WO2020153664A1 - Compresseur - Google Patents

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Publication number
WO2020153664A1
WO2020153664A1 PCT/KR2020/000843 KR2020000843W WO2020153664A1 WO 2020153664 A1 WO2020153664 A1 WO 2020153664A1 KR 2020000843 W KR2020000843 W KR 2020000843W WO 2020153664 A1 WO2020153664 A1 WO 2020153664A1
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WO
WIPO (PCT)
Prior art keywords
suction port
suction
compressor
chamber
refrigerant
Prior art date
Application number
PCT/KR2020/000843
Other languages
English (en)
Korean (ko)
Inventor
송세영
김옥현
성열우
윤덕빈
이원빈
최준식
김광진
황승용
Original Assignee
한온시스템 주식회사
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 한온시스템 주식회사 filed Critical 한온시스템 주식회사
Publication of WO2020153664A1 publication Critical patent/WO2020153664A1/fr

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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
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • F05B2260/962—Preventing, counteracting or reducing vibration or noise by means creating "anti-noise"

Definitions

  • the present invention relates to a compressor, and more particularly, to a compressor that can reduce the noise of the refrigerant flowing into the suction chamber.
  • an air conditioner for indoor air conditioning is installed in a vehicle.
  • Such an air conditioning system includes a compressor that compresses a low-temperature, low-pressure gaseous refrigerant drawn from an evaporator into a high-temperature and high-pressure gaseous refrigerant and sends it to a condenser as a cooling system.
  • Compressors include a reciprocating type for compressing refrigerant according to the reciprocating motion of a piston and a rotating type for performing compression while rotating.
  • crank type that uses a crank to transfer a plurality of pistons according to a transmission method of a drive source
  • a swash plate type that transmits to a rotating shaft provided with a swash plate.
  • rotary type a rotary rotary shaft and a vane rotary type using vanes
  • scrolling type using orbiting scroll and fixed scroll.
  • Such a compressor typically includes a casing having a suction chamber and a discharge chamber, and a compression mechanism that sucks and compresses refrigerant in the suction chamber and discharges it to the discharge chamber, and further includes noise reduction means for reducing the noise of the refrigerant.
  • Figure 1 is a cross-sectional view showing a conventional compressor
  • Figure 2 is a cross-sectional view showing a noise reduction means in the compressor.
  • the noise reduction means in the conventional compressor is inserted into the suction port 132 of the casing 100 and the suction chamber S1 of the casing 100 from the suction port 132 It is formed of a so-called suction damping device (SDD) that controls the amount of refrigerant flowing into the furnace.
  • SDD suction damping device
  • the conventional noise reduction means includes a valve seal 14, a valve inlet 12 communicating the valve seal 14 and the suction port 132, and the valve seal 14 and the suction chamber S1.
  • the valve body 10 having a valve outlet (16) communicating, reciprocating inside the valve chamber (14) and adjusting the opening amount of the valve inlet (12) and the opening amount of the valve outlet (16) It includes a valve core 20 and an elastic member 30 for applying an elastic force to the valve core (20).
  • Conventional noise reduction means by adjusting the opening amount of the valve inlet 12 and the opening amount of the valve outlet 16 according to the compressor load to reduce the noise of the refrigerant flowing into the suction chamber (S1) Reduce.
  • the load of the compressor increases, more refrigerant flows into the compressor and is compressed and then discharged. Since the refrigerant is a kind of noise source, the increase in the amount of refrigerant flowing into the compressor means that the noise increases as well. Accordingly, in order to reduce noise, it is necessary to prevent more than necessary refrigerant from flowing into the interior of the compressor, and the conventional noise reduction means adjusts the refrigerant suction amount flowing from the suction port 132 into the suction chamber S1. Thus, noise is reduced by preventing more refrigerant than necessary from entering the compressor (more precisely, the suction chamber S1).
  • the noise reduction means is formed in a manner that is fastened to the casing 100
  • various processes for fastening the noise reduction means to the casing 100 for example, forming fastening protrusions on the noise reduction means and fastening protrusions
  • the process of forming the inserted fastening groove in the casing, the process of assembling the noise reducing means to the casing, etc. is required, and there is a problem in that the cost required to form the noise reducing means in the casing 100 is increased.
