chamber 301 and the exhaust side chamber 302.
  • the gas enters from the main air inlet hole 110, flows through the suction side chamber 301 in sequence, enters the cylinder inner wall 200 from the suction hole 220, and is discharged from the exhaust port 230 after being compressed. It flows through the exhaust side chamber 302 and then is sent to the main exhaust hole 120 .
  • multiple suction side chambers 301 are provided, and multiple exhaust side chambers 302 are provided.
  • Each suction side chamber 301 is arranged adjacently and connected through a partial passage 410, and each exhaust side chamber 302 is adjacent. Set up and connected via channel 410 from another section.
  • gas-liquid separation can be effectively realized and exhaust noise can be eliminated, and the noise generated when the compression chamber 210 is exhausted can be reduced.
  • the total air inlet hole 110 and the total exhaust hole 120 on the cylinder can also be adjusted to the settings according to the structure of the compressor or other requirements.
  • On the crankshaft housing (main bearing) or auxiliary bearing it is guaranteed to be connected with the corresponding high/low pressure cavity 300 to achieve the same function and effect.
  • the cylinder outer wall 100 has a concave structure in the middle and a convex outer periphery.
  • the convex structure of the cylinder outer wall 100 matches the straight shell of the compressor.
  • a cavity is formed between the middle recessed position of the cylinder outer wall 100 and the straight body shell of the compressor. This cavity can reduce the direct metal contact area between the cylinder and the compressor casing, thereby forming a thermal insulation bridge, reducing the heat transfer between the pump body and the casing when the compressor is running, and preventing the compressor casing from overheating.
  • the outer diameter of the upper and lower bearings matching the cylinder can be designed to be larger than the outer diameter of the cylinder.
  • the outer diameter of the cylinder wall 100 can be Lower than the outer diameter of the upper and lower bearings, a heat-insulating cavity can also be formed after being installed into the housing.
  • the cylinder includes an upper cylinder and a lower cylinder that can be connected to each other through a middle partition.
  • the upper cylinder includes an outer wall of the upper cylinder and an inner wall of the upper cylinder.
  • the lower cylinder includes an outer wall of the lower cylinder and an inner wall of the lower cylinder. , the outer wall of the upper cylinder and the outer wall of the lower cylinder together form the outer wall of the cylinder 100, and the inner wall of the upper cylinder and the inner wall of the lower cylinder together form the inner wall 200 of the cylinder.
  • the displacement of the compressor can be increased, processing is facilitated, and at the same time, by extending The length of the circulation can fully reduce the suction noise, separate the lubricating oil mixed in the settled gaseous refrigerant from the liquid that is not completely vaporized, and prevent the liquid material from directly entering the compression chamber 210 to cause liquid shock.
  • the suction side chamber 301 includes an upper suction side chamber and a lower suction side chamber that are connected to each other
  • the exhaust side chamber 302 includes an upper exhaust side chamber and a lower exhaust side chamber that are connected to each other.
  • the upper suction side chamber and the upper exhaust side chamber are arranged between the outer wall of the upper cylinder and the inner wall of the upper cylinder
  • the lower suction side chamber and the lower exhaust side chamber are arranged between the outer wall of the lower cylinder and the lower cylinder body
  • the gas enters from the main air inlet hole 110, flows through the upper suction side chamber and the lower suction side chamber, enters the cylinder inner wall 200 from the suction hole 220, and is discharged from the exhaust port 230 after being compressed.
  • Arranging multiple suction-side chambers 301 and multiple exhaust-side chambers 302 in series can achieve the desired effect of silencer and oil-gas separation. Among them, by extending the circulation path of the refrigerant and increasing the number of flow direction changes, it can further facilitate the complete vaporization of the liquid refrigerant and the settlement of the lubricating oil. Combined with the flow direction of the gaseous refrigerant in Figure 2, the upper cylinder and the lower cylinder can be respectively set according to the specific situation. Can be beneficial to noise reduction and oil and gas separation.
  • chambers such as sound attenuation, heat insulation and oil-gas separation can also be arranged between adjacent suction side chambers 301.
  • the adjacent exhaust side chambers 302 can be arranged between adjacent exhaust side chambers.
  • a silencing cover, silencing chamber, etc. of the compressor are externally connected between the side chambers 302 to further improve the silencing effect.
  • multiple suction side chambers 301 and exhaust side chambers 302 may be provided respectively.
  • at least two suction side chambers are provided, and at least two exhaust side chambers are provided. Set up two, each suction side chamber in the upper cylinder is connected in series, and each exhaust side chamber is connected in series. The same is true for the lower cylinder to fully silence and separate gas and liquid.
  • this embodiment also provides a compressor.
  • the compressor can be a rotor compressor.
  • the compressor includes the cylinder of the above embodiment, which can actively reduce the noise of the suction and exhaust device and actively mix the lubricating oil with the compressor.
  • the gaseous refrigerant is separated and can effectively improve the sealing between the piston rotor in the compressor and the inner wall of the cylinder, thereby minimizing the noise during compressor operation and reducing leakage during the compressor process, thereby improving the energy efficiency of the compressor.
  • ⁇ COP value is improved to a certain extent compared with the existing technical level.
  • this embodiment provides an oil and gas separation structure.
  • This structure is provided on the exhaust passage of the compressor and is used to separate the refrigerant and lubricating oil in the compressor. It at least includes a gas-liquid separation chamber. 1. Oil passage one 5, gap oil drainage structure and oil passage two 6;
  • the inlet of the oil passage 5 is connected with the gas-liquid separation chamber 1, and oil is guided from the gas-liquid separation chamber 1 to the entrance of the gap channel;
  • the second oil passage 6 is used to connect the outlet of the clearance channel and the oil pool 7, and introduce oil from the outlet of the clearance channel to the oil pool 7;
  • the gas-liquid separation chamber 1 is used to separate refrigerant and lubricating oil. As shown in Figure 6, the gas-liquid separation chamber has a partitioned labyrinth structure, which can maximize the separation of refrigerant and lubricating oil and use gravity to stratify;
  • the pressure difference between the gas-liquid separation chamber 1 and the oil pool 7 and the gap oil discharge structure can cause the lubricating oil to pass through the oil passage 1 5, the gap passage, and the oil passage 2 6 from the high temperature and high pressure gas-liquid separation chamber 1 in sequence. Enter the low-pressure oil pool 7;
  • the clearance oil discharge mechanism includes a mandrel mounting seat 4 and a mandrel 3.
  • An inner hole is provided in the center of the mandrel mounting seat 4 to clearance match the mandrel 3.
  • the top of the inner hole is a cone.
  • the top of the inner hole is tapered and flared, which is also convenient for installing the mandrel 3 into the mandrel mounting seat 4.
  • the oil passage one 5 and the oil passage two 6 are misaligned with the mandrel 3 to form a blocking position, that is, the oil passage one 5 and the oil passage two 6 Channel two 6 is not axial with core axis 3;
  • the matching clearance between the inner hole of the mandrel 3 and the mandrel mounting base 4 is 0.002mm.
  • the 0.002mm gap is required, measure the dimensions of the mandrel mounting seat 4 with the inner hole ground through the hinge beam and the mandrel 3 with the finely ground outer circle, select the 0.002mm gap, and then install them into the compressor. (As shown in Figure 5), combined with the needs of compressors under different working conditions and corresponding lubricating oil, the oil discharge gap can be artificially controlled when assembling the compressor to meet the needs;
  • the gap oil drainage structure of this embodiment is a structure that can independently realize the oil drainage function and effectively prevent the high and low pressure gas cross-flow of the compressor. Its installation location is not limited to the crankshaft shell of the compressor, the compressor housing 11, the exhaust pipe, On the cylinder 12, auxiliary bearing cover 13, silencer cover 14 or temperature regulator;
  • the above-mentioned oil pool 7 is provided in the compressor casing 11 and is located below the cylinder 12.
  • the compressor also includes an oil supply device.
  • the oil supply device is connected to the oil pool 7 and is used to transfer the oil.
  • the oil in the pool 7 is delivered to the cylinder 12 ; an oil supply device is also provided in the compressor casing 11 and located below the cylinder 12 .
  • this embodiment provides a filter structure for an oil and gas separation structure.
  • the filter structure is used to filter impurities in the lubricating oil to make the oil circuit circulation in the gap smoother;
  • the gas-liquid separation chamber 1 is provided with an exhaust hole and an oil discharge hole 2, and the filter structure is arranged in the oil discharge hole 2 or between the oil discharge hole 2 and the oil passage 5;
  • the filter structure is a filter core 8.
  • the filter core 8 is a high-density microporous filter structure.
  • the size of the filter pores on the filter core 8 is designed to be less than 0.005mm, so that it can filter impurities and foreign matter in the settled lubricating oil;
  • the upper opening of the oil passage one 5 is located at the lower opening of the filter structure, that is, the inlet of the oil passage one 5 is connected with the outlet of the filter structure. Therefore, the filtered liquid lubricating oil will pass through the filter structure and the oil passage.
  • Channel one 5 is introduced into the gap oil drainage structure;
  • a magnetic block 9 is added to the filter structure and is applied to the filter core.
  • the shape of the magnetic block 9 can be a T-shape, a cylinder or a concave-shaped strong magnet. In actual use, its shape is not limited and can be selected according to actual conditions such as the installation space.
  • the magnetic block 9 is set on the filter core. The top of 8 can absorb metal impurities in the lubricating oil to prevent the metal impurities from clogging the filter element 8.
  • the filter element 8 since the filter element 8 has a certain length, the adsorption capacity of the magnetic block 9 when it is placed on the top of the filter element 8 is difficult to cover the entire filter element 8 , and metal impurities are easy to accumulate in the lower part of the lubricating oil, so a magnetic ring (not shown in the figure) can be added at a position where the filter element 8 is flush with the bottom of the gas-liquid separation chamber 1, which can improve the adsorption effect. , extend the service life of the filter element 8;
  • the shape of the filter core 8 is not limited to a cylindrical shape, and may also be a square cylinder or other shapes with a polygonal cross-section.
  • This embodiment also provides a compressor, including the oil and gas separation structure in the above embodiment.
