WO2023155331A1 - 压缩机和制冷设备 - Google Patents

压缩机和制冷设备 Download PDF

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Publication number
WO2023155331A1
WO2023155331A1 PCT/CN2022/095996 CN2022095996W WO2023155331A1 WO 2023155331 A1 WO2023155331 A1 WO 2023155331A1 CN 2022095996 W CN2022095996 W CN 2022095996W WO 2023155331 A1 WO2023155331 A1 WO 2023155331A1
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WO
WIPO (PCT)
Prior art keywords
suction hole
piston
dead center
compressor
suction
Prior art date
Application number
PCT/CN2022/095996
Other languages
English (en)
French (fr)
Inventor
黄刚
张洋洋
汪坤
晏子涵
马涛
Original Assignee
安徽美芝制冷设备有限公司
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.)
Filing date
Publication date
Application filed by 安徽美芝制冷设备有限公司 filed Critical 安徽美芝制冷设备有限公司
Priority to KR1020247025046A priority Critical patent/KR20240126052A/ko
Publication of WO2023155331A1 publication Critical patent/WO2023155331A1/zh

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Classifications

    • 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
    • F04B39/123—Fluid connections
    • 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
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/12—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high pressure
    • 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
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • 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
    • 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
    • F04B39/122—Cylinder block
    • 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
    • F04B39/125—Cylinder heads
    • 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
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type

Definitions

  • the present application relates to the technical field of compressors, in particular to compressors and refrigeration equipment.
  • Household refrigerators generally have a freezer compartment and a refrigerator compartment. During the cooling process of the freezer compartment and the refrigerator compartment, the evaporation temperatures of the corresponding refrigerants are different, and the pressures of the corresponding refrigerants are also different.
  • the existing compressors are connected in series to realize the refrigeration function of freezing and refrigerating through a suction pipe, which makes the COP (energy efficiency ratio) of the refrigerator lower.
  • the new single-cylinder double independent suction pump body structure has the ability to greatly improve the overall performance of the reciprocating compressor.
  • a second suction hole is correspondingly added at the same time.
  • the refrigerant requirements required by the freezer and refrigerator are different.
  • the main purpose of this application is to propose a compressor and refrigeration equipment, aiming at providing a compressor capable of realizing double suction and reasonably distributing the main suction volume and supplementary air volume.
  • the present application proposes a compressor, wherein the compressor includes:
  • a cylinder block the cylinder head of which is provided with a first suction hole, and the first suction hole is used to communicate with the first refrigeration flow path;
  • the piston assembly includes a piston movably arranged in the cylinder body, a working chamber is formed between the piston and the bottom of the cylinder body, and the piston has an upper stop located on the cylinder head of the cylinder body during the movable stroke. point and the bottom dead center of the cylinder head away from the cylinder block, the distance between the top dead center and the bottom dead center is S;
  • the cylinder or the piston is provided with a second air suction hole for communicating with the second refrigeration flow path, and the second air suction hole is set to be in contact with the set position when the piston moves to the set position.
  • the working chamber is connected, and at the set position, the distance between the piston and the top dead center is L1, and L1>0.5S.
  • the side wall of the cylinder is provided with a second suction hole
  • the distance between the second suction hole and the top dead center is L2, and L2>0.5S.
  • the side wall of the piston blocks and seals the second suction hole.
  • the second suction hole is a round hole.
  • the diameter of the second suction hole is D1, wherein D1 ⁇ 6mm.
  • the compressor further includes a first suction pipe for connecting the first cooling flow path and the first suction hole, and connecting the second cooling flow path and the first suction hole.
  • the second air suction pipe of the two air suction holes is a first suction pipe for connecting the first cooling flow path and the first suction hole, and connecting the second cooling flow path and the first suction hole.
  • the inner diameter of the second suction pipe is d1
  • the outer diameter of the second suction pipe is d2, wherein 0.3mm ⁇ d1 ⁇ 6mm, 0.4mm ⁇ d2 ⁇ 12.5mm.
  • the present application also provides a refrigeration device, which includes the above-mentioned compressor, and the compressor includes:
  • a cylinder block the cylinder head of which is provided with a first suction hole, and the first suction hole is used to communicate with the first refrigeration flow path;
  • the piston assembly includes a piston movably arranged in the cylinder body, a working chamber is formed between the piston and the bottom of the cylinder body, and the piston has a position on the upper side of the cylinder head close to the cylinder body during the movable stroke.
  • the bottom dead center and the bottom dead center of the cylinder head away from the cylinder block, the distance between the top dead center and the bottom dead center is S;
  • the cylinder or the piston is provided with a second air suction hole for communicating with the second refrigeration flow path, and the second air suction hole is set to be in contact with the set position when the piston moves to the set position.
  • the working chamber is connected, and at the set position, the distance between the piston and the top dead center is L1, and L1>0.5S.
  • the refrigeration device is a refrigerator.
  • the intake pressure of the first air intake hole is P1
  • the intake pressure of the second air intake hole is P2, wherein 1 ⁇ P2/P1 ⁇ 6.
  • the compressor includes a cylinder body and a piston assembly, and the cylinder head of the cylinder body is provided with a first suction hole, and the first suction hole is used to communicate with the first refrigeration flow path;
  • the piston assembly includes a piston movably arranged in the cylinder body, a working chamber is formed between the piston and the bottom of the cylinder body, and the piston has a cylinder head located close to the cylinder body during a movable stroke.
  • the second refrigeration flow path communicates with the second suction hole, and the second suction hole is set to communicate with the working chamber when the piston moves to the set position, and at the set position, the The distance between the piston and the top dead center is L1, and L1>0.5S.
  • the first refrigerating flow path corresponds to the freezer compartment of the refrigerator. Because the freezer compartment requires a relatively large cooling capacity and requires a large amount of refrigerant, the pressure of the refrigerant consumed during the working process is also relatively large, and
  • the second refrigerating flow path corresponds to the refrigerating room of the refrigerator.
  • the main purpose is to open the first suction hole for main suction, which can suck in a relatively large amount of refrigerant on the refrigeration flow path corresponding to the freezing chamber.