  • the valve core 20 reciprocates and generates noise, and a gap is generated between the noise reduction means and the casing 100 due to tolerance or thermal expansion, so that the noise reduction means is relatively vibrated relative to the casing 100 Noise is generated.
  • the noise reduction means since the noise reduction means only adjusts the amount of the noise source (refrigerant suction amount) and does not attenuate the noise source, there is a limit to reducing the noise of the refrigerant.
  • each distance from the outlet of the noise reduction means (valve outlet 16) to the plurality of compression chambers is different from each other, and there is a problem that the refrigerant is not evenly distributed to the plurality of compression chambers.
  • an object of the present invention is to provide a compressor that can reduce the cost required to form the noise reduction means and suppress the increase in the weight of the compressor by the noise reduction means.
  • Another object of the present invention is to provide a compressor capable of reducing the cost required when forming the noise reduction means in the casing.
  • Another object of the present invention is to provide a compressor capable of preventing noise generated by noise reduction means.
  • Another object of the present invention is to provide a compressor in which a noise reduction means attenuates a noise source to further reduce noise.
  • Another object of the present invention is to provide a compressor in which a refrigerant can be evenly distributed to a plurality of compression chambers.
  • a suction chamber, a discharge chamber and a casing having a suction port for guiding a refrigerant to the suction chamber;
  • a compression mechanism for sucking and compressing the refrigerant in the suction chamber and discharging it into the discharge chamber;
  • noise reduction means for reducing noise of the refrigerant flowing into the suction chamber, wherein the noise reduction means provides a compressor integrally formed with the suction port.
  • the suction port the suction port inlet communicating with the refrigerant suction pipe;
  • a suction port muffler extending from the suction port inlet toward the suction chamber;
  • a suction port outlet communicating the suction port muffler with the suction chamber.
  • the suction port muffler may extend to the center of the suction chamber.
  • the compression mechanism includes a plurality of compression chambers, and the suction port outlets may be formed at the center of the suction chambers so that the distances from the suction port outlets to the plurality of compression chambers are equal to each other.
  • the suction port outlet may be formed as a long hole extending along the longitudinal direction of the suction port muffler.
  • the long hole may be formed of a polygon.
  • the long hole may be formed in an oval shape.
  • the suction port outlets may be formed in plural, and the plurality of suction port outlets may be formed in different shapes from each other.
  • the plurality of suction port outlets (132c) includes a first suction port outlet located in the center and a second suction port outlet located on the side, the first suction port outlet is formed in a pentagon, the second suction port The outlet may be formed in a square shape.
  • the plurality of suction port outlets (132c) includes a first suction port outlet located in the center and a second suction port outlet located on the side, the first suction port outlet is formed in an elliptical shape, the second suction port May be formed in a square.
  • the plurality of suction port outlets 132c include a first suction port outlet located at the center and a second suction port outlet positioned at the side, and the first suction port outlet is formed in a circular shape, and the second suction port May be formed in an oval shape.
  • the suction port outlets may be formed in plural, and the plurality of suction port outlets may be formed at different positions in the longitudinal direction of the suction port muffler.
  • the compression mechanism includes a plurality of compression chambers, and when the value obtained by dividing the total stroke volume of the plurality of compression chambers by the number of the plurality of compression chambers is a single stroke volume, the volume of the suction port muffler is the single stroke. It may be formed to be greater than or equal to 40% of the volume.
  • the volume of the suction port muffler may be formed to be less than or equal to 25% of the volume of the suction chamber.
  • the noise reduction means may be formed integrally with the casing.
  • the compressor according to the present invention a suction chamber, a discharge chamber and a casing having a suction port for guiding the refrigerant to the suction chamber; A compression mechanism for sucking and compressing the refrigerant in the suction chamber and discharging it into the discharge chamber; And noise reduction means for reducing the noise of the refrigerant flowing into the suction chamber, wherein the noise reduction means is formed integrally with the suction port, thereby reducing the cost required to form the noise reduction means, and noise reduction means By this, it is possible to suppress an increase in the weight of the compressor.
  • the noise reduction means is integrally formed with the suction port and the casing, it is possible to reduce the cost required when the noise reduction means is formed in the casing.