  • the compressor also includes a compressor housing 11 and a driving assembly 15, a cylinder 12, an auxiliary bearing 13, a piston and a silencer cover 14 arranged in the compressor housing 11 (only the compressor connected to the oil and gas separation structure is indicated here. Some parts, ), when the oil-gas separation structure is applied to this compressor, the gas-liquid separation chamber 1 can be provided through the cylinder 12, and the top surface of the auxiliary bearing 13 is the bottom of the gas-liquid separation chamber 1;
  • the piston is arranged in the compression chamber 21 and is drivingly connected with the driving assembly 15, and rotates in the compression chamber 21 driven by the driving assembly 15;
  • the first oil passage 5 is opened on the auxiliary bearing 13; the second oil passage 6 is opened on the silencer cover 14; the auxiliary bearing 13 is provided with a hole to accommodate the gap oil discharge structure, and the contact surface between the auxiliary bearing 13 and the spindle mounting seat 4 Sealed connection to ensure no air leakage, which can satisfy the need for lubricating oil to be discharged from the high-pressure area to the low-pressure area using the holes of the gap oil drainage structure as a channel, and also ensure that the high and low pressures are not directly connected to cause air leakage;
  • the auxiliary bearing 13 is provided with a mounting hole (i.e., the oil drain hole 2) that matches the filter element 8, and the cylinder 12 is provided with an arc-shaped groove that matches the outer surface of the filter element 8.
  • This arc-shaped groove is The groove is used to limit the position of the filter element 8. When the compressor is inverted, tilted, or rotated, the filter element 8 will not leave the pre-installed position.
  • this embodiment also provides a cylinder.
  • the cylinder 12 includes a cylinder outer wall 122 and a cylinder inner wall 121.
  • the compression chamber 21 is formed in the cylinder inner wall 121.
  • the liquid separation chamber 1 is located between the cylinder outer wall 122 and the cylinder inner wall 121 .
  • the outer wall 122 of the cylinder is provided with mounting positions and openings for assembly with other parts of the compressor, such as the crankshaft shell (main bearing), auxiliary bearing 13, silencer cover 14, oil control system and gaseous refrigerant system of the compressor. ;
  • the compression chamber 21 cooperates with the piston rotor/integrated rotating shaft in the compressor, and the cylinder inner wall 21 is configured as a flexible structure.
  • the gas-liquid separation chamber 1 is connected with the main exhaust hole 23 and the main air inlet hole 24 .
  • the inner wall 121 of the cylinder is provided with an air suction port 25, and the gas enters the compression chamber 21 through the main air inlet 24, the gas-liquid separation chamber 1, and the air suction port 25 in sequence.
  • An exhaust port 22 is provided on the inner wall 121 of the cylinder.
  • the gas in the compression chamber 21 compressed by the piston enters the gas-liquid separation chamber 1 through the exhaust port 22 and is discharged from the total exhaust gas through the gas-liquid separation chamber 1.
  • the hole 23 exits the cylinder 12 .
  • the total exhaust hole 23 and the total air inlet hole 24 can be provided not only on the cylinder 12 but also on the upper bearing located on the upper side of the cylinder 12 or the lower bearing located on the lower side of the cylinder 12 .
  • the gas-liquid separation chamber 1 includes a plurality of cavities 26 that play a silencing and buffering role.
  • the cavity 26 is partly composed of a flexible cylinder inner wall 121 so that the cylinder inner wall 121 can be deformed by changing the cavities 26.
  • the inner wall 121 of the cylinder is set to have a certain flexible structure. Through the design of the cavity 26 and the compression process of the compressor, it can be ensured that the inner wall 121 of the cylinder realizes subtle force-following deformation under the action of external force.
  • the flexible deformation can ensure that The sealing performance between the piston rotor/integrated rotating shaft and the cylinder inner wall 121 in the compressor can reduce leakage during the compression process, and can also reduce the occurrence of the cylinder inner wall 121 blocking the piston rotor.
  • the setting can also have functions such as silencing and disturbing the suction and exhaust movements of the compressor, thereby minimizing the noise during compressor operation.
  • a part of the cavities 26 forms a suction side chamber 31, and another part of the cavities 26 forms an exhaust side chamber 32.
  • Two adjacent cavities among the plurality of cavities 26 included in the suction side chamber 26 are separated by the separation reinforcement ribs 27 provided between the cylinder outer wall 122 and the cylinder inner wall 121.
  • Two adjacent cavities 26 among the plurality of cavities 26 included in the exhaust side chamber 32 are also separated. They are separated by a partition reinforcement rib 27 provided between the cylinder outer wall 122 and the cylinder inner wall 121 .
  • a channel 28 is provided on the partition reinforcement rib 27 to connect adjacent cavities 26 .
  • the separating reinforcement ribs 27 connect the cylinder outer wall 122 and the cylinder inner wall 121, which can also improve the strength of the cylinder 12 and extend its service life.
  • the two sets of cavities 26 are divided into a high-pressure cavity (exhaust side cavity 32) and a low-pressure cavity (suction side cavity) by dividing the reinforcing ribs 27, and a heat insulation groove is provided between the high-pressure cavity and the low-pressure cavity. 29. It can effectively reduce the direct heat transfer between the high-pressure and high-temperature zone and the low-pressure and low-temperature zone to avoid directly causing the suction temperature to be too high.
  • the suction side chamber 31 is connected to the main air inlet hole 24, and the exhaust side chamber 32 is connected to the main exhaust hole 23. Gas enters from the main air inlet hole 24 and flows through the suction side.
  • the chamber 31 enters the compression chamber 21 from the suction port 25, is compressed by the piston and is discharged from the exhaust port 22, flows through the exhaust side chamber 32, and then exits from the main exhaust hole 23 discharge.
  • the channel 28 includes an upper channel 281 and a lower channel 282 .
  • the upper channel 281 is relatively close to the top of the separation reinforcement 27 or is provided at the top of the separation reinforcement 27 .
  • the channel 282 is provided at the bottom end of the dividing reinforcement rib 27.
  • the distance between the upper channel 281 and the lower channel 282 realizes gas-liquid separation, so that the upper channel 281 is used to circulate gas, so that all
  • the lower channel 282 is used to circulate liquid; by respectively setting the upper channel 281 and the lower channel 282 on the partition reinforcement 27, the low-temperature gaseous refrigerant mixed with lubricating oil can be settled for the first time to achieve gas-liquid separation and improve the energy efficiency ratio.
  • the high-pressure cavity and the low-pressure cavity are respectively provided with upper channels 281 and lower channels 282 to achieve primary gas-liquid separation on the low-pressure side, primary gas-liquid separation on the high-pressure side, and gas-liquid separation. The effect is remarkable.
  • the openings at both ends of the channel 28 are respectively provided on both sides of the width direction of the separating reinforcement rib 27. It can be understood that the area of the openings at both ends of the channel 28 is usually relatively smaller than the area of the cavity 26, thereby forcing the flow rate of the fluid refrigerant to change. Disturbing the flow direction and flow, the structure of the channel 28 can effectively eliminate the suction noise; specifically, a notch is processed on the separation reinforcement 27, and the notches are connected to the adjacent cavities 26 respectively, and the notch is defined as the channel 28.
  • the ratio of the cross-sectional area of the cavity 26 to the cross-sectional area of the channel is: 12.5 to 10:1, and the cross-sectional area of the channel is The ratio of the cross-sectional areas of the exhaust ports 22 is 2 to 8:1.
  • the outer wall of the cylinder 122 has a concave structure in the middle and a convex outer surface.
  • the convex structure of the outer wall 122 of the cylinder matches the straight shell of the compressor.
  • the outer wall 122 of the cylinder has a concave center.
  • a cavity is formed between the position and the straight shell of the compressor; this cavity can reduce the direct metal contact area between the cylinder 12 and the compressor shell, thereby forming a thermal insulation bridge, reducing the distance between the pump body and the shell when the compressor is running.
  • the outer diameter of the upper and lower bearings matching the cylinder 12 can be designed to be larger than the outer diameter of the cylinder, with the center as After the basic assembly is completed, the cylinder outer wall 122 is radially lower than the outer diameter of the upper and lower bearings, and can also form a heat-insulating cavity after being finally installed into the shell.
  • the cylinder includes an upper cylinder and a lower cylinder that can be connected to each other through a middle partition.
  • the upper cylinder includes an outer wall of the upper cylinder and an inner wall of the upper cylinder.
  • the lower cylinder includes an outer wall of the lower cylinder and a lower cylinder body. The inner wall, the outer wall of the upper cylinder and the outer wall of the lower cylinder together form the outer wall 122 of the cylinder, and the inner wall of the upper cylinder and the inner wall of the lower cylinder together form the inner wall 121 of the cylinder.
  • the compressor displacement can be increased, processing is facilitated, and at the same time,
  • the circulation length is extended to fully reduce the suction noise, separate the lubricating oil mixed in the settled gaseous refrigerant from the incompletely vaporized liquid, and prevent liquid substances from directly entering the compression chamber 21 to cause liquid shock.
  • the suction side chamber 31 includes an upper suction side chamber and a lower suction side chamber that are connected to each other
  • the exhaust side chamber 32 includes an upper exhaust side chamber and a lower exhaust side chamber that are connected to each other.
  • the upper suction side chamber and the upper exhaust side chamber are arranged between the outer wall of the upper cylinder and the inner wall of the upper cylinder
  • the lower suction side chamber and the lower exhaust side chamber are arranged between the outer wall of the lower cylinder and the lower cylinder body
  • the gas enters from the main air inlet 24, flows through the upper suction side chamber and the lower suction side chamber, enters the cylinder inner wall 121 from the suction port 25, and is discharged from the exhaust port 22 after being compressed.
  • the gaseous refrigerant flow direction can be set up according to the specific situation.
  • the upper cylinder and the lower cylinder can be arranged separately, which can be beneficial to noise reduction and oil and gas separation.
  • this embodiment also provides a refrigeration and heating system.
  • the refrigeration and heating system includes an evaporator and a condenser, and a refrigerant circulates between the compressor, the evaporator, and the condenser;
  • the refrigerant can be carbon dioxide refrigerant.
  • the compressor in the refrigeration and heating system adopts the compressor in the above embodiment.
  • the refrigerant and lubricating oil can be separated more thoroughly, improving the refrigeration effect and preventing the lubricating oil from entering the refrigeration area. It affects the refrigeration effect and also improves the return effect of lubricating oil, so that the internal parts of the compressor are fully lubricated and has a longer service life.
  • the third embodiment is to apply the cylinder of the above-mentioned Embodiment 1 to a two-cylinder compressor.
  • this embodiment also provides a compressor, including a compressor housing, a driving assembly, a main bearing, an auxiliary bearing, a piston, a sliding vane and the cylinder of the above embodiment, a driving assembly, a main bearing, and an auxiliary bearing.
  • the piston and sliding vane are all installed in the compressor casing.
  • the main bearing and the auxiliary bearing are fixed on both sides of the cylinder respectively to seal the compression chamber.
  • the piston is accommodated in the compression chamber and is connected to the driving assembly through the rotating shaft.