  • the second suction hole and the working The cavity is connected, the first suction hole is closed, the second suction hole starts to fill in high-pressure refrigerant gas, and continues to supply gas in the first half of the stroke of the compression stage, and finally in the second half of the stroke of the compression, the first The two suction holes are closed, and the piston compresses the refrigerant in the working chamber, which not only effectively improves the cooling capacity and energy efficiency ratio of the compressor, but also reasonably distributes the refrigerant gas with different pressures on the two refrigeration flow paths Return to the compressor to provide a compressor capable of realizing double suction and reasonably distributing the main suction volume and supplementary air volume.
  • FIG. 1 is a schematic diagram of the internal structure of an embodiment of a compressor provided by the present application
  • Fig. 2 is a schematic cross-sectional view of an embodiment of a compressor provided by the present application
  • FIG. 3 is a schematic perspective view of the compressor in FIG. 1 .
  • the directional indications are only used to explain the position in a certain posture (as shown in the attached figure). If the specific posture changes, the directional indication will also change accordingly.
  • Household refrigerators generally have a freezer compartment and a refrigerator compartment. During the cooling process of the freezer compartment and the refrigerator compartment, the evaporation temperatures of the corresponding refrigerants are different, and the pressures of the corresponding refrigerants are also different.
  • the existing compressors are connected in series to realize the refrigeration function of freezing and refrigerating through a suction pipe, which makes the COP (energy efficiency ratio) of the refrigerator lower. In order to obtain a better energy efficiency ratio, it is different from the traditional single Based on the suction single exhaust compression pump body mechanism, the new single-cylinder double independent suction pump body structure has the ability to greatly improve the overall performance of the reciprocating compressor.
  • Fig. 1 to Fig. 3 are specific embodiments of the compressor 100 provided in the present application.
  • the compressor 100 is used in the refrigeration system of the refrigerator as an example for illustration.
  • the high-temperature and high-pressure refrigerant gas is transported from the compressor to the evaporator of the corresponding freezer and refrigerator for evaporation and heat absorption, realizing The refrigeration of the freezer and the refrigerator, but the temperatures set in the freezer and the refrigerator are inconsistent, the evaporation temperature of the two is different, the temperature and pressure of the refrigerant after the heat exchange between the freezer and the refrigerator are different, and in the prior art,
  • the compressor realizes the refrigeration function of freezing and refrigerating through one flow path, so that when the freezer or the refrigerator needs to be refrigerated, the entire heat exchange system needs to participate in the work, resulting in high energy consumption and low energy efficiency .
  • the compressor 100 includes a cylinder body 1 and a piston assembly 2, the cylinder head of the cylinder body 1 is provided with a first air suction hole 11, and the first air suction hole 11 is used for It communicates with the first refrigeration flow path;
  • the piston assembly 2 includes a piston 21 movably arranged in the cylinder body 1, a working chamber 1a is formed between the piston 21 and the bottom of the cylinder body 1, and the piston 21 In the active stroke, there is a top dead center of the cylinder head located at the cylinder body 1 and a bottom dead center of the cylinder head far away from the cylinder body 1, and the distance between the top dead center and the bottom dead center is S ;
  • the cylinder 1 or the piston 21 is provided with a second suction hole 12 for communication with the second refrigeration flow path, and the second suction hole 12 is set to move in the piston 21 When reaching the set position, it communicates with the working chamber 1a, and when at the set position, the distance between the piston 21 and the top dead center is
  • the compressor 100 includes a cylinder body 1 and a piston assembly 2, and the cylinder head of the cylinder body 1 is provided with a first air suction hole 11, and the first air suction hole 11 is used to communicate with the first air suction hole.
  • a refrigeration flow path is connected;
  • the piston assembly 2 includes a piston 21 movable in the cylinder body 1, and the piston 21 has a top dead center located close to the cylinder head of the cylinder body 1 and a distance away from the The bottom dead center of the cylinder head of the cylinder block 1, the distance between the top dead center and the bottom dead center is S;
  • the cooling flow path communicates with the second suction hole 12, and the second suction hole 12 is set to communicate with the working chamber 1a when the piston 21 moves to the set position.
  • the first refrigerating flow path corresponds to the freezer compartment of the refrigerator. Because the freezer compartment requires a relatively large cooling capacity and requires a large amount of refrigerant, the pressure of the refrigerant consumed during the working process is also relatively large, and The second refrigerating flow path corresponds to the refrigerating room of the refrigerator.
  • the pressure of the consumed refrigerant is also relatively small, so the pressure returned to the first suction hole 11 It is much lower than the pressure of the second suction hole 12, but the amount of refrigerant in the first refrigeration flow path is relatively large, so that when the compressor 100 is working, the piston 21 first passes through the first half of the suction.
  • the first suction hole 11 is mainly opened for main suction, which can suck in a relatively large amount of refrigerant on the refrigeration flow path corresponding to the freezing chamber.
  • the second suction The hole 12 communicates with the working chamber 1a, the first suction hole 11 is closed, and the second suction hole 12 starts to replenish high-pressure refrigerant gas, and continues to replenish gas in the first half of the compression stage, and finally in the compression stage
  • the second suction hole 12 is closed, and the piston 21 compresses the refrigerant in the working chamber 1a, so that the first suction hole 11 and the second suction hole Reasonable setting of the opening and closing time of the hole 12 not only effectively improves the energy-efficiency ratio of the cooling capacity of the compressor 100, but also can reasonably distribute and return the refrigerant gas of different pressures on the two cooling flow paths to the compressor 100, so as to Provided is a compressor 100 capable of realizing double suction and reasonably distributing the main suction volume and supplementary air volume.
  • the distance between the piston 21 and the top dead center is L1, that is, the end surface of the end surface of the piston 21 close to the bottom wall of the cylinder body 1 and the distance between the cylinder body 1
  • the distance between the bottom walls is L1.
  • the distance between the top dead center and the bottom dead center is S, that is, the top dead center means that the end face of the end of the piston 21 close to the bottom wall of the cylinder 1 moves close to the cylinder.
  • the distance S is the distance between the two limit states of the end surface of the piston 21 close to the bottom wall of the cylinder 1 .