  • noise generated by the noise reduction means can be prevented.
  • noise reduction means attenuates sound waves, noise can be further reduced.
  • the refrigerant can be evenly distributed to the plurality of compression chambers.
  • FIG. 1 is a cross-sectional view showing a conventional compressor
  • Figure 2 is a cross-sectional view showing a noise reduction means in the compressor
  • Figure 3 is a cross-sectional view showing a compressor according to an embodiment of the present invention.
  • FIG. 4 is a front view showing the rear housing integrally formed with the noise reduction means in the compressor of Figure 3,
  • Figure 5 is a cross-sectional view showing the refrigerant flow at the outlet of the suction port when the refrigerant in the compressor of Figure 3 is small
  • FIG. 6 is a cross-sectional view showing the flow of refrigerant at the outlet of the suction port when the refrigerant in the compressor of FIG.
  • FIG. 7 is a front view showing a rear housing integrally formed with noise reduction means in a compressor according to another embodiment of the present invention.
  • FIG. 8 is a front view showing a rear housing integrally formed with noise reduction means in a compressor according to another embodiment of the present invention.
  • FIG. 9 is a front view showing a rear housing integrally formed with noise reduction means in a compressor according to another embodiment of the present invention.
  • FIG. 10 is a front view showing a rear housing integrally formed with noise reduction means in a compressor according to another embodiment of the present invention.
  • FIG. 11 is a cross-sectional view of FIG. 10.
  • Figure 3 is a cross-sectional view showing a compressor according to an embodiment of the present invention
  • Figure 4 is a front view showing a rear housing integrally formed with a noise reduction means in the compressor of Figure 3
  • Figure 5 is a compressor of Figure 3 It is a sectional view showing the flow of refrigerant at the outlet of the suction port when the amount of refrigerant is small
  • FIG. 6 is a sectional view showing the flow of refrigerant at the outlet of the suction port when the amount of refrigerant suction is high in the compressor of FIG.
  • the compressor according to an embodiment of the present invention, the casing 100, the rotating shaft 200 rotatably mounted to the casing 100, through the rotating shaft 200 It may include a compression mechanism (300) for compressing the refrigerant receiving the rotational force from a driving source (for example, an engine) (not shown).
  • a driving source for example, an engine
  • the casing 100 is provided on the cylinder block 110 in which the compression mechanism 300 is accommodated, the front housing 120 coupled to the front side of the cylinder block 110 and the rear side of the cylinder block 110. It may include a rear housing 130 to be coupled.
  • a shaft hole 112 into which the rotation shaft 200 is inserted may be formed at a center side of the cylinder block 110.
  • a piston 320 to be described later may be inserted into the outer circumferential side of the cylinder block 110 and a bore 114 forming a compression chamber together with the piston 320 may be formed.
  • the bore 114 is formed of n pieces so that the number of compression chambers is n, and the n bores 114 may be arranged along the circumferential direction of the cylinder block 110 around the shaft hole 112. .
  • the front housing 120 may be fastened to the cylinder block 110 on the opposite side of the rear housing 130 based on the cylinder block 110.
  • the cylinder block 110 and the front housing 120 may be fastened to each other to form a crankcase S4 between the cylinder block 110 and the front housing 120.
  • the swash plate 310 and the rotor, which will be described later, may be accommodated in the crankcase S4.
  • the rear housing 130 may be fastened to the cylinder block 110 on the opposite side of the front housing 120 based on the cylinder block 110.
  • the rear housing 130 may include a suction chamber S1 in which refrigerant to be introduced into the compression chamber is accommodated, and a discharge chamber S3 in which refrigerant discharged from the compression chamber is accommodated.
  • the rear housing 130 further includes a suction port 132 for guiding the refrigerant to the suction chamber S1 and noise reduction means for reducing the noise of the refrigerant flowing into the suction chamber S1,
  • the suction port 132 and the noise reduction means may be integrally formed.
  • the suction port 132 the suction port inlet 132a communicating with a refrigerant suction pipe (not shown) for guiding the refrigerant to be compressed into the casing 100
  • the suction port inlet 132a from the A suction port muffler 132b extending toward the suction chamber S1 and a suction port outlet 132c communicating the suction port muffler 132b and the suction chamber S1 may be included.
