KR100304556B1 - Structure for reducing noise of rotary compressor - Google Patents

Structure for reducing noise of rotary compressor Download PDF

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Publication number
KR100304556B1
KR100304556B1 KR1019980022951A KR19980022951A KR100304556B1 KR 100304556 B1 KR100304556 B1 KR 100304556B1 KR 1019980022951 A KR1019980022951 A KR 1019980022951A KR 19980022951 A KR19980022951 A KR 19980022951A KR 100304556 B1 KR100304556 B1 KR 100304556B1
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South Korea
Prior art keywords
hole
noise reduction
discharge port
inner diameter
cylinder
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KR1019980022951A
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Korean (ko)
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KR19990023160A (en
Inventor
김종목
서홍석
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구자홍
엘지전자주식회사
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Publication of KR19990023160A publication Critical patent/KR19990023160A/en
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Publication of KR100304556B1 publication Critical patent/KR100304556B1/en

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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
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

PURPOSE: A noise reduction structure for hermetic rotary compressor is provided to reduce pulse noise caused from the discharged gas, while improving volumetric efficiency of the compressor by reducing the loss caused due to the re-expansion of refrigerant gas. CONSTITUTION: A compression space(P) is formed to allow a rolling piston(9) to eccentrically rotate within the compression space. The compression space has a refrigerant gas inlet port formed at the inner periphery of the compression space, and a refrigerant outlet port(8a) the side surface of the compression space. A cylinder(8) is coupled with a vane which elastically contacts the rolling piston between the refrigerant inlet port and refrigerant outlet port so as to divide the interior of the cylinder into a suction chamber and a compression chamber. A noise reduction hole(H) is formed to be communicated to the refrigerant outlet port. The noise reduction hole is constituted by a first hole(8d) overlapped to the refrigerant outlet port and a second hole(8e) having an inner diameter smaller than the inner diameter of the first hole. The first and second holes are connected with each other in the lengthwise direction of the cylinder.

Description

밀폐형 회전식 압축기의 소음저감구조{STRUCTURE FOR REDUCING NOISE OF ROTARY COMPRESSOR}Noise reduction structure of hermetic rotary compressor {STRUCTURE FOR REDUCING NOISE OF ROTARY COMPRESSOR}

본 발명은 밀폐형 회전식 압축기에 관한 것으로, 특히 냉매가스가 압축되어 토출되는 과정에서 발생되는 토출가스의 맥동음을 저감시킬 수 있도록 한 밀폐형 회전식 압축기의 소음저감구조에 관한 것이다.The present invention relates to a hermetic rotary compressor, and more particularly, to a noise reduction structure of a hermetic rotary compressor to reduce pulsation noise of a discharge gas generated in a process in which refrigerant gas is compressed and discharged.

일반적으로 밀폐형 회전식 압축기는, 도 1a, 1b에 도시한 바와 같이, 소정의 내부체적을 갖는 밀폐용기(1)의 내부에 설치되어 구동력을 발생시키는 전동기구부와 상기 전동기구부의 구동력을 전달받아 냉매가스를 압축하는 압축기구부로 구성된다.Generally, the hermetic rotary compressor is installed in the hermetic container 1 having a predetermined internal volume as shown in FIGS. 1A and 1B and receives a driving force of the electric mechanism unit generating the driving force and the driving force of the electric mechanism unit. Compressor unit for compressing the configuration.

상기 전동기구부는 밀폐용기(1)내벽에 결합되는 고정자(2)와, 상기 고정자(2)의 내부에 삽입되어 회전하는 회전자(3)을 포함하여 구성된다.The electric machine part includes a stator 2 coupled to the inner wall of the sealed container 1, and a rotor 3 inserted into the stator 2 to rotate.

상기 압축기구부는 상기 회전자(3)의 내경에 압입되고 하부에 편심부(4a)가 형성된 회전축(4)과, 상기 회전축의 편심부(4a)가 삽입되는 원통형의 압축 공간(P)을 구비하여 형성되어 상기 편심부(4a)를 감싸며 설치되는 실린더(8)와, 상기 회전축(4)에 삽입되어 실린더(8)의 상,하부에 각각 결합되어 볼트(7)에 의해 체결되는 상부베어링(5) 및 하부베어링(6)과, 상기 회전축(4)의 편심부(4a)에 삽입됨과 더불어 실린더 압축 공간(P)의 내주면을 접하면서 자전 및 공전하는 롤링피스톤(9)과, 상기 실린더(8)의 일측에 직선운동 가능하게 삽입되어 상기 롤링피스톤(9)의 외주면과 슬라이딩 접촉되면서 실린더 압축 공간(P)을 흡입실(a)과 압축실(b)로 분리하는 베인(10)을 포함하여 구성된다.The compression mechanism has a rotary shaft (4) press-fitted into the inner diameter of the rotor (3) and an eccentric (4a) formed at the bottom, and a cylindrical compression space (P) into which the eccentric (4a) of the rotary shaft is inserted And an upper bearing which is formed to surround the eccentric portion 4a and is installed to be inserted into the rotary shaft 4 and coupled to the upper and lower portions of the cylinder 8, respectively, and fastened by bolts 7. 5) and the lower bearing 6, the rolling piston 9 which is inserted into the eccentric portion 4a of the rotary shaft 4 and rotates and rotates while contacting the inner circumferential surface of the cylinder compression space P, and the cylinder ( 8) is inserted into one side of the linear movement so that the sliding contact with the outer peripheral surface of the rolling piston (9) includes a vane (10) for separating the cylinder compression space (P) into the suction chamber (a) and the compression chamber (b) It is configured by.