  • the second suction hole 12 can be arranged on the bottom wall of the cylinder body 1, opened and closed by a valve, and when the piston 21 moves to the set position, that is, the distance from the upper When the distance from the dead point is greater than 0.5S, the valve is opened, the second suction hole 12 is opened to supplement the working chamber 1a, and the first suction hole 11 is closed at the same time; of course, the second suction hole 12 is closed.
  • the suction hole 12 can also be arranged on the piston 21, and the valve controls the opening and closing of the second suction hole 12 on the piston 21; or the side wall of the piston 21 is provided with The second suction hole 12, the side wall of the cylinder 1 is provided with a groove corresponding to the second suction hole 12, by setting the position of the groove, the piston 21 moves to At the set position, the second air suction hole 12 corresponds to the groove, so that the second air suction hole 12 communicates with the working chamber 1a through the groove to replenish air.
  • the side wall of the cylinder body 1 is provided with a second suction hole 12, the distance between the second suction hole 12 and the top dead center is L2, and L2>0.5 S, because the first suction hole 11 is provided with a control valve group for its opening and closing, during the movement of the piston 21, the first suction hole 11 and the second suction hole 12
  • the opening and closing states are as follows:
  • the suction stroke of the cylinder including:
  • First stroke the piston 21 moves from the top dead center to the bottom dead center, and the distance from the top dead center is less than 0.5S.
  • the control valve group is opened, so that the first suction hole 11 is connected, and the second suction hole 12 is blocked by the piston 21 .
  • the working chamber 1 a of the cylinder body 1 only realizes air suction through the first air suction hole 11 .
  • the total amount of refrigerant in the working chamber 1 a comes from the first suction hole 11 , that is, the refrigerant in the first refrigeration flow path.
  • Second stroke when the piston 21 moves from the first dead center to the second dead center, and the distance from the first dead center is greater than 0.5S.
  • the piston 21 does not block the second suction hole 12 , so that the second suction hole 12 communicates with the working chamber 1 a of the cylinder 1 .
  • the control valve group is switched between an open state and a closed state according to actual requirements.
  • the control valve group is in an open state, the first air suction hole 11 and the second air suction hole 12 input airflow to the working chamber 1 a of the cylinder body 1 at the same time.
  • the second suction hole 12 supplies airflow to the working chamber 1 a of the cylinder body 1 .
  • the refrigerant replenished into the working chamber 1 a comes from the second suction hole 12 , that is, the refrigerant in the second refrigeration flow path flows back into the working chamber 1 a of the cylinder body 1 .
  • the position of the second air suction hole 12 can be set according to the requirement of the amount of supplementary air.
  • the compression stroke of the cylinder including:
  • the piston 21 moves from the bottom dead center to the direction close to the top dead center, and the distance from the top dead center is greater than 0.5S.
  • the control valve group is closed, and the piston 21 moves rapidly toward the top dead center.
  • the second air suction hole 12 still supplies airflow to the working chamber 1 a of the cylinder body 1 .
  • the refrigerant replenished into the working chamber 1 a comes from the second suction hole 12 . Therefore, in the third stroke, when the airflow in the working chamber 1a of the cylinder body 1 is compressed, the air flow input into the working chamber 1a of the cylinder body 1 through the second suction hole 12 will not be hindered excessively.
  • Airflow so that the cylinder 1 can still inhale airflow during the compression stroke. And, because the airflow from the first suction hole 11 and the second suction hole 12 is mixed in the working chamber 1a of the cylinder body 1, the pressure of the airflow in the working chamber 1a of the cylinder body 1 is less than Through the airflow pressure in the second suction hole 12 .
  • the piston 21 moves from the bottom dead center to the direction close to the top dead center, and the distance from the top dead center is less than 0.5S.
  • the control valve group is still closed, and the piston 21 blocks the second suction hole 12 .
  • the piston 21 compresses the airflow in the working chamber 1a of the cylinder 1 into a high-pressure airflow.
  • the airflow pressure in the working chamber 1a of the cylinder 1 is compressed to a certain position.
  • the control valve group connected to the output pipeline of the working chamber 1a of the cylinder 1 is switched from the closed state to the open state to output the compressed high-pressure air flow.
  • the compressor 100 does not need to specially set a control valve group to control the second suction hole 12
  • the automatic opening and closing of the second suction hole 12 can be realized during the movable stroke of the piston 21.
  • the structure design is ingenious, and the cost is also saved, and by setting the second suction hole 12
  • the distance between the hole 12 and the top dead center and the bottom dead center can control the intake air volume of the second air suction hole 12, that is, because the position setting of the second air suction hole 12 can make
  • the piston 21 reciprocates, it adjusts the duration of opening and closing of the second suction hole 12 , so as to adjust the flow ratio between the first suction hole 11 and the second suction hole 12 .
  • the flow path of the air flow in the first air intake channel is: the first external air intake pipe ⁇ the first air intake hole 11 ⁇ the working chamber 1a of the cylinder body 1 .
  • the air flow path in the second air intake channel is: the second external air intake pipe ⁇ the second air intake hole 12 ⁇ the working chamber 1 a of the cylinder body 1 .
  • the compressor 100 also includes an inner discharge pipe communicating with the working chamber 1a of the cylinder body 1, and the inner discharge pipe is used to communicate with the exhaust outer pipe 6 so as to discharge the internal discharge pipe in the working chamber 1a of the cylinder body 1.
  • the compressed high-pressure airflow is discharged from the inner discharge pipe to the exhaust outer pipe 6 .
  • the distance between the second suction hole 12 and the top dead center is L2, that is, the distance between the center line of the second suction hole 12 and the top dead center is L2.
  • the piston 21 can enable the second suction hole 12 in the first stroke and the fourth stroke in the suction and compression strokes.
  • the second suction hole 12 is in a closed state.
  • the side wall of the piston 21 is sealed with the second suction hole 12
  • the length of the piston 21 is at least greater than 0.5S, so that when the piston 21 runs to the top dead center, the side wall of the piston 21 still blocks the second suction hole 12 .
  • the second suction hole 12 is a round hole.
  • the cross-section of the second air suction hole 12 is circular, the pressure on the inner walls is the same, so that the stress on the second air suction hole 12 is the most uniform and the strength is the highest.
  • the way to adjust the air supply amount of the second suction hole 12 can also be adjusted by adjusting the size of the aperture of the second suction hole 12.