  • the suction port muffler (132b) is a space for attenuating the sound waves of the refrigerant flowing into the suction port muffler (132b), increasing the volume of the suction port muffler (132b) to increase the attenuation effect of the suction port inlet It may be formed extending from (132a) to the center of the suction chamber (S1).
  • the volume of the suction port muffler 132b may be preferably formed to be included in a predetermined range.
  • the suction port muffler 132b since the attenuation effect of the suction port muffler 132b increases as the volume of the suction port muffler 132b increases, when only the improvement of the attenuation effect of the suction port muffler 132b is considered, the suction port muffler 132b It may be desirable to form the volume of) as large as possible.
  • suction chamber S1 Reduces the sound wave of the refrigerant flowing into the suction chamber (S1) on a principle similar to that of the suction port muffler (132b), thereby reducing the effect of the suction port muffler (132b) as well as the damping effect of the suction chamber (S1).
  • the volume of the suction port muffler 132b is less than or equal to 25% of the volume of the suction chamber S1. That is, when the volume of the suction port muffler (132b) is greater than 25% of the volume of the suction chamber (S1), considering the attenuation effect of the suction port muffler (132b) and the attenuation effect of the suction chamber (S1) Since the attenuation effect is significantly reduced, it may be desirable that the volume of the suction port muffler 132b is less than or equal to 25% of the volume of the suction chamber S1.
  • the compression mechanism 300 includes a plurality of the compression chamber as described above, the entire stroke volume of the plurality of compression chambers (piston 320 is located in the bottom dead center piston in the volume of the compression chamber ( 320) is the value obtained by subtracting the volume of the compression chamber when it is located at the top dead center) divided by the number of the compression chambers as a single stroke volume, the attenuation effect of the suction port muffler 132b is the suction port muffler When the volume of 132b is less than 40% of the single stroke volume, it may be desirable that the volume of the suction port muffler 132b is greater than or equal to 40% of the single stroke volume.
  • the suction port outlet 132c may be formed at the center of the suction chamber S1. Thereby, each distance from the suction port outlet 132c to the plurality of compression chambers becomes equal to each other, and refrigerant discharged from the suction port outlet 132c can be evenly distributed to the plurality of compression chambers. .
  • the suction port outlet 132c so that the opening amount of the suction port outlet 132c is adjusted according to the refrigerant suction amount, that is, when the load of the compressor is increased, the suction port outlet 132c
  • the suction port muffler 132b may be formed as a long hole extending along the longitudinal direction. A more detailed description of this will be provided later.
  • the rotating shaft 200 is extended in one direction, one end is inserted into the cylinder block 110 (more precisely, the shaft hole 112 is rotatably supported, the other end penetrates the front housing 120)
  • the casing 100 protrudes to the outside and is connected to the driving source (not shown), and the middle part may be connected to the compressor mechanism 300.
  • the compression mechanism 300 sucks refrigerant from the suction chamber (S1) into the compression chamber, compresses the sucked refrigerant in the compression chamber, and discharges the compressed refrigerant from the compression chamber to the discharge chamber (S3). Can be formed.
  • the compression mechanism 300 is connected to the rotating shaft 200, the swash plate 310 is rotated in the interior of the crankcase (S4), the swash plate 310 is in communication with the inside of the bore 114 It may include a piston 320 reciprocating in.
  • the swash plate 310 is formed in a disc shape, and may be inclined to the rotation shaft 200 in the crankcase S4.
  • the piston 320 may be provided in n corresponding to the bore 114.
  • each piston 320 is one end inserted into the bore 114 and the other end extending from the one end to the opposite side of the bore 114 and connected to the swash plate 310 in the crankcase S4. It may include.
  • the valve chamber 400 for communicating and shielding the suction chamber (S1) and the discharge chamber (S3) with the compression chamber and the compressor to adjust the refrigerant discharge amount according to the load required
  • An inclination adjustment mechanism 500 for adjusting the inclination angle of the swash plate 310 with respect to the rotating shaft 200 may be further included.