그리고, 상기 베인(10)에 의해 압축실(b)을 이루는 실린더(8)의 일측에 압축된 냉매가스를 토출시키는 토출포트(8a)가 형성되고, 상기 상부베어링(5)의 일측에 상기 토출포트(8a)와 연통되게 토출공(5a)이 형성되어 있다.In addition, a discharge port 8a for discharging the compressed refrigerant gas is formed at one side of the cylinder 8 constituting the compression chamber b by the vane 10, and the discharge is at one side of the upper bearing 5. The discharge hole 5a is formed in communication with the port 8a.

상기 실린더(8)의 흡입실(a)에는 냉매가스가 실린더(8)내부로 유입되는 흡입구(8b)가 형성되고, 상기 흡입구(8b)는 밀폐용기(1)의 측부에 설치되는 어큐뮬레이터(11) 및 냉매유입관(12)에 의해 연결되어 있다.An intake port 8b through which refrigerant gas flows into the cylinder 8 is formed in the suction chamber a of the cylinder 8, and the intake port 8b is an accumulator 11 installed at the side of the sealed container 1. ) And a refrigerant inlet pipe 12.

상기 밀폐용기(1)의 저면에는 슬라이딩이 일어나는 부품에 공급되는 오일이 채워져 있고, 상기 밀폐용기(1)의 상부에는 압축된 냉매가스가 외부로 토출되는 토출관(14)이 설치되어 있다.The bottom surface of the hermetic container 1 is filled with oil supplied to a sliding element, and an upper part of the hermetic container 1 is provided with a discharge tube 14 through which compressed refrigerant gas is discharged to the outside.

미설명 부호 15는 상부베어링의 상면에 결합되어 토출공을 개폐시키는 토출밸브이며, 미설명 부호 16은 토출밸브의 움직임을 한정 지지하는 리테이너이고, 미설명 부호 17은 소음기이며, 상기 소음기는 상부베어링이나 하부베어링에 결합되어 토출소음을 저감시키게 된다.Reference numeral 15 is a discharge valve coupled to the upper surface of the upper bearing to open and close the discharge hole, reference numeral 16 is a retainer for limiting the movement of the discharge valve, reference numeral 17 is a silencer, the silencer is an upper bearing Or is coupled to the lower bearing to reduce the discharge noise.

상기한 바와 같은 압축기는 인가되는 전류에 의해 회전자(3)가 회전하면서 회전축(4)을 회전시키게 되면, 회전축(4)의 회전에 의해 회전축의 편심부(4a)에 결합되어 있는 롤링피스톤(9)이 베인(10)과 접촉된 상태에서 실린더 압축 공간(P)에서 편심 회전하게 되고, 상기 롤링피스톤(9)의 편심 회전에 의한 실린더 압축 공간(P)의 체적변화로 저온저압의 냉매가스가 냉매유입관(12)과 흡입구(8b)를 통해 실린더(8)내부로 흡입되어 고온고압의 상태로 압축되며 그 압축된 고온고압의 냉매가스는 토출포트(8a) 및 토출공(5a)을 통해 실린더(8) 외부로 토출되며, 토출된 냉매가스는 밀폐용기(1)의 상부에 설치된 토출관(14)을 통해 밀폐용기(1)외부로 토출된다.As described above, when the rotor 3 rotates while the rotor 3 rotates by an applied current, the compressor is connected to the eccentric portion 4a of the rotation shaft by the rotation of the rotation shaft 4 ( 9) is eccentric rotation in the cylinder compression space (P) in contact with the vane 10, the refrigerant gas of low temperature low pressure due to the volume change of the cylinder compression space (P) by the eccentric rotation of the rolling piston (9) Is sucked into the cylinder (8) through the refrigerant inlet pipe (12) and the suction port (8b) and compressed to a state of high temperature and high pressure, the compressed high-temperature high-pressure refrigerant gas is discharged to the discharge port (8a) and the discharge hole (5a) Discharged to the outside of the cylinder (8), the discharged refrigerant gas is discharged to the outside of the sealed container (1) through a discharge pipe 14 installed on the top of the sealed container (1).