  • the amount of supplementary air, in this embodiment, the diameter of the second suction hole 12 is D1, wherein D1 ⁇ 6mm.
  • the compressor 100 further includes a first suction pipe 3 for communicating with the first refrigeration flow path and the first suction hole 11, and a first suction pipe 3 for communicating with the second refrigeration flow path.
  • the flow path and the second suction pipe 4 of the second suction hole 12 in this way, two suction pipes are provided to communicate with the corresponding two suction holes and the two refrigeration flow paths, so that the two refrigeration flow paths can Set up in parallel to provide two refrigerant gases with different pressures.
  • the manner in which the refrigerant gas with two different pressures can enter the cylinder body 1 corresponding to the first suction hole 11 and the second suction hole 12 is not limited to the above-mentioned certain method.
  • the high-pressure gas can directly flow into the casing 5 of the compressor 100, and then when the second suction hole 12 is opened, the high-pressure gas in the casing 5 is sucked through the second suction hole 12.
  • the housing 5 of the compressor 100 is provided with various components such as the cylinder body 1, the noise reduction device and the crankcase, and its internal space is relatively small, in order to realize the The internal space of the housing 5 is communicated and can be reasonably utilized.
  • the inner diameter of the second suction pipe 4 is d1
  • the outer diameter of the second suction pipe 4 is d2, wherein, 0.3mm ⁇ d1 ⁇ 6mm, 0.4mm ⁇ d2 ⁇ 12.5mm, so as to prevent the second air suction pipe 4 from being too thick and interfering with other parts, and if it is too thin, it will affect the amount of air supply, and the second air suction pipe 4
  • the thickness of the pipe wall of the pipe 4 is also correspondingly set to ensure that the air pressure strength does not damage the second suction pipe 4, and it can also have a certain degree of flexibility to prevent vibration noise.
  • the present application also proposes a refrigeration device, which includes the compressor 100 described in the above technical solution.
  • the detailed structure of the compressor 100 of the refrigeration equipment can refer to the embodiment of the above-mentioned compressor 100, which will not be repeated here; since the above-mentioned compressor 100 is used in the refrigeration equipment of the present application, therefore, this
  • the embodiments of the application for refrigeration equipment include all the technical solutions of all the embodiments of the above-mentioned compressor 100, and the achieved technical effects are also completely the same, which will not be repeated here.
  • the specific form of the refrigeration equipment is not limited, and it may be a refrigerator, a dehumidifier, or other equipment.