  • the compression mechanism 300 is formed in a so-called variable capacity swash plate 310 type, but is not limited thereto. That is, for example, it may include a turning scroll that is pivotally moved by the driving motor and a fixed scroll that is engaged with the turning scroll, and the driving motor may be formed in a variable capacity scrolling type controlled by an inverter.
  • the rotating shaft 200 and the swash plate 310 may be rotated together.
  • the piston 320 may be reciprocated within the bore 114 by converting the rotational motion of the swash plate 310 into a linear motion.
  • the compression chamber communicates with the suction chamber S1 by the valve mechanism 400 and is shielded from the discharge chamber S3, so that the suction The refrigerant in the seal (S1) can be sucked into the compression chamber.
  • the noise of the refrigerant may be reduced by the noise reduction means before the refrigerant is sucked into the compression chamber. That is, the refrigerant flowing into the suction port muffler 132b from the refrigerant suction pipe (not shown) through the suction port inlet 132a is attenuated by sound waves inside the suction port muffler 132b, and thus the noise is primarily reduced.
  • the refrigerant, which is reduced, and whose noise is primarily reduced by the suction port muffler 132b flows into the suction chamber S1 from the suction port muffler 132b through the suction port outlet 132c.
  • the refrigerant introduced into the seal S1 is attenuated by sound waves inside the suction chamber S1, and the noise is secondarily reduced, and the refrigerant whose noise is primarily reduced by the suction chamber S1 is transferred to the compression chamber. Can be aspirated.
  • the compression chamber is shielded from the suction chamber S1 and the discharge chamber S3 by the valve mechanism 400, and the refrigerant in the compression chamber Can be compressed.
  • the compression chamber is shielded from the suction chamber (S1) by the valve mechanism 400 and communicates with the discharge chamber (S3), in the compression chamber
  • the compressed refrigerant may be discharged to the discharge chamber (S3).
  • the noise reduction means may be integrally formed with the suction port 132. That is, the suction port 132 may include the suction port muffler 132b. Thereby, the number of parts of the noise reduction means is reduced, the cost required to form the noise reduction means is reduced, and the weight of the compressor can be suppressed from being increased by the noise reduction means.
  • the noise reduction means may be integrally formed with the rear housing 130. That is, the suction port 132 is formed integrally with the rear housing 130, as described above, the suction port 132 may include the suction port muffler 132b.
  • the suction chamber (S1) is formed integrally with the rear housing 130, the suction chamber (S1) may be formed to reduce the noise of the refrigerant flowing into the suction chamber (S1). Accordingly, there is no need to separately fasten the noise reduction means to the rear housing 130, and the cost required to form the noise reduction means on the rear housing 130 can be reduced.
  • noise reduction means is integrally formed with the suction port 132 and the rear housing 130, noise can be prevented from being generated by the noise reduction means itself. That is, since the noise reduction means does not include driving parts such as the conventional valve core 20 and the elastic member 30, noise generated from movement of the driving parts can be prevented. In addition, since the noise reduction means is not relatively vibrated with respect to the suction port 132 and the rear housing 130, noise generated by the vibration can be prevented.
  • the noise reduction means does not simply adjust the amount of the noise source (refrigerant suction), but attenuates the noise source (sound wave of refrigerant), the noise of the refrigerant can be further reduced.
  • each distance between the plurality of compression chambers from the suction port outlet 132c may be formed at an equal level with each other. Accordingly, the refrigerant discharged from the suction port outlet 132c can be evenly distributed to the plurality of compression chambers.
  • the suction port outlet (132c) is formed in a long hole extending along the longitudinal direction (flow direction of refrigerant) of the suction port muffler (132b).
  • the same effect as the opening amount of the suction port outlet 132c is adjusted according to the refrigerant suction amount. That is, when the load of the compressor is increased, the suction port outlet 132c can be prevented from acting as a bottle neck.
  • the flow rate of the refrigerant may be slow. Accordingly, as illustrated in FIG. 5, the refrigerant of the suction port muffler 132b does not go far in the flow direction of the refrigerant and may flow to the suction chamber S1 through a portion of the suction port outlet 132c. have.
  • the flow rate of the refrigerant may be fast. Accordingly, as illustrated in FIG. 6, the refrigerant in the suction port muffler 132b may go far in the direction of flow of the refrigerant and flow into the suction chamber S1 through all of the suction port outlet 132c. .