한편, 상기 전동기구부의 구동력을 전달받아 압축기구부에서 냉매가스를 흡입하여 압축하고 토출시키는 과정에서, 높은 맥동소음을 발생시키게 되는데 이를 위한 종래 소음저감구조는 다음과 같다.On the other hand, in the process of receiving, compressing and discharging the refrigerant gas in the compressor mechanism by receiving the driving force of the electric mechanism, high pulsation noise is generated. The conventional noise reduction structure for this is as follows.

종래 밀페형 회전식 압축기의 소음저감구조는, 도 1b, 1c에 도시한 바와 같이, 실린더(8)의 압축실측에 형성되어 압축된 냉매가스가 토출되는 토출포트(8a)의 측부에 일정한 체적을 갖는 원통형의 소음저감방(8c)이 형성되어 이루어진다. 상기 소음저감방(8c)은 소정의 내경과 깊이를 갖도록 형성되며, 상기 토출포트(8a)와 연통되도록 형성되어 있다.The noise reduction structure of the conventional hermetic rotary compressor has a constant volume on the side of the discharge port 8a, which is formed in the compression chamber side of the cylinder 8 and discharges the compressed refrigerant gas, as shown in FIGS. 1B and 1C. A cylindrical noise reduction chamber 8c is formed. The noise reduction chamber 8c is formed to have a predetermined inner diameter and depth, and is formed to communicate with the discharge port 8a.

상기 구조는 실린더의 압축 공간 압축실(b)에서 압축된 냉매가스가 토출포트(8a)를 통해 상부베어링의 토출공(5a)을 통해 토출되는 과정에서, 도 2에 도시한 바와 같이, 냉매가스가 소음저감방(8c)을 거쳐 토출됨에 의해 특정 주파수 대역의 소음을 상쇄시켜 맥동소음을 저감시키게 된다. 상기 특정 주파수 대역의 소음은 소음저감방의 체적 요소인 단면적과 깊이에 의해 설정된다.In the above structure, the refrigerant gas compressed in the compression space compression chamber (b) of the cylinder is discharged through the discharge hole (5a) of the upper bearing through the discharge port (8a), as shown in Figure 2, the refrigerant gas By being discharged through the noise reduction room 8c, the noise of a specific frequency band is canceled to reduce pulsation noise. The noise of the specific frequency band is set by the cross-sectional area and the depth, which are the volume components of the noise reduction room.

그러나, 상기한 바와 같은 종래의 소음저감구조는 압축기구부의 조립과정이나 실린더(8)의 제작과정에서, 상기 토출포트(8a)와 소음저감방(8c)을 연통시키는 입구부분이 막히거나 비정상적으로 줄어들 경우 냉매가스가 소음저감방(8c)으로 유입되지 못하거나 입구가 작아 소음저감방(8c)의 역할을 제대로 하지 못하게 된다. 만일,토출포트(8a)와 소음저감방(8c)을 연통시키는 입구부분의 크기를 크게 하기 위하여 소음저감방(8c)의 내경을 크게 할 경우 소음저감방(8c)의 크기가 크게 되고, 상기 소음저감방(8c)의 크기가 크게 되면 소음저감방(8c)을 거쳐 토출되는 냉매가스가 미쳐 토출되지 못하고 압축실(b)로 재유입되어 재팽창 손실을 증가시키게 된다.However, in the conventional noise reduction structure as described above, in the assembling process of the compression mechanism or the manufacturing process of the cylinder 8, the inlet portion communicating the discharge port 8a and the noise reduction chamber 8c is blocked or abnormally. If it is reduced, the refrigerant gas does not flow into the noise reduction room 8c or the inlet is small so that the role of the noise reduction room 8c may not be properly performed. If the inner diameter of the noise reduction chamber 8c is increased in order to increase the size of the inlet portion communicating with the discharge port 8a and the noise reduction chamber 8c, the size of the noise reduction chamber 8c becomes large. When the size of the noise reduction room 8c is increased, the refrigerant gas discharged through the noise reduction room 8c may not be discharged so as to flow back into the compression chamber b to increase the re-expansion loss.

따라서 본 발명의 목적은 냉매가스의 재팽창 손실에 의한 성능저하를 방지함과 더불어 맥동소음을 최소화할 수 있도록 한 밀폐형 회전식 압축기의 소음저감구조를 제공함에 있다.Accordingly, an object of the present invention is to provide a noise reduction structure of a hermetic rotary compressor to prevent performance degradation due to re-expansion loss of refrigerant gas and to minimize pulsation noise.