  • the refrigeration device is a refrigerator.
  • the second suction hole 12 can normally intake air during the suction and compression process of the cylinder 1.
  • the first The intake pressure of one suction hole 11 is P1
  • the intake pressure of the second suction hole 12 is P2, wherein 1 ⁇ P2/P1 ⁇ 6.
  • the second air suction hole 12 can supply air to the working chamber 1a, thereby improving the working chamber 1a of the cylinder body 1.
  • the suction capacity of the compressor can be improved, thereby improving the compression refrigeration capacity and energy efficiency of the compressor, and realizing the respective working conditions through two parallel flow paths, reducing power consumption.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)

Abstract

本申请公开一种压缩机和制冷设备，压缩机包括缸体和活塞组件，缸体的气缸盖上设置有第一吸气孔；活塞在活动行程中具有位于靠近缸体的气缸盖的上止点及远离缸体的气缸盖的下止点，上止点与下止点之间的距离为S，在缸体或活塞上设置有第二吸气孔，第二吸气孔被设置为在活塞活动至设定位置时与工作腔连通，在设定位置时，活塞与上止点的距离为L1，且L1＞0.5S。

Description

压缩机和制冷设备
本申请要求于2022年2月18日申请的、申请号为202210155326.6的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及压缩机技术领域，尤其涉及压缩机和制冷设备。
 背景技术
压缩机作为制冷系统的最核心部件和耗能大件，对其的制冷性能和能效水平也提出的更高要求。家用冰箱一般有冷冻室和冷藏室，在实现冷冻室和冷藏室的降温过程中，对应的冷媒的蒸发温度不一样，且对应的冷媒的压力也不一样。
现有的压缩机以串联的形式通过一根吸气管管路实现冷冻和冷藏的制冷功能，这样使得冰箱的COP（能效比）较低，为了取得较好的能效比，区别于传统的单吸气单排气压缩泵体机构基础上，新型的单气缸双独立吸气的泵体结构具有大幅提升往复式压缩机整体性能的能力，在压缩机工作的时候，为了提升其制冷量和能效COP，同时相应的增设第二吸气孔，但是压缩机气缸在工作过程中因冷冻室与冷藏室对应的制冷需求不同，冷冻室与冷藏室所需的冷媒需求却均不同。
 技术问题
本申请的主要目的是提出一种压缩机和制冷设备，旨在提供一种能够实现双吸气并将主吸气量和补气量进行合理分配的压缩机。
 技术解决方案
为实现上述目的，本申请提出的一种压缩机，其中所述压缩机包括：
缸体，所述缸体的气缸盖上设置有第一吸气孔，所述第一吸气孔用以与第一制冷流路连通；以及，
活塞组件，包括活动设于所述缸体内的活塞，所述活塞与所述缸体的底部之间形成工作腔，所述活塞在活动行程中具有位于所述缸体的气缸盖的上止点及远离所述缸体的气缸盖的下止点，所述上止点与所述下止点之间的距离为S；
其中，所述缸体或所述活塞上设置有用以与第二制冷流路连通设置的第二吸气孔，所述第二吸气孔被设置为在所述活塞活动至设定位置时与所述工作腔连通，在所述设定位置时，所述活塞与所述上止点的距离为L1，且L1＞0.5S。
在一实施例中，所述缸体的侧壁贯设有第二吸气孔；
所述第二吸气孔与所述上止点的距离为L2，且L2＞0.5S。
在一实施例中，在所述活塞位于所述上止点时，所述活塞的侧壁遮挡密封所述第二吸气孔。
在一实施例中，所述第二吸气孔为圆孔。
在一实施例中，所述第二吸气孔的孔径为D1，其中，D1≤6mm。
在一实施例中，所述压缩机还包括用以连通所述第一制冷流路和所述第一吸气孔的第一吸气管，以及连通所述第二制冷流路和所述第二吸气孔的第二吸气管。
在一实施例中，所述第二吸气管的内径为d1，所述第二吸气管的外径为d2，其中，0.3mm≤d1≤6mm，0.4mm≤d2≤12.5mm。
本申请还提供一种制冷设备，所述制冷设备包括上述的压缩机，所述压缩机包括：
缸体，所述缸体的气缸盖上设置有第一吸气孔，所述第一吸气孔用以与第一制冷流路连通；以及，
活塞组件，包括活动设于所述缸体内的活塞，所述活塞与所述缸体的底部之间形成工作腔，所述活塞在活动行程中具有位于靠近所述缸体的气缸盖的上止点及远离所述缸体的气缸盖的下止点，所述上止点与所述下止点之间的距离为S；
其中，所述缸体或所述活塞上设置有用以与第二制冷流路连通设置的第二吸气孔，所述第二吸气孔被设置为在所述活塞活动至设定位置时与所述工作腔连通，在所述设定位置时，所述活塞与所述上止点的距离为L1，且L1＞0.5S。
在一实施例中，所述制冷设备为冰箱。
在一实施例中，所述第一吸气孔的进气压力为P1，所述第二吸气孔的进气压力为P2，其中，1＜P2/P1≤6。
 有益效果
本申请提供的技术方案中，压缩机包括缸体和活塞组件，所述缸体的气缸盖上设置有第一吸气孔，所述第一吸气孔用以与第一制冷流路连通；所述活塞组件包括活动设于所述缸体内的活塞，所述活塞与所述缸体的底部之间形成工作腔，所述活塞在活动行程中具有位于靠近所述缸体的气缸盖的上止点及远离所述缸体的气缸盖的下止点，所述上止点与所述下止点之间的距离为S；通过在所述缸体或所述活塞上设置有用以与第二制冷流路连通设置的第二吸气孔，所述第二吸气孔被设置为在所述活塞活动至设定位置时与所述工作腔连通，在所述设定位置时，所述活塞与所述上止点的距离为L1，且L1＞0.5S。所述第一制冷流路对应的是冰箱冷冻室，因冷冻室所需的制冷量较大，所需的冷媒量较多，在工作工程中，其消耗掉的冷媒的压力也较多，而所述第二制冷流路对应的是冰箱冷藏室，因冷藏室所需的制冷量较小，其消耗掉的冷媒的压力也较少，这样回流至所述第一吸气孔内的压力是远小于所述第二吸气孔的压力，但是第一制冷流路的冷媒量较大，这样在所述压缩机工作时，通过所述活塞先在吸气的前大半段的吸气行程中主要是打开第一吸气孔进行主吸气，能够吸入冷冻室对应的制冷流路上的较大的冷媒量，在后面小半段的吸气行程中，所述第二吸气孔与所述工作腔连通，第一吸气孔关闭，所述第二吸气孔开始补入高压冷媒气体，并在压缩阶段的前小半段行程继续补气，最后在压缩的后大半段行程中，所述第二吸气孔关闭，所述活塞将所述工作腔内的冷媒进行压缩，不仅使得压缩机的制冷量和能效比有效的提高，并且将两个制冷流路上的不同压力的冷媒气体能够合理分配回流至所述压缩机，以提供一种能够实现双吸气并将主吸气量和补气量进行合理分配的压缩机。