  • the suction port outlet (132c) is formed differently from the present embodiment (for example, the inner diameter is formed in a circle smaller than the long axis length of the long hole of the present embodiment, or in a direction perpendicular to the longitudinal direction of the suction port muffler When formed as an elongated hole), during high load operation, some of the refrigerant in the suction port muffler 132b is blocked by the wall around the suction port outlet 132c, and the amount of refrigerant flowing into the suction chamber S1 is less than the required amount. Can.
  • the suction port outlet 132c is formed as a long hole extending along the longitudinal direction (refrigerant flow direction) of the suction port muffler 132b, the suction port outlet 132c during high load operation ) Can have the same effect as the opening amount of the suction port outlet 132c is increased during low load operation, and the suction port outlet 132c may not lower the refrigerant suction amount during high load operation.
  • the shape of the suction port outlet 132c that can obtain the effect of adjusting the opening amount of the suction port outlet 132c according to the refrigerant suction amount is not limited to this embodiment.
  • the suction port outlet 132c is formed as one, but as shown in FIGS. 7 to 11, a plurality of suction port outlets 132c are formed, and the plurality of suction port outlets 132c are formed.
  • the longitudinal direction of the suction port muffler (132b) may be formed at different positions from each other.
  • the plurality of suction port outlets 132c can reduce the noise of the refrigerant together with the suction port muffler 132b and the suction chamber S1. have.
  • the plurality of suction port outlets 132c may be formed in different shapes from each other. That is, the suction port outlet 132c located at the center of the plurality of suction port outlets 132c is referred to as a first suction port outlet, and the suction port outlet 132c located on the side of the plurality of suction port outlets 132c is located.
  • the first suction port outlet may be formed of one pentagonal long hole, and the second suction port outlet may be formed in a square shape.
  • the first suction port outlet may be formed in three circles, and the second suction port outlet may be formed in an elliptical shape or a circular shape having a larger diameter than the first suction port outlet.
  • the first suction port outlet may be formed in six circles, and the second suction port outlet may be formed in an elliptical shape or a circular shape having a larger diameter than the first suction port outlet.
  • the first suction port outlet may be formed of one elliptical long hole, and the second suction port outlet may be formed in a square shape. In this case, the noise reduction effect by the plurality of suction port outlets 132c may be further improved.

Abstract

La présente invention concerne un compresseur comprenant : un boîtier ayant une chambre d'aspiration, une chambre de décharge et un orifice d'aspiration pour guider un réfrigérant vers la chambre d'aspiration; un dispositif de compression pour aspirer et comprimer le réfrigérant de la chambre d'aspiration et le décharger vers la chambre de décharge; et un moyen de réduction de bruit pour réduire le bruit du réfrigérant s'écoulant dans la chambre d'aspiration, le moyen de réduction de bruit pouvant être formé d'un seul tenant avec l'orifice d'aspiration. Par conséquent, les coûts nécessaires à la formation du moyen de réduction de bruit sont réduits, le poids du compresseur ne peut augmenter en raison du moyen de réduction de bruit, les coûts nécessaires à la formation du moyen de réduction de bruit dans le boîtier sont réduits, et le bruit causé par le moyen de réduction de bruit peut être évité d'être généré.
PCT/KR2020/000843 2019-01-21 2020-01-17 Compresseur WO2020153664A1 (fr)

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KR1020190007317A KR102596317B1 (ko) 2019-01-21 2019-01-21 압축기
KR10-2019-0007317 2019-01-21

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WO2020153664A1 true WO2020153664A1 (fr) 2020-07-30

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JPH11280646A (ja) * 1998-03-30 1999-10-15 Toyota Autom Loom Works Ltd 圧縮機における冷媒吸入構造
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US5971716A (en) * 1995-06-09 1999-10-26 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor having a muffler and a capacity control valve mounted thereto
JPH11280646A (ja) * 1998-03-30 1999-10-15 Toyota Autom Loom Works Ltd 圧縮機における冷媒吸入構造
KR20000062480A (ko) * 1999-03-01 2000-10-25 이시카와 타다시 압축기의 흡입 머플러 구조
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