도 1a는 일반적인 밀폐형 회전식 압축기를 도시한 종단면도,Figure 1a is a longitudinal sectional view showing a typical hermetic rotary compressor,

도 1b는 상기 밀폐형 회전식 압축기의 횡단면도,1b is a cross-sectional view of the hermetic rotary compressor,

도 1c는 종래 밀폐형 회전식 압축기의 소음저감구조를 도시한 단면도,Figure 1c is a cross-sectional view showing a noise reduction structure of a conventional hermetic rotary compressor,

도 2는 종래 밀폐형 회전식 압축기의 소음저감구조를 모델링하여 도시한 구성도,2 is a configuration diagram showing a model of the noise reduction structure of a conventional hermetic rotary compressor;

도 3a는 본 발명의 밀폐형 회전식 압축기 소음저감구조를 도시한 평면도,Figure 3a is a plan view showing a closed rotary compressor noise reduction structure of the present invention,

도 3b는 본 발명의 밀폐형 회전식 압축기 소음저감구조를 도시한 정단면도,Figure 3b is a front sectional view showing a closed rotary compressor noise reduction structure of the present invention,

도 4는 본 발명의 밀폐형 회전식 압축기 소음저감구조에서 소음저감홀의 변형예를 도시한 단면도,Figure 4 is a cross-sectional view showing a modification of the noise reduction hole in the closed rotary compressor noise reduction structure of the present invention,

도 5는 본 발명의 밀폐형 회전식 압축기 소음저감구조의 소음저감홀과 토출포트의 겹침 상태 정도를 나타낸 평면도,5 is a plan view showing the overlapping state of the noise reduction hole and the discharge port of the closed rotary compressor noise reduction structure of the present invention;

도 6은 본 발명의 밀폐형 회전식 압축기 소음저감구조에서 소음저감홀의 치수 상태를 나타낸 단면도,Figure 6 is a cross-sectional view showing the dimensional state of the noise reduction hole in the closed rotary compressor noise reduction structure of the present invention,

도 7은 본 발명의 밀폐형 회전식 압축기 소음저감구조를 모델링하여 도시한 구성도,Figure 7 is a schematic view showing the modeling the closed rotary compressor noise reduction structure of the present invention,

도 8은 본 발명의 밀폐형 회전식 압축기 소음저감구조에서 토출포트와 소음저감홀의 겹침 치수에 따른 소음 발생 상태를 도시한 그래프,8 is a graph illustrating a noise generation state according to overlapping dimensions of a discharge port and a noise reduction hole in the closed rotary compressor noise reduction structure according to the present invention;

도 9는 종래의 밀폐형 회전식 압축기 소음저감구조에서 발생되는 소음 상태를 도시한 그래프,9 is a graph showing a noise state generated in the conventional closed rotary compressor noise reduction structure,

도 10에서 12는 본 발명의 밀폐형 회전식 압축기의 소음저감구조에서 소음저감홀의 치수에 따른 범위내에서, 설정된 값으로 실험을 통해 발생되는 소음 상태를 각각 도시한 그래프.10 to 12 are graphs showing the noise state generated through the experiment to the set value, respectively, within the range according to the dimensions of the noise reduction hole in the noise reduction structure of the hermetic rotary compressor of the present invention.

(도면의 주요부분에 대한 부호의 설명)(Explanation of symbols on the main parts of drawing

8 ; 실린더 8a ; 토출포트8 ; Cylinder 8a; Discharge port

8b ; 흡입구 8d ; 제1홀8b; Inlet 8d; Hall 1

8e ; 제2홀 8f ; 제3홀8e; Second hole 8f; Hall 3

9 ; 롤링피스톤 10 ; 베인9; Rolling piston 10; Bain

a ; 흡입실 b ; 압축실a; Suction chamber b; Compression chamber

H ; 소음저감홀 P ; 압축 공간H; Noise reduction hole P; Compression space

상기한 바와 같은 본 발명의 목적을 달성하기 위하여 내부에 롤링피스톤이 편심 회전하는 압축 공간이 형성되고 상기 압축 공간의 내주면에 냉매가스가 유입되는 흡입구가 형성되며 그 측부에 압축된 냉매가스가 토출되는 토출포트가 형성되고 상기 흡입구와 토출포트사이에 상기 롤링피스톤에 탄성적으로 접촉되어 내부를 흡입실과 압축실로 나누는 베인이 결합되어 이루어진 실린더를 구비한 밀폐형 회전식 압축기에 있어서; 상기 토출포트와 연통되도록 토출포트의 측부에 내경이 다른 원통형 홀이 상기 실린더의 길이 방향으로 점차 작아지도록 다단으로 이어진 형태의 소음저감홀이 형성되어 이루어짐을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조가 제공된다.In order to achieve the object of the present invention as described above, a compression space in which a rolling piston is eccentrically rotated is formed therein, and an inlet port through which refrigerant gas is introduced is formed in the inner circumferential surface of the compression space, and the compressed refrigerant gas is discharged to the side thereof. A sealed rotary compressor having a cylinder having a discharge port formed therein and a vane for elastically contacting the rolling piston between the suction port and the discharge port and dividing an interior into a suction chamber and a compression chamber; The noise reduction structure of the hermetic rotary compressor is characterized in that the cylindrical hole having a different inner diameter is formed at the side of the discharge port so as to communicate with the discharge port, and the noise reduction hole is formed in a multi-stage form so as to gradually decrease in the longitudinal direction of the cylinder. Is provided.