 附图说明
为了更清楚地说明本申请实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图示出的结构获得其他的附图。
图1为本申请提供的压缩机一实施例的内部结构示意图；
图2为本申请提供的压缩机一实施例的截面示意图；
图3为图1中的压缩机的立体示意图。
附图标号说明：
标号 名称 标号 名称
100 压缩机 21 活塞
1 缸体 3 第一吸气管
1a 工作腔 4 第二吸气管
11 第一吸气孔 5 壳体
12 第二吸气孔 6 排气外管
2 活塞组件    
本申请目的的实现、功能特点及优点将结合实施例，参照附图做进一步说明。
 本发明的实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请的一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
需要说明，若本申请实施例中有涉及方向性指示（诸如上、下、左、右、前、后……），则该方向性指示仅用于解释在某一特定姿态（如附图所示）下各部件之间的相对位置关系、运动情况等，如果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，若本申请实施例中有涉及“第一”、“第二”等的描述，则该“第一”、“第二”等的描述仅用于描述目的，而不能理解为指示或暗示其相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。另外，全文中出现的“和/或”的含义，包括三个并列的方案，以“A和/或B”为例，包括A方案、或B方案、或A和B同时满足的方案。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本申请要求的保护范围之内。
压缩机作为制冷系统的最核心部件和耗能大件，对其的制冷性能和能效水平也提出的更高要求。家用冰箱一般有冷冻室和冷藏室，在实现冷冻室和冷藏室的降温过程中，对应的冷媒的蒸发温度不一样，且对应的冷媒的压力也不一样。现有的压缩机以串联的形式通过一根吸气管管路实现冷冻和冷藏的制冷功能，这样使得冰箱的COP（能效比）较低，为了取得较好的能效比，区别于传统的单吸气单排气压缩泵体机构基础上，新型的单气缸双独立吸气的泵体结构具有大幅提升往复式压缩机整体性能的能力，在压缩机工作的时候，为了提升其制冷量和能效COP，同时相应的增设第二吸气孔，但是压缩机气缸在工作过程中因冷冻室与冷藏室对应的制冷需求不同，冷冻室与冷藏室所需的冷媒需求却均不同。
为了解决上述问题，本申请提供一种压缩机100，图1至图3为本申请提供的压缩机100的具体实施例。
以所述压缩机100用于冰箱的制冷系统为例进行说明，因冰箱在制冷过程中，高温高压冷媒冷媒气体自压缩机输送至对应的冷冻室和冷藏室的蒸发器进行蒸发吸热，实现冷冻室和冷藏室的制冷，但是冷冻室和冷藏室设置的温度不一致，两者蒸发温度不一样，冷媒在冷冻室和冷藏室进行换热后的温度和压力不相同，并且现有技术中，压缩机通过一个流路实现冷冻和冷藏的制冷功能，这样不管是冷冻室或是冷藏室需要进行制冷的时候，整个换热系统都需要参与到工作中，使得能耗消耗较大，能效比较低。
请参阅图1至图3，所述压缩机100包括缸体1和活塞组件2，所述缸体1的气缸盖上设置有第一吸气孔11，所述第一吸气孔11用以与第一制冷流路连通；所述活塞组件2包括活动设于所述缸体1内的活塞21，所述活塞21与所述缸体1的底部之间形成工作腔1a，所述活塞21在活动行程中具有位于所述缸体1的气缸盖的上止点及远离所述缸体1的气缸盖的下止点，所述上止点与所述下止点之间的距离为S；其中，所述缸体1或所述活塞21上设置有用以与第二制冷流路连通设置的第二吸气孔12，所述第二吸气孔12被设置为在所述活塞21活动至设定位置时与所述工作腔1a连通，在所述设定位置时，所述活塞21与所述上止点的距离为L1，且L1＞0.5S。
本申请提供的技术方案中，压缩机100包括缸体1和活塞组件2，所述缸体1的气缸盖上设置有第一吸气孔11，所述第一吸气孔11用以与第一制冷流路连通；所述活塞组件2包括活动设于所述缸体1内的活塞21，所述活塞21在活动行程中具有位于靠近所述缸体1的气缸盖的上止点及远离所述缸体1的气缸盖的下止点，所述上止点与所述下止点之间的距离为S；通过在所述缸体1或所述活塞21上设置有用以与第二制冷流路连通设置的第二吸气孔12，所述第二吸气孔12被设置为在所述活塞21活动至设定位置时与所述工作腔1a连通，在所述设定位置时，所述活塞21与所述上止点的距离为L1，且L1＞0.5S。所述第一制冷流路对应的是冰箱冷冻室，因冷冻室所需的制冷量较大，所需的冷媒量较多，在工作工程中，其消耗掉的冷媒的压力也较多，而所述第二制冷流路对应的是冰箱冷藏室，因冷藏室所需的制冷量较小，其消耗掉的冷媒的压力也较少，这样回流至所述第一吸气孔11内的压力是远小于所述第二吸气孔12的压力，但是第一制冷流路的冷媒量较大，这样在所述压缩机100工作时，通过所述活塞21先在吸气的前大半段的吸气行程中主要是打开第一吸气孔11进行主吸气，能够吸入冷冻室对应的制冷流路上的较大的冷媒量，在后面小半段的吸气行程中，所述第二吸气孔12与所述工作腔1a连通，第一吸气孔11关闭，所述第二吸气孔12开始补入高压冷媒气体，并在压缩阶段的前小半段行程继续补气，最后在压缩的后大半段行程中，所述第二吸气孔12关闭，所述活塞21将所述工作腔1a内的冷媒进行压缩，这样通过将所述第一吸气孔11和所述第二吸气孔12开启和关闭的时间的合理设置，不仅使得压缩机100的制冷量能效比有效的提高，并且将两个制冷流路上的不同压力的冷媒气体能够合理分配回流至所述压缩机100，以提供一种能够实现双吸气并将主吸气量和补气量进行合理分配的压缩机100。
需要说明的是，请参阅图3，所述活塞21与所述上止点的距离为L1，即所述活塞21靠近所述缸体1的底壁的一端的端面与所述缸体1的底壁之间的距离为L1。所述上止点与所述下止点之间的距离为S，即所述上止点是指所述活塞21靠近所述缸体1的底壁的一端的端面运动至靠近所述缸体1的底壁的最近的距离时，所述活塞21靠近所述缸体1的底壁的一端所在的位置，所述下止点是指所述活塞21靠近所述缸体1的底壁的一端的端面运动至远离所述缸体1的底壁的最远的距离时，所述活塞21靠近所述缸体1的底壁的一端所在的位置。也即距离S为所述活塞21靠近所述缸体1的底壁的一端的端面两种极限状态下之间的距离。
