KR0121144B1 - Noise reducing equipment of rotary compressor - Google Patents

Noise reducing equipment of rotary compressor

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Publication number
KR0121144B1
KR0121144B1 KR1019940031271A KR19940031271A KR0121144B1 KR 0121144 B1 KR0121144 B1 KR 0121144B1 KR 1019940031271 A KR1019940031271 A KR 1019940031271A KR 19940031271 A KR19940031271 A KR 19940031271A KR 0121144 B1 KR0121144 B1 KR 0121144B1
Authority
KR
South Korea
Prior art keywords
groove
rotary compressor
noise
noise reduction
compressor
Prior art date
Application number
KR1019940031271A
Other languages
Korean (ko)
Other versions
KR960018252A (en
Inventor
이창호
Original Assignee
구자홍
엘지전자주식회사
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Publication date
Application filed by 구자홍, 엘지전자주식회사 filed Critical 구자홍
Priority to KR1019940031271A priority Critical patent/KR0121144B1/en
Publication of KR960018252A publication Critical patent/KR960018252A/en
Application granted granted Critical
Publication of KR0121144B1 publication Critical patent/KR0121144B1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/13—Noise

Abstract

The noise reducing device of a rotary compressor is intended to reduce the pressure pulsation of gas generated when the high temperature and high pressure of refrigerant which has been compressed in the compressor is discharged through a discharging hole. The noise reducing device forms a closed curve groove on a cylinder or a bearing and a connecting path through which the groove is connected to a compressing room around the discharging hole, whereby it forms a Helmholtz resonator, thus to reduce noises generated from the frequency according to the peripheral length of the groove.

Description

로타리 압축기의 소음 저감장치Noise reduction device of rotary compressor

제1도는 일반적인 로타리 입축기의 압축실 구조도.1 is a schematic diagram of a compression chamber of a typical rotary granulator.

제2도 및 제3도는 종래 로타리 압축기의 소음 저감구조를 보인 단면도 및 주베어링의 평면도.2 and 3 are cross-sectional views showing the noise reduction structure of the conventional rotary compressor and a plan view of the main bearing.

제4도 및 제5도는 본 발명에 의한 로타리 압축기의 소음 저감장치를 보인 단면도 및 주베어링의 평면도.4 and 5 are cross-sectional views showing the noise reduction device of the rotary compressor according to the present invention and a plan view of the main bearing.

제6도는 본 발명의 요부를 발췌해서 보인 제5도의 A부 상세도.FIG. 6 is a detailed view of portion A of FIG. 5 showing an essential part of the present invention.

제7도는 본 발명의 다른 실시예를 보인 요부 상세도.Figure 7 is a detailed view of the main portion showing another embodiment of the present invention.

제8도는 본 발명의 또 다른 실시예를 보인 요부 상세도.8 is a detailed view of the main portion showing another embodiment of the present invention.

* 도면의 주요부분에 대한 부호의 설명* Explanation of symbols for main parts of the drawings

7 : 주베어링 9 : 토출통로7: main bearing 9: discharge passage

10 : 폐곡선 홈 11 : 연결통로10: closed curve groove 11: connection path

본 발명은 로타리 압축기의 소음 저감장치에 관한 것으로, 특히 압축실에서 압축된 고온, 고압의 냉매가스가 토출구를 통해 분출될 때 발생하는 가스의 압력 맥동을 감소시킬 수 있도록 한 로타리 압축기의 소음 저감장치에 관한 것이다.The present invention relates to a noise reduction device of a rotary compressor, and in particular, a noise reduction device of a rotary compressor to reduce pressure pulsation of a gas generated when a high temperature and high pressure refrigerant gas compressed in a compression chamber is ejected through a discharge port. It is about.

일반적인 로타리 압축기의 압축실 구조가 제1도에 도시되어 있는 바, 간단히 살펴보면 다음과 같다.The compression chamber structure of a typical rotary compressor is shown in FIG. 1, which is briefly described as follows.

도시한 바와 같이, 일반적인 로타리 압축기의 압축실은 실린더(1), 롤러(2) 및 베인(3)등에 의해서 형성되며, 흡입포트(4)를 통해 흡입된 냉매가스는 크랭크축(5)의 회전력에 의해 압축되어 토출포트(6)를 통해 토출된다. 이때 토출되는 고온, 고압의 가스는 고주파 성분(3KHz 이상)의 압력맥동을 생성시켜 압축기 소음의 한 원인으로 작용하게 된다.As shown, the compression chamber of a general rotary compressor is formed by a cylinder (1), a roller (2) and a vane (3), and the refrigerant gas sucked through the suction port (4) is applied to the rotational force of the crankshaft (5). Is compressed and discharged through the discharge port 6. At this time, the discharged high-temperature, high-pressure gas generates a pressure pulsation of high frequency components (3KHz or more) to act as a cause of the compressor noise.

이와 같이 발생되는 소음을 줄이기 위한 장치가 로타리 압축기에 구성되어 있다. 제2도 및 제3도에 종래 일반적으로 알려지고 있는 로타리 압축기의 소음 저감장치를 나타내었는 바, 이를 살펴보면 다음과 같다.A device for reducing the noise generated in this way is configured in the rotary compressor. 2 and 3 show a noise reduction device of a rotary compressor, which is generally known in the prior art.