  • the driving assembly is driven by the rotating shaft.
  • the piston rotates, and the sliding plate is movably installed in the cylinder and flexibly cooperates with the piston to separate the compression chamber.
  • the cylinder includes an upper cylinder 101 and a lower cylinder 101, and a middle partition 103 is provided between the upper cylinder 101 and the lower cylinder 102.
  • the upper cylinder 101 and the lower cylinder 101 are respectively provided with an upper piston and a lower piston as well as an upper sliding plate and a lower sliding plate that cooperate with the upper piston and the lower piston respectively.
  • the upper piston and the lower piston are connected to the driving assembly through the same rotating shaft. The eccentric part of the piston is misaligned.
  • the upper cylinder 101 is provided with an upper compression chamber 1011, an upper intake buffer chamber 1012 and an upper exhaust buffer chamber 1013.
  • the upper air intake buffer chamber 1012 and the upper exhaust buffer chamber 1013 constitute the cavity of the upper cylinder 101, and are located between the outer wall and the inner wall of the upper cylinder 101, playing the role of silencing and buffering. At least part of the cavity It consists of the inner wall of the cylinder.
  • the upper intake buffer chamber 1012 and the upper exhaust buffer chamber 1013 surround the upper compression chamber 1011.
  • the arc occupied by the upper intake buffer chamber 1012 is smaller than the arc of the upper exhaust buffer chamber 1013; that is, the arc of the upper intake buffer chamber 1012 is
  • the angle formed by the two ends and the center point of the upper compression chamber 1011 is smaller than the angle formed by the two ends of the upper exhaust buffer chamber 1013 and the center point of the upper compression chamber 1011 .
  • the lower cylinder 102 is provided with a lower compression chamber 1021, a lower intake buffer chamber 1022 and a lower exhaust buffer chamber 1023.
  • the lower air intake buffer chamber 1022 and the lower exhaust buffer chamber 1023 constitute a cavity on the lower cylinder 102 and are located between the outer wall of the lower cylinder 102 and the inner wall of the cylinder to play the role of silencing and buffering.
  • the lower cylinder At least part of the cavity 102 is formed by the inner cylinder wall of the lower cylinder 102 .
  • the lower intake buffer chamber 1022 and the lower exhaust buffer chamber 1023 surround the lower compression chamber 1021.
  • the arc occupied by the lower intake buffer chamber 1022 is smaller than the arc of the lower exhaust buffer chamber 1023; that is, the two sides of the lower intake buffer chamber 1022
  • the angle formed by the two ends of the lower exhaust buffer chamber 1023 and the center point of the lower compression chamber 1021 is smaller than the angle formed by the two ends of the lower exhaust buffer chamber 1023 and the center point of the upper compression chamber 1021 .
  • the upper air intake buffer chamber 1012 and the lower air intake buffer chamber 1022 are connected in series, and the upper exhaust buffer chamber 1013 and the lower exhaust buffer chamber 1023 are connected in series.
  • the low-pressure gas needs to pass through the upper air intake buffer chamber 1012 and the lower air intake buffer chamber 1022.
  • the high-pressure gas needs to pass through the lower exhaust buffer chamber 1023 and the upper exhaust buffer chamber 1013 and then discharged out of the cylinder, the buffer time is longer, the sound attenuation effect and the gas-liquid separation effect are better, and its function is the same as that of the intake buffer chamber, which will not be described again here.
  • the compressor may also include an upper silencer cover 7, which is located on the upper part of the upper cylinder 101.
  • the low-pressure gas enters the lower air intake buffer through the first channel 104 formed by the upper silencer cover 7, the upper cylinder 101 and the middle partition 103.
  • through holes are provided in the upper silencer cover 7, the upper cylinder 101 and the middle partition 103, and these through holes are connected with each other to form the first channel 104.
  • the lower air intake buffer chamber 1022 and the upper air intake buffer chamber 1012 are connected through the second passage 105 , and part of the low-pressure gas located in the lower air intake buffer chamber 1022 enters into the upper air intake buffer chamber 1012 through the second passage 105 .
  • the compressor also includes an air inlet flange 106.
  • the air inlet flange 106 is disposed at the air inlet end of the first passage 104, and the air inlet flange 106 protrudes from its peripheral structure to prevent foreign matter in the cavity. , liquid lubricating oil, etc. directly enter the cylinder suction port.
  • the low-pressure gas enters the compressor through the compressor air inlet 21, and then enters the lower air inlet buffer chamber 1022 after passing through the first channel 104.
  • Some of the low-pressure gas passes through the lower air inlet buffer chamber 1022 and then enters the lower compression chamber 1021, and some low-pressure gas also enters the lower air inlet buffer chamber 1022. From the lower air intake buffer chamber 1022, it enters the upper air intake buffer chamber 1012 through the second passage 105, and then enters the upper compression chamber 1011.
  • the compressor may also include an upper silencer cover 7 and a lower silencer cover 8.
  • the upper silencer cover 7 is located on the upper part of the main bearing 5.
  • An upper silencer chamber 71 is formed between the upper silencer cover 7 and the main bearing 5.
  • the upper silencer chamber 71 is connected to the upper cylinder.
  • the exhaust ports of 101 are connected, and the upper silencing chamber 71 is also connected with the lower exhaust buffer chamber 1023.
  • the high-pressure gas discharged from the upper cylinder 7 passes through the upper silencing chamber 71 and reaches the lower exhaust buffer chamber 1023.
  • the lower silencing cover 8 is located at the lower part of the auxiliary bearing 6.
  • a lower silencing cavity 81 is formed between the lower silencing cover 8 and the auxiliary bearing 6.
  • the lower silencing cavity 81 is connected to the exhaust port of the lower cylinder 102.
  • the lower silencing cavity 81 is also connected to the lower exhaust port.
  • the gas buffer chamber 1023 is connected, and the high-pressure gas discharged from the lower cylinder 102 passes through the lower silencer chamber 81 to the lower exhaust buffer chamber 1023; the lower exhaust buffer chamber 1023 and the upper exhaust buffer chamber 1013 are connected, and the upper cylinder 7 and the lower cylinder 8 After the discharged high-pressure gas passes through the lower exhaust buffer chamber 1023, it flows into the upper exhaust buffer chamber 1013, and is discharged out of the cylinder from the upper exhaust buffer chamber 1013.
  • the upper silencing chamber 71 and the lower silencing chamber 81 are both composed of multiple interconnected cavities.
  • High-pressure gas enters from one end of the upper silencing chamber 71 or the lower silencing chamber 81 and is discharged from the other end;
  • the lower exhaust buffer chamber 1023 is composed of multiple cavities. It consists of two interconnected sub-exhaust buffer chambers.
  • the sub-exhaust buffer chambers located at both ends are the terminal sub-exhaust buffer chamber 10231 and the front-terminal exhaust buffer chamber 10232.
  • the upper silencer chamber 71 is connected to the terminal sub-exhaust buffer chamber 10231.
  • the lower silencer cavity 81 is connected with the sub-exhaust buffer cavity adjacent to the end sub-exhaust buffer cavity 10231; the front terminal exhaust buffer cavity 10232 is connected with one end of the upper exhaust buffer cavity 1013, and high-pressure gas is exhausted from the upper buffer cavity The other end of the cavity 1013 exits the cylinder.
  • the high-pressure gas in the upper compression chamber 1011 flows to the terminal sub-exhaust buffer chamber 10231 through the upper muffler chamber 71
  • the high-pressure gas in the lower compression chamber 1011 flows to the sub-exhaust gas near the terminal sub-exhaust buffer chamber 10231 through the lower muffler chamber 81.
  • all high-pressure gases are mixed and flow into the front terminal exhaust buffer chamber 10232.
  • both high-pressure gas and low-pressure gas are refrigerants, but they belong to different states of refrigerant.
  • the auxiliary bearing 6 is provided with an oil collection channel, and the bottom of the compressor is provided with an oil pool 9.
  • the upper end of the oil collection channel is connected to the lower exhaust buffer chamber 1023, and the lower end of the oil collection channel is connected to the oil pool 9; the auxiliary bearing 6
  • a filter element accommodation cavity is provided on the filter element accommodation cavity, and a detachable filter element 107 is installed in the filter element accommodation cavity.
  • One end of the filter element 107 penetrates the oil collection channel, and the other end exposes the compressor casing 2, and is fixed to the compressor casing by a nut.
  • the nut is removably fixed on the compressor casing.
  • the removable nut not only fixes the filter element, but also further strengthens the sealing of the oil return port to prevent leakage on the high-pressure side.
  • the filter element can be taken out by removing the nut, and the filter element can be cleaned and replaced.
  • the filter element has a very small gap, which is used for filtering the compressor during installation. , Foreign matter generated during operation, such as iron filings and iron powder, requires frequent cleaning of the filter element.
  • This embodiment also provides a refrigeration/heating system, which can be used for refrigeration or heating, and specifically can be applied to air conditioners, refrigerators and other electrical appliances.
  • the refrigeration/heating system includes an evaporator, a condenser and a compressor, with refrigerant circulating between the compressor, evaporator and condenser; the compressor is any one of the above.
  • the refrigerant may be carbon dioxide refrigerant.