可以理解的是，所述第二吸气孔12可以设置在所述缸体1的底壁上，通过阀门进行开闭，在所述活塞21运动至所述设定位置，即距离所述上止点的距离大于0.5S时，所述阀门打开，所述第二吸气孔12开启对所述工作腔1a进行补气，同时所述第一吸气孔11关闭；当然，所述第二吸气孔12还可以设置在所述活塞21上，所述阀门控制所述活塞21上的所述第二吸气孔12的开启和关闭；亦或是所述活塞21的侧壁上设置有所述第二吸气孔12，所述缸体1的侧壁上设置有与所述第二吸气孔12对应设置的凹槽，通过设置凹槽的位置，使得在所述活塞21活动至所述设定位置时，所述第二吸气孔12与所述凹槽对应，使得所述第二吸气孔12通过所述凹槽连通所述工作腔1a进行补气。以上的各种形式都使得所述活塞21在吸气的后半段行程和压缩的前半段行程中开启所述第二吸气孔12，使得所述第一吸气孔11开启的时间较长，即吸气时长较长，也使得所述第一吸气孔11的吸气量较大，而所述第二吸气孔12开启的时间较短，补气时间较短，合理对应所述第二吸气孔12的补气量较小，从而达到合理分配两个制冷流路上的冷媒量。
具体地，在本实施例中，所述缸体1的侧壁贯设有第二吸气孔12，所述第二吸气孔12与所述上止点的距离为L2，且L2＞0.5S，因所述第一吸气孔11设有用以实现其开闭的控制阀组，所述活塞21在运动过程中，所述第一吸气孔11及所述第二吸气孔12的开闭状态如下：
气缸的吸气行程，包括：
第一行程：所述活塞21自所述上止点向所述下止点活动，且距所述上止点的距离小于0.5S。在第一行程中，所述控制阀组开启，使得所述第一吸气孔11导通，且所述第二吸气孔12被所述活塞21遮挡。此时，所述缸体1的工作腔1a仅通过所述第一吸气孔11实现吸气。此时所述工作腔1a内的冷媒总量均来自于所述第一吸气孔11，即第一制冷流路的冷媒。可以理解的是，由于所述活塞21在向靠近所述下止点的位置活动时，所述缸体1的工作腔1a的压缩空间增大，处于负压状态，便于外部的气流自所述第一吸气孔11进入所述缸体1的工作腔1a。而由于经由所述第一吸气孔11的气流压力小于经由所述第二吸气孔12的气流压力。故，在此活动行程中，通过所述活塞21将所述第二吸气孔12遮挡，以避免所述第二吸气孔12的气流阻碍所述第一吸气孔11的气流进入所述缸体1的工作腔1a。
第二行程：在所述活塞21自所述第一止点向所述第二止点活动，且距所述第一止点的距离大于0.5S。在第二行程中，所述活塞21未遮挡所述第二吸气孔12，使得所述第二吸气孔12连通所述缸体1的工作腔1a。此时，所述控制阀组按实际需求在开启状态与闭合状态之间切换。在所述控制阀组处于开启状态时，所述第一吸气孔11及所述第二吸气孔12同时向所述缸体1的工作腔1a输入气流。由于在第一行程中，所述缸体1的工作腔1a的空间内经由所述第一吸气孔11吸入了一定量的气流，使得压缩空间中具有一定的气流压力。故，在经由所述第二吸气孔12向所述缸体1的工作腔1a输入气流时，对所述第一吸气孔11的气流影响较小。且由于所述第二吸气孔12到所述第一止点的距离大于0.5S，也即到所述第一吸气孔11的距离大于0.5S，使得两者之间存在适宜的缓冲距离，减轻了所述第二吸气孔12的气流对所述第一吸气孔11气流的阻碍影响，提高压缩能效。在所述控制阀组处于闭合状态时，所述第二吸气孔12向所述缸体1的工作腔1a输入气流。此时补充至所述工作腔1a内的冷媒来自于所述第二吸气孔12，即第二制冷流路的冷媒均回流至所述缸体1的工作腔1a内。可以理解的是，所述第二吸气孔12越靠近所述第一止点与所述第二止点的中点，所述第二吸气孔12开启时间早，并且关闭的时间晚，所述第二制冷流路提供的高压冷媒时间长，补气量大；所述第二吸气孔12越靠近所述第二止点时，所述第二吸气孔12开启时间晚，并且关闭的时间早，所述第二制冷流路提供的高压冷媒时间短，补气时间短，从而补气量也较少。在现实中，可以依据补气量的需求，来设置所述第二吸气孔12的位置。
气缸的压缩行程，包括：
第三行程：所述活塞21自所述下止点向靠近所述上止点的方向活动，且距所述上止点大于0.5S。在第三行程中，所述控制阀组关闭，所述活塞21向靠近所述上止点的方向快速活动。此时，所述第二吸气孔12仍然向所述缸体1的工作腔1a输入气流。此时补充至所述工作腔1a内的冷媒来自于所述第二吸气孔12。因此，在第三行程中，所述缸体1的工作腔1a中的气流被压缩时，尚不会过度阻碍经由所述第二吸气孔12输入所述缸体1的工作腔1a内的气流，使得所述缸体1在压缩行程中，仍可吸入气流。并且，由于所述缸体1的工作腔1a中混合有来自所述第一吸气孔11及所述第二吸气孔12的气流，使得所述缸体1的工作腔1a中气流压力小于经由所述第二吸气孔12内的气流压力。
第四行程：所述活塞21自所述下止点向靠近所述上止点的方向活动，且距所述上止点的距离小于0.5S。在第四行程中，所述控制阀组仍关闭，且所述活塞21遮挡所述第二吸气孔12。此过程中，所述活塞21将所述缸体1的工作腔1a中的气流压缩成高压气流。并在所述活塞21活动至所述下止点时，所述缸体1的工作腔1a中的气流压力压缩到位。此时，连通所述缸体1的工作腔1a的输出管道的控制阀组从关闭状态切换为打开状态，以输出压缩好的高压气流。
在本实施例的技术方案中，通过将所述第二吸气孔12靠近所述下止点设置，从而使得所述压缩机100无需专门设置控制阀组来控制所述第二吸气孔12的开闭，而是在所述活塞21的活动行程中就能实现对所述第二吸气孔12的自动开闭，结构设计巧妙，还节约了成本，并且通过设置所述第二吸气孔12距离所述上止点和所述下止点的距离，可以控制所述第二吸气孔12的进气量，即，因所述第二吸气孔12的位置设定，可以使得所述活塞21在往复运动的时候，来调整所述第二吸气孔12开闭的时长，从而实现调节所述第一吸气孔11和所述第二吸气孔12的流量配比。
需要说明的是，所述压缩机100对应两个制冷流路的工作线路为：
第一吸气流道中气流的流路为：第一外部吸气管→所述第一吸气孔11→所述缸体1的工作腔1a。
所述第二吸气流道中气流流路为：第二外部吸气管→所述第二吸气孔12→所述缸体1的工作腔1a。
且所述压缩机100还包括与所述缸体1的工作腔1a连通的内排管，所述内排管用以与排气外管6连通，以将所述缸体1的工作腔1a内压缩好的高压气流自所述内排管排出至排气外管6。
需要说明的是，所述第二吸气孔12与所述上止点的距离为L2，也即，所述第二吸气孔12的中心线与所述上止点的距离为L2。
进一步地，为了利用所述活塞21完全充当阀门开闭的功能，使得所述活塞21在吸气和压缩的行程中能够使得所述第二吸气孔12在第一行程和第四行程中能够使得所述第二吸气孔12处于关闭状态，在本实施例中，在所述活塞21位于所述上止点时，所述活塞21的侧壁以与所述第二吸气孔12密封设置，即所述活塞21的长度至少大于0.5S，这样在所述活塞21运行至所述上止点时，所述活塞21的侧壁依然将所述第二吸气孔12封堵。