상기 소음저감홀은 상기 토출포트와 연통되도록 겹쳐지는 제1홀과, 상기 제1홀보다 내경이 작은 제2홀로 형성됨을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조가 제공된다.The noise reduction hole is provided with a noise reduction structure of a hermetic rotary compressor, characterized in that it is formed of a first hole overlapping to communicate with the discharge port, and a second hole having a smaller inner diameter than the first hole.

상기 소음저감홀은 상기 토출포트와 연통되도록 겹쳐지는 제1홀과 상기 제1홀보다 내경이 작은 제2홀과, 상기 제2홀보다 내경이 작은 제3홀로 형성됨을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조가 제공된다.The noise reduction hole may include a first hole overlapping to communicate with the discharge port, a second hole having an inner diameter smaller than the first hole, and a third hole having an inner diameter smaller than the second hole. Noise reduction structure is provided.

상기 제1홀과 토출포트의 겹침 영역의 폭은 제1홀 지름의 0.1 ~ 0.2임을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조가 제공된다.The noise reduction structure of the hermetic rotary compressor is characterized in that the width of the overlapping area of the first hole and the discharge port is 0.1 to 0.2 of the diameter of the first hole.

상기 제1홀의 내경(D)과 제2홀의 내경(d)과의 비(d/D)는 0.5≤d/D≤0.8 이고, 소음저감홀의 전체 깊이(P)와 제1홀의 깊이(P')의 비(P'/P)는 0.1≤P'/P≤0.5 임을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조가 제공된다.The ratio d / D between the inner diameter D of the first hole and the inner diameter d of the second hole is 0.5 ≦ d / D ≦ 0.8, and the total depth P of the noise reduction hole and the depth P ′ of the first hole are The ratio P '/ P) is 0.1? P' / P≤0.5, and the noise reduction structure of the hermetic rotary compressor is provided.

이하, 본 발명의 밀폐형 회전식 압축기의 소음저감구조를 첨부도면에 도시한 실시예에 따라 설명하면 다음과 같다.Hereinafter, the noise reduction structure of the hermetic rotary compressor of the present invention will be described according to the embodiment shown in the accompanying drawings.

본 발명의 밀폐형 회전식 압축기 소음저감구조는, 도 3a, 3b에 도시한 바와 같이, 내부에 롤링피스톤(9)이 편심 회전하는 압축 공간(P)이 형성되고, 상기 압축 공간(P)의 내주면에 냉매가스가 유입되는 흡입구(8b)가 형성되며, 그 측부에 압축된 냉매가스가 토출되는 토출포트(8a)가 형성되고, 상기 흡입구(8b)와 토출포트(8a)사이에 상기 롤링피스톤(9)에 탄성적으로 접촉되어 내부를 흡입실(a)과 압축실(b)로 나누는 베인(10)이 결합되어 이루어진 실린더(8)에서, 상기 토출포트(8a)와 연통되도록 토출포트(8a)의 측부에 위치하는 실린더(8)에 직경이 다른 원통형 홀이 다단으로 이어진 형태의 소음저감홀(H)이 형성되어 이루어진다.In the closed rotary compressor noise reduction structure of the present invention, as shown in FIGS. 3A and 3B, a compression space P in which the rolling piston 9 is eccentrically rotated is formed therein, and an inner peripheral surface of the compression space P is formed. A suction port 8b through which the refrigerant gas flows is formed, and a discharge port 8a through which the compressed refrigerant gas is discharged is formed at a side thereof, and the rolling piston 9 is disposed between the suction port 8b and the discharge port 8a. In the cylinder (8) formed by coupling the vane (10) elastically in contact with the suction chamber (a) and the compression chamber (b), the discharge port (8a) so as to communicate with the discharge port (8a) In the cylinder (8) located on the side of the cylindrical hole of different diameters is made of a noise reduction hole (H) of the form of a multi-stage.

상기 토출포트(8a)는 종래와 같이 실린더(8) 압축 공간(P)을 이루는 상면 모서리에 곡면홈을 이루도록 형성되며, 상기 소음저감홀(8d)은 실린더(8)의 상면에 형성된다.The discharge port 8a is formed to form a curved groove in the upper edge of the cylinder 8 compression space P as in the prior art, the noise reduction hole (8d) is formed on the upper surface of the cylinder (8).