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Abstract

一种气缸、压缩机及制冷/制热系统。气缸包括：缸体外壁（100）；作为压缩腔（210）的缸体内壁（200），设置在缸体外壁（100）内；以及用于消音缓冲的至少一个的空腔（300），空腔（300）设置在缸体外壁（100）和缸体内壁（200）之间，且空腔（300）的至少部分由缸体内壁（200）组成。

Description

气缸、压缩机及制冷/制热系统
本申请要求在2022年3月16日提交至中国专利局、申请号为202210257232.X的中国专利申请以及在2022年5月31日提交至中国专利局、申请号为202210601537.8的中国专利申请的优先权，这些申请的全部内容通过引用结合在本申请中。
技术领域
本发明涉及压缩机领域，特别涉及一种气缸、压缩机及制冷/制热系统。
背景技术
压缩机的吸气、压缩和排气的动作过程中存在需要解决的问题，包括：
(1)会产生较大的吸/排气噪音；
(2)压缩机内部的润滑油会部分与冷媒混合，影响空调系的能效比；
(3)活塞与气缸内壁之前的密封线泄露；
这些问题点都是转子式压缩机迫切需要优化的。
发明内容
本发明的目的在于至少解决现有技术中存在的技术问题之一。为此，本发明提出一种气缸，能有效将压缩机运行时的噪音减小到最低，同时减少压缩过程中的泄露，以提高压缩机的能效比。
本发明实施例提供一种气缸，其包括：
缸体外壁；
作为压缩腔的缸体内壁，设置在所述缸体外壁内；以及
用于消音缓冲的至少一个的空腔，所述空腔设置在所述缸体外壁和所述缸体内壁之间，且所述空腔的至少部分由所述缸体内壁组成。
优选地，所述缸体外壁和所述缸体内壁之间设有一道或多道的分隔加强筋，相邻的所述分隔加强筋与所述缸体外壁的内侧、所述缸体内壁的外侧围成所述 空腔，至少部分的所述分隔加强筋上设有至少一个的通道，所述通道使至少部分的所述空腔连通。
优选地，所述通道包括上通道和下通道，所述上通道相对靠近所述分隔加强筋的顶端设置或设置在所述分隔加强筋的顶端，所述下通道设置在所述分隔加强筋的底端，通过所述上通道与所述下通道之间存在的间距实现气液分离，以使所述上通道用于流通气体，以使所述下通道用于流通液体。
优选地，所述气缸上设有总进气孔和总排气孔，所述缸体内壁设有吸气孔和排气口，所述空腔包括吸气侧腔室和排气侧腔室，气体从所述总进气孔进入，依次流经所述吸气侧腔室后，从所述吸气孔进入所述缸体内壁，经压缩后从所述排气口排出，并流经所述排气侧腔室，然后送至所述总排气孔。
优选地，所述吸气侧腔室设置多个，所述排气侧腔室设置多个，各所述吸气侧腔室相邻设置并通过部分的所述通道连通，各所述排气侧腔室相邻设置并通过另一部分的所述通道连通。
优选地，所述吸气侧腔室与所述排气侧腔室之间设有高低压分隔部，所述高低压分隔部中设置有隔热槽。
优选地，所述空腔的横截面积与所述通道的横截面积之比为：12.5-10:1，所述通道的横截面积与所述排气口的横截面积之比为2-8:1。
优选地，所述气缸包括能够相互连接的上气缸和下气缸，所述上气缸包括上缸体外壁和上缸体内壁，所述下气缸包括下缸体外壁和下缸体内壁，所述上缸体外壁和所述下缸体外壁共同构成所述缸体外壁，所述上缸体内壁和下缸体内壁共同构成所述缸体内壁；
所述吸气侧腔室包括相互连通的上吸气侧腔室和下吸气侧腔室，所述排气侧腔室包括相互连通的上排气侧腔室和下排气侧腔室，所述上吸气侧腔室和所述上排气侧腔室设置在所述上缸体外壁和所述上缸体内壁之间，所述下吸气侧腔室和所述下排气侧腔室设置在下缸体外壁和下缸体内壁之间，气体从所述总进气孔进入，流经所述上吸气侧腔室、所述下吸气侧腔室后，从所述吸气孔进入所述缸体内壁，经压缩后从所述排气口排出，并流经所述上排气侧腔室、所述下排气侧腔室，然后送至所述总排气孔。
本发明实施例还提供一种压缩机，其包括上述任一实施例所述的气缸，所述压缩机还包括油气分离结构，所述油气分离结构具有气液分离腔，所述气液分离腔包括多个所述空腔，所述油气分离结构还包括：
间隙排油结构，其包括芯轴以及与所述芯轴配合的芯轴安装座，所述芯轴与所述芯轴安装座之间形成间隙通道；
过油通道一，其入口与所述气液分离腔连通，从所述气液分离腔导油至所述间隙通道的入口；
过油通道二，其用于连通所述间隙通道的出口与油池，将油从所述间隙通道的出口导入至所述油池；
所述气液分离腔内的油依次穿过所述过油通道一、间隙通道、过油通道二，排出至所述油池；
所述气液分离腔内具有润滑油，所述润滑油通过所述过油通道一、间隙通道、过油通道二，排出至所述气液分离腔外。
优选地，所述压缩机包括：
压缩机壳体，其内设置有驱动组件；
气缸，其设置在所述压缩机壳体内，所述气缸内设置有压缩腔，所述气液分离腔与所述压缩腔连通；
活塞，其设置在所述压缩腔内，并与所述驱动组件传动连接，在所述驱动组件驱动下在所述压缩腔内转动。
优选地，所述芯轴安装座设置有内孔，所述芯轴装配于所述芯轴安装座的内孔中，所述过油通道一和所述过油通道二与所述芯轴错位分布，以能够将所述芯轴限位于所述内孔中。
优选地，所述油气分离结构还包括过滤结构，所述气液分离腔内设有排气孔和排油孔，所述过滤结构设置在所述排油孔内或者设置在所述排油孔与所述过油通道一之间，所述过油通道一的入口与所述过滤结构的出口连通。
优选地，所述间隙通道的宽度为0.001mm-0.020mm。
优选地，所述压缩机还包括：
副轴承，其设置在所述压缩机壳体内，所述过油通道一开设在所述副轴承 上，所述副轴承上开设有与所述间隙排油结构配合的孔；
消音盖，其位于所述副轴承的下侧，所述过油通道二开设在所述消音盖上。
优选地，所述气液分离腔与总排气孔和总进气孔连通；
所述缸体内壁设有吸气口，气体依次经所述总进气孔、气液分离腔、吸气口，进入所述压缩腔内；
所述缸体内壁上设置有排气口，所述压缩腔内被所述活塞压缩后的气体，经所述排气口进入所述气液分离腔，并经由所述气液分离腔从所述总排气孔排出所述气缸外。
本发明实施例还提供一种压缩机，其包括压缩机壳体、驱动组件、主轴承、副轴承、活塞、滑片及上述任一实施例所述的气缸，所述驱动组件、主轴承、副轴承、活塞、滑片均设置于所述压缩机壳体内，所述主轴承和副轴承分别固定在所述气缸的两侧，所述活塞容纳在所述压缩腔内，通过转轴与驱动组件连接，所述驱动组件通过转轴带动所述活塞转动，所述滑片可移动地安装在所述气缸中，并与所述活塞活动配合，分隔所述压缩腔；
所述气缸包括上气缸和下气缸，所述上气缸和下气缸之间设置中隔板，所述上气缸上开设有上压缩腔，所述上气缸的空腔包括上进气缓冲腔和上排气缓冲腔，所述上进气缓冲腔和所述上排气缓冲腔环绕在上压缩腔的周侧；所述下气缸上开设有下压缩腔，所述下气缸的空腔下进气缓冲腔和下排气缓冲腔，所述下进气缓冲腔和所述下排气缓冲腔环绕在下压缩腔的周侧；所述上进气缓冲腔和所述下进气缓冲腔相串联，所述上排气缓冲腔和所述下排气缓冲腔相串联。
优选地，该压缩机还包括上消音盖，所述上消音盖位于所述上气缸的上部，低压气体经过所述上消音盖、上气缸和中隔板共同构成的第一通道进入所述下进气缓冲腔；所述下进气缓冲腔与所述上进气缓冲腔通过第二通道相连通，位于所述下进气缓冲腔中的部分低压气体通过所述第二通道进入至所述上进气缓冲腔内。
优选地，该压缩机还包括上消音盖和下消音盖，所述上消音盖位于所述主轴承的上部，所述上消音盖和所述主轴承之间形成上消音腔，所述上消音腔与所述上气缸的排气口相连通，所述上消音腔还与所述下排气缓冲腔相连通，所 述上气缸排出的高压气体经过所述上消音腔排到所述下排气缓冲腔；
所述下消音盖位于所述副轴承的下部，所述下消音盖和所述副轴承之间形成下消音腔，所述下消音腔和所述下气缸的排气口相连通，所述下消音腔还与所述下排气缓冲腔相连通，所述下气缸排出的高压气体经过所述下消音腔排到所述下排气缓冲腔；
所述下排气缓冲腔和所述上排气缓冲腔相连通，所述上气缸和所述下气缸排出的高压气体经过所述下排气缓冲腔后，流向所述上排气缓冲腔，并从所述上排气缓冲腔排出气缸外。
优选地，所述上消音腔和下消音腔皆由多个相互连通的空腔组成，高压气体从所述上消音腔或者下消音腔的一端进入，并从另一端排出；
所述下排气缓冲腔由多个相互连通的子排气缓冲腔组成，位于两端的子排气缓冲腔分别为末端子排气缓冲腔和前端子排气缓冲腔，所述上消音腔与所述末端子排气缓冲腔相连通，所述下消音腔与邻近所述末端子排气缓冲腔的子排气缓冲腔相连通；所述前端子排气缓冲腔与所述上排气缓冲腔的一端相连通，高压气体从所述上排气缓冲腔的另一端排出气缸外。
本发明实施例还提供一种制冷/制热系统，其包括上述任一实施例所述的压缩机，还包括蒸发器和冷凝器，所述压缩机、蒸发器、冷凝器之间有制冷剂循环流动。
本发明实施例的气缸，通过在缸体外壁和缸体内壁设置空腔，使得压缩机压缩过程中缸体内壁在外力的作用下实现细微的受力跟随变形，能保证压缩机内活塞转子与缸体内壁的密封性能，减少压缩过程中的泄露，又能减少缸体内壁卡死活塞转子的情况发生，同时多个空腔的组合及对应的设置也可以对压缩机的吸排气动作具有消音、扰流等作用，以此将压缩机运行时的噪音减小到最低。
附图说明
通过附图中所示的本发明优选实施例更具体说明，本发明上述及其它目的、特征和优势将变得更加清晰。在全部附图中相同的附图标记指示相同的部分， 且并未刻意按实际尺寸等比例缩放绘制附图，重点在于示出本发明的主旨。
图1为本发明实施例一的结构示意图。
图2为本发明实施例一的正视图。
图3为图2中A-A的剖视图。
图4为实施例二的内部结构示意图。
图5为图4的A处局部放大图。
图6为实施例二的气液分离腔的结构示意图。
图7为实施例二的间隙排油结构的结构示意图。
图8为实施例二的缸体的结构示意图。
图9为实施例二的分隔加强筋及通道处的结构示意图。