进一步地，在本实施例中，所述第二吸气孔12为圆孔。当所述第二吸气孔12的截面为圆形时，因内壁面受到的压强相同，这样使得所述第二吸气孔12的受力最均匀，且强度最高。
具体地，调整所述第二吸气孔12的补气量的方式除了调节所述第二吸气孔12的开闭时长，还可以通过调整所述第二吸气孔12的孔径的大小来调节补气量，在本实施例中，所述第二吸气孔12的孔径为D1，其中，D1≤6mm。
具体地，在本实施例中，所述压缩机100还包括用以连通所述第一制冷流路和所述第一吸气孔11的第一吸气管3，以及连通所述第二制冷流路和所述第二吸气孔12的第二吸气管4，这样通过设置两个吸气管来连通对应的两个吸气孔和两个制冷流路，使得两个制冷流路能够并联设置，以提供不同压力两路冷媒气体。
可以理解的是，当然实现两个不同的压力的冷媒气体能够分别对应所述第一吸气孔11和所述第二吸气孔12进入所述缸体1的方式也不仅限于采用上述的一定采用两个管路，也还可以是只设置所述第一吸气管3，将所述第一制冷流路与所述第一吸气孔11连通，而所述第二制冷流路回流的高压气体可以直接流入至所述压缩机100的壳体5内，然后在所述第二吸气孔12被打开时，所述壳体5内的高压气体通过所述第二吸气孔12被压入至所述缸体1内；同理，还可以是只设置所述第二吸气管4，将所述第二制冷流路与所述第二吸气孔12连通，而所述第一制冷流路回流的高压气体可以直接流入至所述压缩机100的壳体5内，然后在所述第一吸气孔11被打开时，所述壳体5内的高压气体通过所述第一吸气孔11被压入至所述缸体1内。
具体地，因所述压缩机100的壳体5内设置有所述缸体1，消音装置和曲轴箱等各种零部件，其内部空间较小，为了实现所述第二吸气管4的连通并能够合理的利用所述壳体5的内部空间，在本实施例中，所述第二吸气管4的内径为d1，所述第二吸气管4的外径为d2，其中，0.3mm≤d1≤6mm，0.4mm≤d2≤12.5mm，这样防止所述第二吸气管4过粗，与其它的零部件产生干涉，过细，又影响补气量，并且所述第二吸气管4的管壁的厚度也相应设置在保证气压强度不损坏所述第二吸气管4的情况下，又能够有一定的柔韧性，防止产生震动噪音。
此外，为实现上述目的，本申请还提出一种制冷设备，所述制冷设备包括上述技术方案所述的压缩机100。需要说明的是，所述制冷设备的压缩机100的详细结构可参照上述压缩机100的实施例，此处不再赘述；由于在本申请的制冷设备中使用了上述压缩机100，因此，本申请制冷设备的实施例包括上述压缩机100全部实施例的全部技术方案，且所达到的技术效果也完全相同，在此不再赘述。
需要说明的是，所述制冷设备的具体形式不做限制，可以是冷柜，也可以是除湿机，还可以是其他设备。具体地，在本实施例中，所述制冷设备为冰箱。
进一步地，为了使得所述压缩机100能正常工作，所述缸体1的吸气和压缩过程中，所述第二吸气孔12能够正常的进气，在本实施例中，所述第一吸气孔11的进气压力为P1，所述第二吸气孔12的进气压力为P2，其中，1＜P2/P1≤6。这样通过设置两个并联的流路，即冷冻制冷流路和冷藏制冷流路，即所述压缩机100将压缩形成的高温高压冷媒可以合理的分配至冷冻流路和冷藏流路，这样在所述缸体1对第一吸气孔11输送的冷媒气体压缩时，所述第二吸气孔12可以对所述工作腔1a内进行补气，从而提高了所述缸体1的工作腔1a的吸气量，进而提高压缩机的压缩制冷能力和能效，并且通过两个并联的流路来实现各自的工况条件，降低功率消耗。
以上所述仅为本申请的优选实施例，并非因此限制本申请的专利范围，凡是在本申请的发明构思下，利用本申请说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本申请的专利保护范围内。

Claims (10)

  1. 一种压缩机，其中，包括：
    缸体，所述缸体的气缸盖上设置有第一吸气孔，所述第一吸气孔用以与第一制冷流路连通；以及，
    活塞组件，包括活动设于所述缸体内的活塞，所述活塞与所述缸体的底部之间形成工作腔，所述活塞在活动行程中具有位于靠近所述缸体的气缸盖的上止点及远离所述缸体的气缸盖的下止点，所述上止点与所述下止点之间的距离为S；
    其中，所述缸体或所述活塞上设置有用以与第二制冷流路连通设置的第二吸气孔，所述第二吸气孔被设置为在所述活塞活动至设定位置时与所述工作腔连通，在所述设定位置时，所述活塞与所述上止点的距离为L1，且L1＞0.5S。
  2. 如权利要求1所述的压缩机，其中，所述缸体的侧壁贯设有第二吸气孔；
    所述第二吸气孔与所述上止点的距离为L2，且L2＞0.5S。
  3. 如权利要求2所述的压缩机，其中，在所述活塞位于所述上止点时，所述活塞的侧壁遮挡密封所述第二吸气孔。
  4. 如权利要求2所述的压缩机，其中，所述第二吸气孔为圆孔。
  5. 如权利要求2所述的压缩机，其中，所述第二吸气孔的孔径为D1，其中，D1≤6mm。
  6. 如权利要求1所述的压缩机，其中，所述压缩机还包括用以连通所述第一制冷流路和所述第一吸气孔的第一吸气管，以及连通所述第二制冷流路和所述第二吸气孔的第二吸气管。
  7. 如权利要求6所述的压缩机，其中，所述第二吸气管的内径为d1，所述第二吸气管的外径为d2，其中，0.3mm≤d1≤6mm，0.4mm≤d2≤12.5mm。
  8. 一种制冷设备，其中，包括如权利要求1至7任一项所述的压缩机。
  9. 如权利要求8所述的制冷设备，其中，所述制冷设备为冰箱。
  10. 如权利要求9所述的制冷设备，其中，所述第一吸气孔的进气压力为P1，所述第二吸气孔的进气压力为P2，其中，1＜P2/P1≤6。
PCT/CN2022/095996 2022-02-18 2022-05-30 压缩机和制冷设备 WO2023155331A1 (zh)

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CN103615377A (zh) * 2013-11-26 2014-03-05 武汉凌达压缩机有限公司 一种往复式压缩机
CN107407265A (zh) * 2014-12-11 2017-11-28 安吉拉通力测试技术有限公司简称Att有限公司 用于冷却设备的往复式压缩机

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JPH04255581A (ja) * 1991-02-07 1992-09-10 Sanyo Electric Co Ltd 圧縮機の冷却装置
US6318977B1 (en) * 1997-10-06 2001-11-20 Worksmart Energy Enterprises, Inc. Reciprocating compressor with auxiliary port
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