상기 소음저감홀(H)은 상기 토출포트(8a)와 연통되도록 겹쳐지는 제1홀(8d)과, 상기 제1홀(8d)보다 내경이 작은 제2홀(8e)로 형성된다.The noise reduction hole H is formed of a first hole 8d overlapping with the discharge port 8a and a second hole 8e having an inner diameter smaller than that of the first hole 8d.

또한, 상기 소음저감홀(H)의 변형예로서, 도 4에 도시한 바와 같이, 상기 소음저감홀(H)은 상기 토출포트(8a)와 연통되도록 겹쳐지는 제1홀(8d)과 상기 제1홀(8d)보다 내경이 작은 제2홀(8e)과, 상기 제2홀(8e)보다 내경이 작은 제3홀(8f)로 형성된다.Further, as a modification of the noise reduction hole H, as shown in FIG. 4, the noise reduction hole H overlaps the first hole 8d and the first hole so as to communicate with the discharge port 8a. A second hole 8e having an inner diameter smaller than the one hole 8d and a third hole 8f having an inner diameter smaller than the second hole 8e are formed.

상기 제1홀(8d)과 토출포트(8a)의 겹침 영역의 폭(C)은, 도 5에 도시한 바와 같이, 제1홀(8d) 지름의 0.1 ~ 0.2의 범위에서 형성된다.The width C of the overlapping region of the first hole 8d and the discharge port 8a is formed in the range of 0.1 to 0.2 of the diameter of the first hole 8d.

그리고, 도 6에 도시한 바와 같이, 상기 제1홀(8d)의 내경(D)과 제2홀(8e)의 내경(d)의 비(d/D)가 0.5≤d/D≤0.8 이고, 소음저감홀(H)의 전체 깊이(P)와 제1홀(8d)의 깊이(P')의 비(P'/P)는 0.1≤P'/P≤0.5 범위에서 형성된다.6, the ratio d / D of the inner diameter D of the first hole 8d and the inner diameter d of the second hole 8e is 0.5 ≦ d / D ≦ 0.8. The ratio P '/ P between the total depth P of the noise reduction hole H and the depth P' of the first hole 8d is formed in the range of 0.1? P '/ P? 0.5.

상기 소음저감홀(H)의 단과 단에 의해 형성되는 모서리 부분에는 모따기하여 경사면을 이루도록 형성됨이 바람직하다.It is preferable that the edge portions formed by the ends and the ends of the noise reduction hole H are formed to form an inclined surface by chamfering.

이하, 본 발명의 밀폐형 회전식 압축기 소음저감구조의 작용효과를 설명하면 다음과 같다.Hereinafter, the operational effects of the hermetic rotary compressor noise reduction structure of the present invention will be described.

먼저, 상기 실린더(8)의 내경(P)에는 회전축의 편심부(4a)에 삽입되는 롤링피스톤(9)이 삽입되며, 상기 실린더(8)의 상,하면에는 상,하부베어링(5,6)이 각각 결합된다. 상기 실린더(8)의 상면에 결합되는 상부베어링(5)에는 실린더(8)에 결합시 상기 토출포트(8a)와 연통되는 토출공(5a)이 형성되어 있다.First, a rolling piston 9 inserted into an eccentric portion 4a of a rotating shaft is inserted into an inner diameter P of the cylinder 8, and upper and lower bearings 5 and 6 are disposed on upper and lower surfaces of the cylinder 8. ) Are respectively combined. The upper bearing 5 coupled to the upper surface of the cylinder 8 has a discharge hole 5a communicating with the discharge port 8a when coupled to the cylinder 8.

상기한 바와 같은 구조는 회전축(4)의 회전에 의해 회전축의 편심부(4a)에 결합되어 있는 롤링피스톤(9)이 베인(10)과 접촉된 상태에서 실린더(8)내부에서 편심 회전하게 되고, 상기 롤링피스톤(9)의 편심 회전에 의한 체적변화로 저온저압의 냉매가스가 흡입구(8b)를 통해 실린더(8)의 압축 공간(P)내부로 흡입되어 고온고압의 상태로 압축되며 압축된 고온고압의 냉매가스는 토출포트(8a) 및 상부베어링의 토출공(5a)을 통해 실린더(8) 외부로 토출되는 과정을 반복하게 된다.As described above, the rolling piston 9 coupled to the eccentric portion 4a of the rotary shaft 4 by the rotation of the rotary shaft 4 is eccentrically rotated inside the cylinder 8 in contact with the vane 10. The refrigerant gas of low temperature and low pressure is sucked into the compression space P of the cylinder 8 through the suction port 8b due to the volume change by the eccentric rotation of the rolling piston 9, and is compressed and compressed to a state of high temperature and high pressure. The high temperature and high pressure refrigerant gas is repeatedly discharged to the outside of the cylinder 8 through the discharge port 8a and the discharge hole 5a of the upper bearing.