图10为实施例三的双气缸的压缩机的剖面图。
图11为实施例三的双气缸的压缩机的进气路线和排油路线图。
图12为图11中AA方向的剖面图。
图13为图11中BB方向的剖面图。
图14为实施例三的双气缸的压缩机的出气路线图。
具体实施方式
为了便于理解本发明，下面将参照相关附图对本进行更全面的描述。
需要说明的是，当一个元件被认为是“连接”另一个元件，它可以是直接连接到另一个元件并与之结合为一体，或者可能同时存在居中元件。本文所使用的术语“安装”、“一端”、“另一端”以及类似的表述只是为了说明的目的。
除非另有定义，本文所使用的所有的技术和科学术语与属于本技术领域的技术人员通常理解的含义相同。本文中说明书中所使用的术语只是为了描述具体的实施例的目的，不是旨在于限制本发明。本文所使用的术语“及/或”包括一个或多个相关的所列项目的任意的和所有的组合。
实施例一
参照图1-图3，本实施例的气缸，应用于压缩机泵体，其作用是与曲轴壳 (主轴承)、副轴承、曲轴和活塞/一体化转轴共同构成一个可承受高压的密封的压缩腔210，通过圆周运动不断的重复吸气、压缩和排气的动作。气缸包括缸体外壁100、缸体内壁200以及至少一个的空腔300。
其中缸体外壁100上设有安装位和安装口，以与压缩机其它零件进行装配，如压缩机的曲轴壳(主轴承)、副轴承消音盖、油控制系统和气态冷媒系统等；其中缸体内壁200作为压缩腔210，与压缩机内的活塞转子/一体化转轴配合，缸体内壁200设置在缸体外壁100内，缸体内壁200设置为柔性结构；其中空腔300用于消音缓冲，空腔300设置在缸体外壁100和缸体内壁200之间，且空腔300的至少部分由缸体内壁200组成，以使缸体内壁200能通过改变空腔300的方式发生变形。通过将缸体内壁200设置为具有一定柔性的结构，通过空腔300的设计结合压缩机压缩过程可确保缸体内壁200在外力的作用下实现细微的受力跟随变形，通过柔性变形即能保证压缩机内活塞转子/一体化转轴与缸体内壁200的密封性能，减少压缩过程中的泄露，又能减少缸体内壁200卡死活塞转子的情况发生，同时多个空腔300的组合及对应的设置也可以对压缩机的吸排气动作具有消音、扰流等作用，以此将压缩机运行时的噪音减小到最低。
具体的实施例中，改变空腔300的方式可为通过挤压使空腔300内凹的方式，也可为由缸体内壁200变形而使空腔300向外延伸的方式，缸体内壁200作为柔性结构具有变形能力，因此缸体内壁200与活塞转子的连接同样能够适应性变化，因为镂空的各空腔300使得缸体内壁200在受到曲轴、活塞/一体化转轴径向压力的情况下会受力让位变形以适应曲轴与活塞旋转时的轨迹轮廓，实现最佳的密封效果。基于柔性结构的变形能力能保证压缩过程中活寒转子与缸体内壁200的配合间隙始终维持在预设的大小，合适的配合间隙能保证密封性能，避免因过大的间隙而导致的高压冷媒泄露、能效比降低，也避免因过小的间隙而导致活塞转子与缸体内壁200卡死。
在本发明的一些实施例中，缸体外壁100和缸体内壁200之间设有一道或多道的分隔加强筋400，相邻的分隔加强筋400与缸体外壁100的内侧、缸体内壁200的外侧围成空腔300。通过分隔加强筋400分别连接缸体外壁100和缸体内壁200，使设置在缸体外壁100和缸体内壁200之间的空腔300分隔成高压空 腔300和低压空腔300，通过多道分隔加强筋400形成多个高压空腔300和/或多个低压空腔300，从而提高使气缸的吸排气过程更加合理，噪音的减弱更加明显。具体的，分隔加强筋400分别连接缸体外壁100和缸体内壁200还可以提高气缸的强度，延长使用寿命。
在本发明的一些实施例中，至少部分的分隔加强筋400上设有至少一个的通道410，通道410使至少部分的空腔300连通。可以理解的是，通道410用于连通相邻的空腔300，如多个高压空腔300或多个低压空腔300的连通，但高压空腔300和低压空腔300之间并不连通，对此吸气侧腔室301与排气侧腔室302之间设有高低压分隔部130，高低压分隔部130中设置有隔热槽131，可有效减少高压高温区与低压低温区之间热量直接热传递，避免直接导致吸气温度过高，该高低压分隔部130可以为加强筋结构，但并不设置通道410在上面，该高低压分隔部130的端面还可以加工成水平，以稳定隔开高压空腔300和低压空腔300，分别实现气缸吸气一侧的液分和消音功能，排气一侧的液分和消音功能。
进一步的，分隔加强筋400通过长度方向的两端分别连接缸体外壁100和缸体内壁200，则通道410的两端开口分别设置于分隔加强筋400的宽度方向两侧，可以理解的是，通道410的两端开口面积大小通常相对小于空腔300的面积，从而迫使流体冷媒的流速发生变化实现扰乱流向和流量，通道410此结构可有效实现消除吸气噪音。具体的，在分隔加强筋400上加工成型缺口，缺口分别连通相邻的空腔300，该缺口即限定为通道410。
在本发明的一些实施例中，具体参照图3，通道410包括上通道411和下通道412，上通道411相对靠近分隔加强筋400的顶端设置或设置在分隔加强筋400的顶端，下通道412设置在分隔加强筋400的底端，通过上通道411与下通道412之间存在的间距实现气液分离，以使上通道411用于流通气体，以使下通道412用于流通液体。可以理解的是，通过在分隔加强筋400上分别设置上通道411和下通道412，可将低温气态冷媒中混合有润滑油进行首次沉降，实现气液分离，提高能效比，同时实现进一步消除排气噪音的效果。进一步的，高压空腔300和低压空腔300均分别设有上通道411和下通道412，实现低压侧的一次气液分离，高压侧一次气液分离，气液分离效果显著。
进一步的，由于下通道412设置在分隔加强筋400的底端，通道410用于连通多个高压空腔300或多个低压空腔300，因此下通道412用于连通高压空腔300的底部，下通道412用于连通低压空腔300的底部，沉降下来的油会平均分配到各个空腔300，设置相应的润滑油流回通道410可为后续滤油和回流提供便捷，使得压缩机的性能更好。
在本发明的一些实施例中，气缸上设有总进气孔110和总排气孔120，缸体内壁200设有吸气孔220和排气口230，腔室包括吸气侧腔室301和排气侧腔室302，气体从总进气孔110进入，依次流经吸气侧腔室301后，从吸气孔220进入缸体内壁200，经压缩后从排气口230排出，并流经排气侧腔室302，然后送至总排气孔120。具体的，吸气侧腔室301设置多个，排气侧腔室302设置多个，各吸气侧腔室301相邻设置并通过部分的通道410连通，各排气侧腔室302相邻设置并通过另一部分的通道410连通。通过一侧集成的设计，可以有效实现气液分离和消除排气噪音，降低压缩腔210进行排气时产生的噪音。进一步的，气缸上的总进气孔110和总排气孔120除了设置于气缸外壁100上，还可根据压缩机的结构或其他需求将总进气孔110和总排气孔120调整到设置于曲轴壳(主轴承)或副轴承上，保证与对应的高/低压的空腔300对应联通，可实现同样的功能和效果。
在本发明的一些实施例中，缸体外壁100为中间凹陷、外周凸起的结构，当气缸与压缩机外壁装配时，缸体外壁100的凸起结构与压缩机直身外壳相配合，此时缸体外壁100的中间凹陷位与压缩机直身外壳之间形成空腔。此空腔能减小气缸与压缩机壳体间金属直接接触面积，从而形成隔热断桥，减小了压缩机运行时泵体与外壳之间热量的传递，避免压缩机壳体过热。在另一些实施例中，当气缸外壁100为直身圆柱形时，可将与气缸相配合的上下轴承的外径设计为大于气缸外径，以中心为基准装配完成后，气缸外壁100在径向低于上下轴承的外径，最后装入壳体后同样可以形成隔热空腔。
在本发明的一些实施例中，气缸包括能够通过中隔板相互连接的上气缸和下气缸，上气缸包括上缸体外壁和上缸体内壁，下气缸包括下缸体外壁和下缸体内壁，上缸体外壁和下缸体外壁共同构成缸体外壁100，上缸体内壁和下缸体 内壁共同构成缸体内壁200，通过组合的方式能提高压缩机排量、方便加工，同时通过延长流通的长度，实现充分减少吸气噪音，分离沉降气态冷媒中混合的润滑油与未完全气化的液态冷淡的效果，避免液态物质直接进入压缩腔210造成液击。
具体的，吸气侧腔室301包括相互连通的上吸气侧腔室和下吸气侧腔室，排气侧腔室302包括相互连通的上排气侧腔室和下排气侧腔室，上吸气侧腔室和上排气侧腔室设置在上缸体外壁和上缸体内壁之间，下吸气侧腔室和下排气侧腔室设置在下缸体外壁和下缸体内壁之间，气体从总进气孔110进入，流经上吸气侧腔室、下吸气侧腔室后，从吸气孔220进入缸体内壁200，经压缩后从排气口230排出，并流经上排气侧腔室、下排气侧腔室，然后送至总排气孔120。设置多个吸气侧腔室301和多个排气侧腔室302串联，可使消音和油气分离的效果达到理想设定效果。其中通过延长冷媒的流通路径，增加流向转变次数，能更进一步利于液态冷媒的完全气化和润滑油的沉降，结合图2的气态冷媒流向，可根据具体情况分别设置上气缸和下气缸，均可利于消音和油气分离。其他实施例中，还可以在相邻的吸气侧腔室301之间布置消音、隔热和油气分离的腔室等，同理于排气侧腔室302，例如可在相邻的排气侧腔室302之间外接压缩机的消音盖消音腔室等，进一步提高消音效果。
进一步的实施例中，吸气侧腔室301和排气侧腔室302可针对性分别设置多个，在另一些实施例中，吸气侧腔室至少设置两个，排气侧腔室至少设置两个，上气缸中各吸气侧腔室串联，各排气侧腔室串联，下气缸同理，以充分消音和气液分离。
参照图1-图3，本实施例还提供一种压缩机，压缩机可以是转子式压缩机，压缩机包括上述实施例的气缸，能实现主动降低吸排气器噪音、主动将润滑油与气态冷媒分离，并可有效提升压缩机内活塞转子与缸体内壁200密封性，以此将压缩机运行时的噪音减小到最低，同时减少压缩机过程中的泄露，使压缩机的能效比\COP值相对于现有技术水平提高一定程度。
实施例二
如图4至图7所示，本实施例提供了一种油气分离结构，该结构设置在压缩机的排气通道上，用于分离压缩机内制冷剂与润滑油，至少包括气液分离腔1、过油通道一5、间隙排油结构和过油通道二6；
过油通道一5的入口与所述气液分离腔1连通，从所述气液分离腔1导油至所述间隙通道的入口；
过油通道二6用于连通所述间隙通道的出口与油池7，将油从所述间隙通道的出口导入至所述油池7；
气液分离腔1用于分离制冷剂和润滑油，如图6所示，气液分离腔为隔断迷宫式结构，能够使制冷剂与润滑油最大限度分离并利用重力分层；
气液分离腔1与油池7之间的压力差以及间隙排油结构可使得润滑油从高温高压的气液分离腔1依次穿过过油通道一5、间隙通道、过油通道二6，进入低压的油池7内；
间隙排油机构包括芯轴安装座4和芯轴3，芯轴安装座4中心处开设有与芯轴3间隙配合的内孔，且为便于间隙进油和排油，此内孔顶部为锥形扩口状(如图7所示)，内孔顶部为锥形扩口状也便于将芯轴3安装至芯轴安装座4内，为将芯轴3限制与芯轴安装座4内，防止其在压缩机工作过程时从芯轴安装座4内脱落，过油通道一5和过油通道二6均与所述芯轴3错位分布形成抵挡位，即过油通道一5和过油通道二6与芯轴3不同轴；
在压缩机行业中根据温度调节系统需求使用工况的不同，会选用不同的制冷剂，例如常见的R22、R134a等，不同的制冷剂需要选配不同的润滑油并将其预封装在压缩机壳体11内，不同的润滑油其粘度、密度、与制冷剂的互溶解性、流动性等特性也存在较大差异，为满足需求，芯轴3和芯轴安装座4的内孔之间的间隙一般为0.001mm-0.010mm，本实施例以68#润滑油为例进行说明；使用68#号润滑油时，芯轴3与芯轴安装座4内孔的配合间隙为0.002mm，确认需求为0.002mm间隙后，将经过铰桁磨削过内孔的芯轴安装座4和精磨外圆的芯轴3测量尺寸并选配出0.002mm间隙后，一并装入到压缩机中(如图5所示)，结合不同工况的压缩机和对应的润滑油的需求，可在装配压缩机时人为的控制此排油间隙以满足使需求；
本实施例的间隙排油结构是一个能够独立实现排油功能并有效防止压缩机高低压串气的结构，其安装位置不局限于压缩机的曲轴壳、压缩机壳体11、排气管道、气缸12、副轴承盖13、消音盖14或温度调节器上；
上述油池7设置在压缩机壳体11中且位于所述气缸12的下方，所述压缩机还包括供油装置，所述供油装置与所述油池7连接，用于将所述油池7的油输送至所述气缸12中；供油装置也设置在所述压缩机壳体11中且位于所述气缸12的下方。
在上述实施例的基础上，如图5所示，本实施例提供一种用于油气分离结构的过滤结构，过滤结构用于过滤润滑油中的杂质，使得间隙中的油路循环更顺畅；
气液分离腔1内设有排气孔和排油孔2，所述过滤结构设置在所述排油孔2内或者设置在所述排油孔2与所述过油通道一5之间；
过滤结构为过滤芯8，过滤芯8为高密度微孔过滤结构，其上的过滤孔隙的尺寸设计为小于0.005mm，从而能够过滤沉降后的润滑油中的杂质、异物；
过油通道一5的上开口位于过滤结构的下开口处，即所述过油通道一5的入口与所述过滤结构的出口连通，因此，过滤后的液态润滑油会经过过滤结构和过油通道一5导入到间隙排油结构处；
由于压缩机在工作时会产生金属磨损，形成一些金属碎屑，这些金属碎屑会堵塞间隙排油结构，为提高过滤结构的过滤效果，在过滤结构上增加一磁性块9，应用于过滤芯8上时，磁性块9的形状可以为T形、圆柱体或倒凹字形的强磁铁，实际使用中其形状不受限制，可根据安装空间等实际情况来选择，磁性块9设置在过滤芯8顶部能够吸附润滑油中的金属杂质，防止金属杂质堵塞过滤芯8，另外，由于过滤芯8具有一定长度，磁性块9设置于过滤芯8的顶部时的吸附能力很难覆盖过滤芯8整体，且金属杂质易堆积在润滑油的下层部分，因此过滤芯8与气液分离腔1的腔底齐平的位置处可加设一磁性环(图中未画出)，这样可提高吸附效果，延长过滤芯8的使用寿命；
过滤芯8的形状也不局限于圆筒状，也可为方筒或截面为多边形的其他形状。
本实施例还提供一种压缩机，包括上述实施例中的油气分离结构。该压缩机还包括压缩机壳体11以及设置在压缩机壳体11内的驱动组件15、气缸12、副轴承13、活塞以及消音盖14(此处仅指出了与油气分离结构相连的压缩机部分零件，)，油气分离结构应用于此压缩机上时，气液分离腔1可贯穿设于气缸12上，副轴承13的顶面为气液分离腔1的腔底；
活塞设置在所述压缩腔21内，并与所述驱动组件15传动连接，在所述驱动组件15驱动下在所述压缩腔21内转动；
过油通道一5开设在副轴承13上；过油通道二6开设在消音盖14上；副轴承13上开设有容纳间隙排油结构的孔，副轴承13与芯轴安装座4的接触面密封连接，以确保不漏气，即可满足润滑油以间隙排油结构的孔为通道从高压区排入低压区，又可确保高低压之间不直接连通而串气；
如图6所示，副轴承13上开设有与过滤芯8配合的安装孔(即排油孔2)，气缸12上开设有一与过滤芯8外表面配合的弧形凹槽，此弧形凹槽用于限制过滤芯8的位置，在压缩机处于倒置、倾斜、转动的情况下，过滤芯8仍不会脱离预装位置。
如图8和图9所示，本实施例还提供一种气缸，所述气缸12包括缸体外壁122和缸体内壁121，所述缸体内壁121中形成所述压缩腔21，所述气液分离腔1位于所述缸体外壁122和缸体内壁121之间。
其中缸体外壁122上设有安装位和安装口，以与压缩机其它零件进行装配，如压缩机的曲轴壳(主轴承)、副轴承13、消音盖14、油控制系统和气态冷媒系统等；压缩腔21与压缩机内的活塞转子/一体化转轴配合，缸体内壁21设置为柔性结构。
气液分离腔1与总排气孔23和总进气孔24连通。
缸体内壁121设有吸气口25，气体依次经所述总进气孔24、气液分离腔1、吸气口25，进入所述压缩腔21内。
缸体内壁121上设置有排气口22，压缩腔21内被所述活塞压缩后的气体，经排气口22进入所述气液分离腔1，并经由气液分离腔1从总排气孔23排出所述气缸12外。
总排气孔23和总进气孔24不仅可以设置在所述气缸12上还可以设置在位于气缸12上侧的上轴承或位于气缸12下侧的下轴承上。
气液分离腔1包括多个起到消音缓冲作用的空腔26，空腔26的部分由柔性的缸体内壁121组成，以使缸体内壁121能通过改变空腔26的方式发生变形，通过将缸体内壁121设置为具有一定柔性的结构，通过空腔26的设计结合压缩机压缩过程，可确保缸体内壁121在外力的作用下实现细微的受力跟随变形，通过柔性变形既能保证压缩机内活塞转子/一体化转轴与缸体内壁121的密封性能，减少压缩过程中的泄露，又能减少缸体内壁121卡死活塞转子的情况发生，同时多个空腔26的组合及对应的设置也可以对压缩机的吸排气动作具有消音、扰流等作用，以此将压缩机运行时的噪音减小到最低。
一部分所述空腔26组成吸气侧腔室31，另一部分所述空腔26组成排气侧腔室32，吸气侧腔室所包含的多个空腔26中的相邻两个空腔26通过设于所述缸体外壁122和所述缸体内壁121之间的分隔加强筋27分隔，排气侧腔室32所包含的多个空腔26中的相邻两个空腔26也通过设于所述缸体外壁122和所述缸体内壁121之间的分隔加强筋27分隔，所述分隔加强筋27上设有使相邻空腔26连通的通道28。
分隔加强筋27连接缸体外壁122和缸体内壁121，还可以提高气缸12的强度，延长使用寿命。
通过分隔加强筋27将两组空腔26分为高压空腔(排气侧腔室32)和低压空腔(吸气侧腔室)，高压空腔和低压空腔之间设置有隔热槽29，可有效减少高压高温区与低压低温区之间热量直接热传递，避免直接导致吸气温度过高。
所述吸气侧腔室31与总进气孔24连通，所述排气侧腔室32与所述总排气孔23连通，气体从总进气孔24进入，流经所述吸气侧腔室31，从所述吸气口25进入所述压缩腔21，经活塞压缩后从所述排气口22排出，并流经所述排气侧腔室32，然后从总排气孔23排出。
如图9所示，所述通道28包括上通道281和下通道282，所述上通道281相对靠近所述分隔加强筋27的顶端设置或设置在所述分隔加强筋27的顶端，所述下通道282设置在所述分隔加强筋27的底端，所述上通道281与所述下通 道282之间存在的间距实现气液分离，以使所述上通道281用于流通气体，以使所述下通道282用于流通液体；通过在分隔加强筋27上分别设置上通道281和下通道282，可将低温气态冷媒中混合有润滑油进行首次沉降，实现气液分离，提高能效比，同时实现进一步消除排气噪音的效果；进一步的，高压空腔和低压空腔均分别设有上通道281和下通道282，实现低压侧的一次气液分离，高压侧一次气液分离，气液分离效果显著。
多个空腔26、通道28以及分隔加强筋27组成一迷宫型结构。
通道28的两端开口分别设置于分隔加强筋27的宽度方向两侧，可以理解的是，通道28的两端开口面积大小通常相对小于空腔26的面积，从而迫使流体冷媒的流速发生变化实现扰乱流向和流量，通道28此结构可有效实现消除吸气噪音；具体的，在分隔加强筋27上加工成型缺口，缺口分别连通相邻的空腔26，该缺口即限定为通道28。
进一步的，所述空腔26的横截面积＞所述通道28的横街面积＞所述排气口22的横截面积，当上述比值过小时会使得气液分离效果差，若比值过大，则压缩气体排出不畅通，压缩效率低；优选的，所述空腔26的横截面积与所述通道的横截面积之比为：12.5～10:1，所述通道的横截面积与所述排气口22的横截面积之比为2～8:1。
缸体外壁122为中间凹陷、外周凸起的结构，当气缸12与压缩机外壁装配时，缸体外壁122的凸起结构与压缩机直身外壳相配合，此时缸体外壁122的中间凹陷位与压缩机直身外壳之间形成空腔；此空腔能减小气缸12与压缩机壳体间金属直接接触面积，从而形成隔热断桥，减小了压缩机运行时泵体与外壳之间热量的传递，避免压缩机壳体过热；另外，当缸体外壁122为直身圆柱形时，可将与气缸12相配合的上下轴承的外径设计为大于气缸外径，以中心为基准装配完成后，气缸外壁122在径向低于上下轴承的外径，最后装入壳体后同样可以形成隔热空腔。