상기 압축 공간(P)에서 압축된 냉매가스가 토출포트(8a) 및 토출공(5a)을 통해 토출되는 과정에서, 도 7에 도시한 바와 같이, 토출포트(8a)의 측부에 형성된 소음저감홀(H)로 거쳐 토출됨에 의해 특정 주파수 대역의 소음을 상쇄시켜 맥동소음을 저감시키게 된다.In the process of discharging the refrigerant gas compressed in the compression space P through the discharge port 8a and the discharge hole 5a, as illustrated in FIG. 7, a noise reduction hole formed at the side of the discharge port 8a is provided. By discharging through (H), the noise of a specific frequency band is canceled to reduce pulsation noise.

본 발명은 소음저감홀(H)을 직경이 다른 홀을 다단으로 형성하게 되므로, 종래의 단일 내경 형태의 홀로 형성된 소음저감방(8c)과 동일한 체적과 깊이내에서 토출포트(8a)와 제1홀(8d)과의 연통된 단면적을 충분히 확보하게 되어 연통된 부분이 막히거나 크기가 작아 소음저감홀(H)의 역할을 제대로 하지 못하는 것을 방지하게 될 뿐만 아니라 기존의 소음저감홀(H)보다 작은 체적으로도 냉매가스의 유로 단면적을 변화시키게 되므로 효과적으로 맥동 소음을 저감시키게 되고, 또한 소음저감방(8c)에 유입된 냉매가스의 재팽창에 의한 손실을 방지하게 된다.According to the present invention, since the noise reduction hole H is formed in multiple stages with holes having different diameters, the discharge port 8a and the first volume within the same volume and depth as the noise reduction chamber 8c formed of the conventional single inner diameter type hole. A sufficient cross-sectional area of communication with the hole 8d is secured to prevent the communication part from clogging or having a small size, thereby preventing the proper function of the noise reduction hole H, as well as the existing noise reduction hole H. Since the channel cross-sectional area of the refrigerant gas is changed even in a small volume, the pulsation noise is effectively reduced, and the loss due to the re-expansion of the refrigerant gas introduced into the noise reduction chamber 8c is prevented.

상기 소음저감홀(H)로 유입된 냉매가스는 직경이 점점 작아지는 제1홀(8d)과 제2홀(8e)로 유입되면서 맥동이 완화되며, 이때 단과 단에 의해 이루어지는 모서리 부분에 경사면이 형성되어 홀에서 다른 홀로 냉매가스의 유입이 원할하게 된다.The refrigerant gas introduced into the noise reduction hole (H) is alleviated by pulsation as it enters the first hole (8d) and the second hole (8e), the diameter of which is gradually reduced, and the inclined surface is formed at the corners formed by the end and the end. It is formed to facilitate the flow of refrigerant gas from one hole to another.

도 8은 동일 주파수 상태에서, 토출포트(8a)와 소음저감홀(H)이 연통되는 입구 단면적에 따른 소음저감 효과를 실험 분석하여 나타낸 그래프이다.FIG. 8 is a graph illustrating an experimental analysis of the noise reduction effect according to the inlet cross-sectional area where the discharge port 8a and the noise reduction hole H communicate with each other in the same frequency state.

도 9는 종래의 구조에서 발생되는 소음 상태를 그래프로 도시한 것이다.9 is a graph illustrating a noise state generated in a conventional structure.

그리고, 도 10에서 12는 제1홀(8d)의 내경(D)과 제2홀(8e)의 내경(d)의 비(d/D)가 0.5≤d/D≤0.8 이고, 소음저감홀(H)의 전체 깊이(P)와 제1홀(8d)의 깊이(P')의 비(P'/P)가 0.1≤P'/P≤0.5인 범위내에서, 설정된 값으로 실험을 통해 발생되는 소음 상태를 그래프로 도시한 것이다. 이에 도시된 바와 같이, 주파수 대역 1.5KHz ~ 2.5KHz 범위에서 약 3 ~ 5dB의 소음저감 효과가 있음을 알수 있다.10 to 12, the ratio d / D of the inner diameter D of the first hole 8d and the inner diameter d of the second hole 8e is 0.5 ≦ d / D ≦ 0.8, and the noise reduction hole is shown in FIG. Experiment with the set value within the range where the ratio P '/ P of the total depth P of (H) to the depth P' of the first hole 8d is 0.1≤P '/ P≤0.5. It is a graph showing the noise state generated. As shown in the figure, it can be seen that the noise reduction effect of about 3 ~ 5dB in the frequency band 1.5KHz ~ 2.5KHz range.