在本实施例的一些实施例中，气缸包括能够通过中隔板相互连接的上气缸和下气缸，上气缸包括上缸体外壁和上缸体内壁，下气缸包括下缸体外壁和下缸体内壁，上缸体外壁和下缸体外壁共同构成缸体外壁122，上缸体内壁和下缸 体内壁共同构成缸体内壁121，通过组合的方式能提高压缩机排量、方便加工，同时通过延长流通的长度，实现充分减少吸气噪音，分离沉降气态冷媒中混合的润滑油与未完全气化的液态冷淡的效果，避免液态物质直接进入压缩腔21造成液击。
进一步的，吸气侧腔室31包括相互连通的上吸气侧腔室和下吸气侧腔室，排气侧腔室32包括相互连通的上排气侧腔室和下排气侧腔室，上吸气侧腔室和上排气侧腔室设置在上缸体外壁和上缸体内壁之间，下吸气侧腔室和下排气侧腔室设置在下缸体外壁和下缸体内壁之间，气体从总进气孔24进入，流经上吸气侧腔室、下吸气侧腔室后，从吸气口25进入缸体内壁121，经压缩后从排气口22排出，并流经上排气侧腔室、下排气侧腔室，然后送至总排气孔23；吸气侧腔室31的多个空腔26和排气侧腔室32的多个空腔26均设置串联，可使消音和油气分离的效果达到理想设定效果；其中通过延长冷媒的流通路径，增加流向转变次数，能更进一步利于液态冷媒的完全气化和润滑油的沉降，结合图8的气态冷媒流向，可根据具体情况分别设置上气缸和下气缸，均可利于消音和油气分离。
在上述实施例的基础上，本实施例还提供一种制冷制热系统，制冷制热系统包括蒸发器和冷凝器，所述压缩机、蒸发器、冷凝器之间有制冷剂循环流动；制冷剂可为二氧化碳制冷剂，制冷制热系统中的压缩机采用上述实施例中的压缩机，在工作时，能够使得制冷剂与润滑油分离的更彻底，提高制冷效果，防止润滑油进入制冷区影响制冷效果，也提高润滑油回流效果，使得压缩机内部零件充分润滑，使用寿命更久。
实施例三
实施例三是将上述实施例一的气缸应用于双气缸的压缩机。
参考图12-16，本实施例还提供一种压缩机，包括压缩机壳体、驱动组件、主轴承、副轴承、活塞、滑片及上述实施例的气缸，驱动组件、主轴承、副轴承、活塞、滑片均设置于压缩机壳体内，主轴承和副轴承分别固定在气缸的两侧，将压缩腔封闭，活塞容纳在压缩腔内，通过转轴与驱动组件连接，驱动组 件通过转轴带动活塞转动，滑片可移动地安装在气缸中，并与活塞活动配合，分隔压缩腔。
气缸包括上气缸101和下气缸101，上气缸101和下气缸102之间设置中隔板103。上气缸101和下气缸101中分别设置有上活塞和下活塞以及分别与上活塞和下活塞配合的上滑片和下滑片，上活塞和下活塞通过同一转轴与驱动组件连接，上活塞和下活塞的偏心部错位设置。
上气缸101上开设有上压缩腔1011、上进气缓冲腔1012和上排气缓冲腔1013。上进气缓冲腔1012和上排气缓冲腔1013构成上气缸101的空腔，且位于上气缸101的缸体外壁和缸体内壁之间，起到消音和缓冲的作用，空腔的至少部分由缸体内壁组成。上进气缓冲腔1012和上排气缓冲腔1013环绕在上压缩腔1011的周侧，上进气缓冲腔1012占据的弧度小于上排气缓冲腔1013的弧度；即上进气缓冲腔1012的两端与上压缩腔1011中心点形成的夹角小于上排气缓冲腔1013的两端与上压缩腔1011中心点形成的夹角。下气缸102上开设有下压缩腔1021、下进气缓冲腔1022和下排气缓冲腔1023。下进气缓冲腔1022和下排气缓冲腔1023构成下气缸102上的空腔，且位于下气缸102的缸体外壁和所述缸体内壁之间，起到消音和缓冲的作用，下气缸102的空腔的至少部分由下气缸102的缸体内壁组成。下进气缓冲腔1022和下排气缓冲腔1023环绕在下压缩腔1021的周侧，下进气缓冲腔1022占据的弧度小于下排气缓冲腔1023的弧度；即下进气缓冲腔1022的两端与下压缩腔1021中心点形成的夹角小于下排气缓冲腔1023的两端与上压缩腔1021中心点形成的夹角。
上进气缓冲腔1012和下进气缓冲腔1022相串联，上排气缓冲腔1013和下排气缓冲腔1023相串联，低压气体需要经过上进气缓冲腔1012和下进气缓冲腔1022后才能进入上压缩腔1011，延长了低压气体的流通路径和流向转变次数，更进一步利于液态冷媒完全气化和润滑油的沉降，且消音效果也更好；高压气体需要通过下排气缓冲腔1023和上排气缓冲腔1013后排出气缸外，缓冲时间更长，消音效果和气液分离效果都更好，其作用与进气缓冲腔的相同，此处不再赘述。
该压缩机还可以包括上消音盖7，上消音盖7位于上气缸101的上部，低压 气体经过上消音盖7、上气缸101和中隔板103共同构成的第一通道104进入下进气缓冲腔1022，在上消音盖7、上气缸101和中隔板103上都开设通孔，这些通孔相互连通，形成第一通道104。下进气缓冲腔1022与上进气缓冲腔1012通过第二通道105相连通，位于下进气缓冲腔1022中的部分低压气体通过第二通道105进入至上进气缓冲腔1012内。在上气缸101、中隔板103和下气缸102上设置通孔，通孔相互连通，且将下进气缓冲腔1022与上进气缓冲腔1012连通。该压缩机还包括进气口凸环106，进气口凸环106设置于第一通道104的进气端，且进气口凸环106凸出于其周侧的结构，可阻止腔内异物、液态润滑油等直接进入气缸吸入口。低压气体通过压缩机进气口21进入压缩机内，经过第一通道104后进入下进气缓冲腔1022，部分低压气体经过下进气缓冲腔1022后进入下压缩腔1021，还有部分低压气体从下进气缓冲腔1022通过第二通道105进入上进气缓冲腔1012，再进入上压缩腔1011。
该压缩机还可以包括上消音盖7和下消音盖8，上消音盖7位于主轴承5的上部，上消音盖7和主轴承5之间形成上消音腔71，上消音腔71与上气缸101的排气口相连通，上消音腔71还与下排气缓冲腔1023相连通，上气缸7排出的高压气体经过上消音腔71到下排气缓冲腔1023。下消音盖8位于副轴承6的下部，下消音盖8和副轴承6之间形成下消音腔81，下消音腔81和下气缸102的排气口相连通，下消音腔81还与下排气缓冲腔1023相连通，下气缸102排出的高压气体经过下消音腔81到下排气缓冲腔1023；下排气缓冲腔1023和上排气缓冲腔1013相连通，上气缸7和下气缸8排出的高压气体经过下排气缓冲腔1023后，流向上排气缓冲腔1013，并从上排气缓冲腔1013排出气缸外。上消音腔71和下消音腔81皆由多个相互连通的空腔组成，高压气体从上消音腔71或者下消音腔81的一端进入，并从另一端排出；下排气缓冲腔1023由多个相互连通的子排气缓冲腔组成，位于两端的子排气缓冲腔分别为末端子排气缓冲腔10231和前端子排气缓冲腔10232，上消音腔71与末端子排气缓冲腔10231相连通，下消音腔81与邻近末端子排气缓冲腔10231的子排气缓冲腔相连通；前端子排气缓冲腔10232与上排气缓冲腔1013的一端相连通，高压气体从上排气缓冲腔1013的另一端排出气缸外。具体地，上压缩腔1011的高压气体经过 上消音腔71流向末端子排气缓冲腔10231，下压缩腔1011中的高压气体经过下消音腔81流向末端子排气缓冲腔10231临近的子排气缓冲腔，所有高压气体混合后流向前端子排气缓冲腔10232，再从前端子排气缓冲腔10232流向上排气缓冲腔1013一端，再从上排气缓冲腔1013的另一端排出该压缩机。同样可以延长冷媒流通路径、增加流向转变次数，更进一步利于液态冷媒完全气化和润滑油的沉降，需要说明的是，高压气体和低压气体都是冷媒，只是属于不同状态的冷媒。
副轴承6上开设有集油通道，该压缩机底部设置有油池9，集油通道的上端与下排气缓冲腔1023相连通，集油通道的下端与油池9相连通；副轴承6上开设有滤芯容置腔，滤芯容置腔内安装有可拆卸的滤芯107，滤芯107的一端贯穿集油通道，另一端露出压缩机壳体2，并由螺帽固定在压缩机壳体上，螺帽可拆卸地固定在压缩机壳体上。可拆卸的螺帽既固定虑芯，又进一步加强回油口密封，防止高压侧泄露，拆掉螺帽可以取出滤芯，可清理更换滤芯，滤芯具有极微的间隙，用于过滤压缩机在装机、运行过程中所产生的异物，如铁屑、铁粉，需要经常清理更好滤芯。
本实施例还提供一种制冷/制热系统，该制冷/制热系统可以用于制冷或者制热，具体来说可以应用于空调、冰箱等电器中。制冷/制热系统包括蒸发器、冷凝器和压缩机，压缩机、蒸发器、冷凝器之间有制冷剂循环流动；压缩机为上述任一项的压缩机。制冷剂可以为二氧化碳制冷剂。
以上实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上实施例仅表达了发明的具体实施方式，其描述较为具体和详细，但并不能因此而理解为对发明专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本发明构思的前提下，还可以做出若干变形和改进，这些都属于本发明的保护范围。因此，本发明专利的保护范围应以所附权利要求为准。

Claims (20)

  1. 一种气缸，其特征在于，包括：
    缸体外壁；
    作为压缩腔的缸体内壁，设置在所述缸体外壁内；以及
    用于消音缓冲的至少一个的空腔，所述空腔设置在所述缸体外壁和所述缸体内壁之间，且所述空腔的至少部分由所述缸体内壁组成。
  2. 根据权利要求1所述的气缸，其特征在于：所述缸体外壁和所述缸体内壁之间设有一道或多道的分隔加强筋，相邻的所述分隔加强筋与所述缸体外壁的内侧、所述缸体内壁的外侧围成所述空腔，至少部分的所述分隔加强筋上设有至少一个的通道，所述通道使至少部分的所述空腔连通。