이상에서 설명한 바와 같이, 본 발명에 의한 밀폐형 회전식 압축기의 소음저감구조는 실린더의 내부에서 압축된 압축가스가 토출포트를 통해 토출되는 과정에서, 토출포트의 측부에 토출포트와 연통되도록 다단으로 홀로 형성된 소음저감홀에 의해 특정 주파수 대역의 맥동 소음이 저감됨과 더불어 설정된 소음저감홀의 체적을 유지하게 되어 재팽창에 의한 손실을 감소시키게 됨으로써 압축기의 체적 효율을 높이고 신뢰성을 향상시킬 수 있는 효과가 있다.As described above, the noise reduction structure of the hermetic rotary compressor according to the present invention is formed in multiple stages so that the compressed gas compressed in the cylinder is discharged through the discharge port so as to communicate with the discharge port on the side of the discharge port. The pulsation noise of the specific frequency band is reduced by the noise reduction hole, and the volume of the noise reduction hole is maintained to reduce the loss due to re-expansion, thereby improving the volumetric efficiency of the compressor and improving reliability.

Claims (5)

내부에 롤링피스톤이 편심 회전하는 압축 공간이 형성되고 상기 압축 공간의 내주면에 냉매가스가 유입되는 흡입구가 형성되며 그 측부에 압축된 냉매가스가 토출되는 토출포트가 형성되고 상기 흡입구와 토출포트사이에 상기 롤링피스톤에 탄성적으로 접촉되어 내부를 흡입실과 압축실로 나누는 베인이 결합되어 이루어진 실린더를 구비한 밀폐형 회전식 압축기에 있어서; 상기 토출포트와 연통되도록 토출포트의 측부에 내경이 다른 원통형 홀이 상기 실린더의 길이 방향으로 점차 작아지도록 다단으로 이어진 형태의 소음저감홀이 형성되어 이루어짐을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조.A compression space in which a rolling piston is eccentrically rotated is formed therein, and an inlet port through which refrigerant gas flows is formed on an inner circumferential surface of the compression space, and a discharge port through which compressed refrigerant gas is discharged is formed between the suction port and the discharge port. An enclosed rotary compressor having a cylinder in which a vane for elastically contacting the rolling piston and dividing an interior into a suction chamber and a compression chamber is coupled to the rolling piston; Noise reduction structure of the hermetic rotary compressor characterized in that the cylindrical hole having a different inner diameter is formed on the side of the discharge port to communicate with the discharge port is formed in the form of continuous noise reduction holes formed in multiple stages so as to gradually decrease in the longitudinal direction of the cylinder. 제1항에 있어서, 상기 소음저감홀은 상기 토출포트와 연통되도록 겹쳐지는 제1홀과 상기 제1홀에 이어 그 제1홀보다 내경이 작은 제2홀로 형성됨을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조.The noise reduction method of claim 1, wherein the noise reduction hole is formed of a first hole overlapping to communicate with the discharge port and a second hole having an inner diameter smaller than the first hole after the first hole. Abatement structure. 제1항에 있어서, 상기 소음저감홀은 상기 토출포트와 연통되도록 겹쳐지는 제1홀과 상기 제1홀보다 내경이 작은 제2홀과, 상기 제2홀보다 내경이 작은 제3홀로 형성됨을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조.The method of claim 1, wherein the noise reduction hole is formed of a first hole overlapping to communicate with the discharge port, a second hole having an inner diameter smaller than the first hole, and a third hole having an inner diameter smaller than the second hole. Noise reduction structure of hermetic rotary compressor. 제2항 또는 제3항에 있어서, 상기 제1홀과 토출포트의 겹침 영역의 폭은 제1홀 지름의 0.1 ~ 0.2임을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조.The noise reduction structure of claim 2 or 3, wherein the width of the overlapping area between the first hole and the discharge port is 0.1 to 0.2 of the diameter of the first hole. 제2항 또는 제3항에 있어서, 상기 제1홀의 내경(D)과 제2홀의 내경(d)의 비(d/D)는 0.5≤d/D≤0.8 이고, 소음저감홀의 전체 깊이(P)와 제1홀의 깊이(P')의 비(P'/P)는 0.1≤P'/P≤0.5 임을 특징으로 하는 밀폐형 회전식 압축기의 소음저감구조.The method of claim 2 or claim 3, wherein the ratio (d / D) of the inner diameter (D) of the first hole and the inner diameter (d) of the second hole is 0.5 ≤ d / D ≤ 0.8, the overall depth (P) of the noise reduction hole ) And the ratio (P '/ P) of the depth (P') of the first hole is 0.1≤P '/ P≤0.5.
KR1019980022951A 1997-08-30 1998-06-18 Structure for reducing noise of rotary compressor KR100304556B1 (en)

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