  3. 根据权利要求2所述的气缸，其特征在于：所述通道包括上通道和下通道，所述上通道相对靠近所述分隔加强筋的顶端设置或设置在所述分隔加强筋的顶端，所述下通道设置在所述分隔加强筋的底端，通过所述上通道与所述下通道之间存在的间距实现气液分离，以使所述上通道用于流通气体，以使所述下通道用于流通液体。
  4. 根据权利要求3所述的气缸，其特征在于：所述气缸上设有总进气孔和总排气孔，所述缸体内壁设有吸气孔和排气口，所述空腔包括吸气侧腔室和排气侧腔室，气体从所述总进气孔进入，依次流经所述吸气侧腔室后，从所述吸气孔进入所述缸体内壁，经压缩后从所述排气口排出，并流经所述排气侧腔室，然后送至所述总排气孔。
  5. 根据权利要求4所述的气缸，其特征在于：所述吸气侧腔室设置多个，所述排气侧腔室设置多个，各所述吸气侧腔室相邻设置并通过部分的所述通道连通，各所述排气侧腔室相邻设置并通过另一部分的所述通道连通。
  6. 根据权利要求5所述的气缸，其特征在于：所述吸气侧腔室与所述排气侧腔室之间设有高低压分隔部，所述高低压分隔部中设置有隔热槽。
  7. 根据权利要求4所述的气缸，其特征在于：所述空腔的横截面积与所述通道的横截面积之比为：12.5-10:1，所述通道的横截面积与所述排气口的横截 面积之比为2-8:1。
  8. 根据权利要求4所述的气缸，其特征在于：所述气缸包括能够相互连接的上气缸和下气缸，所述上气缸包括上缸体外壁和上缸体内壁，所述下气缸包括下缸体外壁和下缸体内壁，所述上缸体外壁和所述下缸体外壁共同构成所述缸体外壁，所述上缸体内壁和下缸体内壁共同构成所述缸体内壁；
    所述吸气侧腔室包括相互连通的上吸气侧腔室和下吸气侧腔室，所述排气侧腔室包括相互连通的上排气侧腔室和下排气侧腔室，所述上吸气侧腔室和所述上排气侧腔室设置在所述上缸体外壁和所述上缸体内壁之间，所述下吸气侧腔室和所述下排气侧腔室设置在下缸体外壁和下缸体内壁之间，气体从所述总进气孔进入，流经所述上吸气侧腔室、所述下吸气侧腔室后，从所述吸气孔进入所述缸体内壁，经压缩后从所述排气口排出，并流经所述上排气侧腔室、所述下排气侧腔室，然后送至所述总排气孔。
  9. 一种压缩机，其特征在于，包括权利要求1-8任一项所述的气缸，所述压缩机还包括油气分离结构，所述油气分离结构具有气液分离腔，所述气液分离腔包括多个所述空腔，所述油气分离结构还包括：
    间隙排油结构，其包括芯轴以及与所述芯轴配合的芯轴安装座，所述芯轴与所述芯轴安装座之间形成间隙通道；
    过油通道一，其入口与所述气液分离腔连通，从所述气液分离腔导油至所述间隙通道的入口；
    过油通道二，其用于连通所述间隙通道的出口与油池，将油从所述间隙通道的出口导入至所述油池；
    所述气液分离腔内的油依次穿过所述过油通道一、间隙通道、过油通道二，排出至所述油池；
    所述气液分离腔内具有润滑油，所述润滑油通过所述过油通道一、间隙通道、过油通道二，排出至所述气液分离腔外。
  10. 根据权利要求9所述的压缩机，其特征在于：所述压缩机包括：
    压缩机壳体，其内设置有驱动组件；
    气缸，其设置在所述压缩机壳体内，所述气缸内设置有压缩腔，所述气液分离腔与所述压缩腔连通；
    活塞，其设置在所述压缩腔内，并与所述驱动组件传动连接，在所述驱动组件驱动下在所述压缩腔内转动。
  11. 根据权利要求9所述的压缩机，其特征在于：所述芯轴安装座设置有内孔，所述芯轴装配于所述芯轴安装座的内孔中，所述过油通道一和所述过油通道二与所述芯轴错位分布，以能够将所述芯轴限位于所述内孔中。
  12. 根据权利要求9所述的压缩机，其特征在于：所述油气分离结构还包括过滤结构，所述气液分离腔内设有排气孔和排油孔，所述过滤结构设置在所述排油孔内或者设置在所述排油孔与所述过油通道一之间，所述过油通道一的入口与所述过滤结构的出口连通。
  13. 如权利要求9所述的压缩机，其特征在于，所述间隙通道的宽度为0.001mm-0.020mm。
  14. 如权利要求9所述的压缩机，其特征在于，所述压缩机还包括：
    副轴承，其设置在所述压缩机壳体内，所述过油通道一开设在所述副轴承上，所述副轴承上开设有与所述间隙排油结构配合的孔；
    消音盖，其位于所述副轴承的下侧，所述过油通道二开设在所述消音盖上。
  15. 根据权利要求9所述的压缩机，其特征在于：
    所述气液分离腔与总排气孔和总进气孔连通；
    所述缸体内壁设有吸气口，气体依次经所述总进气孔、气液分离腔、吸气口，进入所述压缩腔内；
    所述缸体内壁上设置有排气口，所述压缩腔内被所述活塞压缩后的气体，经所述排气口进入所述气液分离腔，并经由所述气液分离腔从所述总排气孔排出所述气缸外。
  16. 一种压缩机，其特征在于，包括压缩机壳体、驱动组件、主轴承、副轴承、活塞、滑片及权利要求1-7任一项所述的气缸，所述驱动组件、主轴承、 副轴承、活塞、滑片均设置于所述压缩机壳体内，所述主轴承和副轴承分别固定在所述气缸的两侧，所述活塞容纳在所述压缩腔内，通过转轴与驱动组件连接，所述驱动组件通过转轴带动所述活塞转动，所述滑片可移动地安装在所述气缸中，并与所述活塞活动配合，分隔所述压缩腔；
    所述气缸包括上气缸和下气缸，所述上气缸和下气缸之间设置中隔板，所述上气缸上开设有上压缩腔，所述上气缸的空腔包括上进气缓冲腔和上排气缓冲腔，所述上进气缓冲腔和所述上排气缓冲腔环绕在上压缩腔的周侧；所述下气缸上开设有下压缩腔，所述下气缸的空腔下进气缓冲腔和下排气缓冲腔，所述下进气缓冲腔和所述下排气缓冲腔环绕在下压缩腔的周侧；所述上进气缓冲腔和所述下进气缓冲腔相串联，所述上排气缓冲腔和所述下排气缓冲腔相串联。
  17. 根据权利要求16所述的压缩机，其特征在于，该压缩机还包括上消音盖，所述上消音盖位于所述上气缸的上部，低压气体经过所述上消音盖、上气缸和中隔板共同构成的第一通道进入所述下进气缓冲腔；所述下进气缓冲腔与所述上进气缓冲腔通过第二通道相连通，位于所述下进气缓冲腔中的部分低压气体通过所述第二通道进入至所述上进气缓冲腔内。
  18. 根据权利要求16所述的压缩机，其特征在于，该压缩机还包括上消音盖和下消音盖，所述上消音盖位于所述主轴承的上部，所述上消音盖和所述主轴承之间形成上消音腔，所述上消音腔与所述上气缸的排气口相连通，所述上消音腔还与所述下排气缓冲腔相连通，所述上气缸排出的高压气体经过所述上消音腔排到所述下排气缓冲腔；
    所述下消音盖位于所述副轴承的下部，所述下消音盖和所述副轴承之间形成下消音腔，所述下消音腔和所述下气缸的排气口相连通，所述下消音腔还与所述下排气缓冲腔相连通，所述下气缸排出的高压气体经过所述下消音腔排到所述下排气缓冲腔；
    所述下排气缓冲腔和所述上排气缓冲腔相连通，所述上气缸和所述下气缸排出的高压气体经过所述下排气缓冲腔后，流向所述上排气缓冲腔，并从所述 上排气缓冲腔排出气缸外。
  19. 根据权利要求18所述的压缩机，其特征在于，所述上消音腔和下消音腔皆由多个相互连通的空腔组成，高压气体从所述上消音腔或者下消音腔的一端进入，并从另一端排出；
    所述下排气缓冲腔由多个相互连通的子排气缓冲腔组成，位于两端的子排气缓冲腔分别为末端子排气缓冲腔和前端子排气缓冲腔，所述上消音腔与所述末端子排气缓冲腔相连通，所述下消音腔与邻近所述末端子排气缓冲腔的子排气缓冲腔相连通；所述前端子排气缓冲腔与所述上排气缓冲腔的一端相连通，高压气体从所述上排气缓冲腔的另一端排出气缸外。
  20. 一种制冷/制热系统，其特征在于，包括权利要求9-19任一项所述的压缩机，还包括蒸发器和冷凝器，所述压缩机、蒸发器、冷凝器之间有制冷剂循环流动。
PCT/CN2022/107017 2022-03-16 2022-07-21 气缸、压缩机及制冷/制热系统 WO2023173638A1 (zh)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104929934A (zh) * 2015-05-27 2015-09-23 广东美芝制冷设备有限公司 旋转式压缩机
CN204729308U (zh) * 2015-05-27 2015-10-28 广东美芝制冷设备有限公司 旋转式压缩机
CN204900246U (zh) * 2015-07-21 2015-12-23 广东美芝制冷设备有限公司 气缸及具有其的旋转式压缩机的压缩组件
CN207777174U (zh) * 2017-12-28 2018-08-28 广东美芝制冷设备有限公司 低背压压缩机
CN111648962A (zh) * 2020-07-07 2020-09-11 苏州英华特涡旋技术股份有限公司 一种卧式涡旋压缩机的油循环结构

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104929934A (zh) * 2015-05-27 2015-09-23 广东美芝制冷设备有限公司 旋转式压缩机
CN204729308U (zh) * 2015-05-27 2015-10-28 广东美芝制冷设备有限公司 旋转式压缩机
CN204900246U (zh) * 2015-07-21 2015-12-23 广东美芝制冷设备有限公司 气缸及具有其的旋转式压缩机的压缩组件
CN207777174U (zh) * 2017-12-28 2018-08-28 广东美芝制冷设备有限公司 低背压压缩机
CN111648962A (zh) * 2020-07-07 2020-09-11 苏州英华特涡旋技术股份有限公司 一种卧式涡旋压缩机的油循环结构

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