도시한 바와 같이, 주베어링(7)의 일측에 소정크기의 공간(8)을 형성하고, 이 공간(8)과 주베어링(7)의 토출통로(9)를 연통되게 연결하여 헬름홀츠 공명기(Helmholtz Resonator)를 형성함으로써 토출되는 고온, 고압가스의 압력맥동으로 인한 소음의 발생을 저감시키도록 구성되어 있다.As shown in the drawing, a space 8 having a predetermined size is formed on one side of the main bearing 7, and the Helmholtz resonator is connected by connecting the space 8 and the discharge passage 9 of the main bearing 7 to communicate with each other. It is configured to reduce the generation of noise due to pressure pulsation of high temperature and high pressure gas discharged by forming a resonator.

그러나, 상기한 바와 같은 종래의 소음 저감장치에 있어서는, 헬름홀츠 공명기의 소음 감쇠 주파수가 f=의 식으로 표시됨으로써 특정 주파수 대역의 소음만 감쇠시키는 단점이 발생되었다{(상기 식에서 C는 음속, L'는 L+0.7d(L:통로 길이, d:통로직경), A는 통로 면적, V는 공간 체적이다}.However, in the conventional noise reduction device as described above, the noise attenuation frequency of the Helmholtz resonator is f = It is expressed by the following equation, resulting in the attenuation of only the noise of a specific frequency band {(where C is the speed of sound, L 'is L + 0.7d (L: path length, d: path diameter), A is the passage area, V Is space volume}.

또한, 종래의 소음 저감구조는 헬름홀츠 공명기를 구성하기 위한 공간(8)에 있는 압축된 냉매가스가 흡입시 압축실로 재팽창됨으로써 압축기의 효율을 저하시키는 요인으로 작용하는 문제도 있었다.In addition, the conventional noise reduction structure also has a problem that the compressed refrigerant gas in the space (8) for constituting the Helmholtz resonator re-expands into the compression chamber upon inhalation, thereby acting as a factor of lowering the efficiency of the compressor.

본 발명은 상기와 같은 문제점을 감안하여 창안한 것으로, 헬름홀츠 공명기에 의한 특정 주파수 대역의 소음뿐만 아니라 다른 주파수 대역의 소음도 저감시킴으로써 압축기의 전체적인 소음을 감소시킬수 있도록 한 로타리 압축기의 소음 저감장치를 제공하는데 그 목적이 있다.The present invention has been made in view of the above problems, and provides a noise reduction device for a rotary compressor that can reduce the overall noise of the compressor by reducing the noise of a specific frequency band as well as the noise of another frequency band by the Helmholtz resonator. The purpose is.

본 발명의 다른 목적은, 압축후 냉매가스가 압축실로 재팽창하는 것을 억제하여 압축기의 효율 상승 효과를 도모한 로타리 압축기의 소음 저감장치를 제공함에 있다.It is another object of the present invention to provide a noise reduction device of a rotary compressor which suppresses the re-expansion of refrigerant gas after compression into a compression chamber to achieve an effect of increasing the efficiency of the compressor.

상기와 같은 본 발명의 목적을 달성하기 위하여, 실린더 또는 주베어링에 폐곡선 홈을 형성하고, 이 홈과 토출구 근처의 압축실과 통하는 연결통로를 구성하여, 헬름홀츠 공명기의 효과와 동시에 상기 홈의 둘레 길이에 따른 주파수의 소음도 저감하도록 한 것을 특징으로 하는 로타리 입축기의 소음 저감장치가 제공된다.In order to achieve the object of the present invention as described above, by forming a closed curved groove in the cylinder or the main bearing, and forming a connection passage communicating with the compression chamber near the groove and the discharge port, at the same time as the effect of the Helmholtz resonator There is provided a noise reduction device of a rotary bearing machine, characterized in that to reduce the noise of the frequency according.

여기서, 상기 홈은 원형이나 타원형의 링형상으로 형성할 수 있고, 또는 사각형태로 형성할 수도 있다.Here, the groove may be formed in a circular or oval ring shape, or may be formed in a square shape.

이하, 상기한 바와 같은 본 발명에 의한 로타리 압축기의 소음 저감장치를 첨부도면에 도시한 실시예를 따라서 보다 상세히 설명한다.Hereinafter, the noise reduction device of the rotary compressor according to the present invention as described above will be described in more detail according to the embodiment shown in the accompanying drawings.

첨부한 제4도 및 제5도는 본 발명에 의한 로타리 압축기의 소음 저감장치를 보인 단면도 및 주베어링의 평면도이고, 제6도는 제5도의 A부 상세도로서, 도시한 바와 같이, 본 발명에 의한 장치는 주베어링(7)의 일측에 링형상의 폐곡선 홈(10)이 형성되어 있고, 이 폐곡선 홈(10)과 토출통로(9)가 연결통로(11)에 의해 연통되게 연결된 구조로 되어 있다.4 and 5 are cross-sectional views showing the noise reduction device of the rotary compressor according to the present invention and a plan view of the main bearing, and FIG. 6 is a detailed view of part A of FIG. 5, as shown in FIG. The device has a ring-shaped closed curved groove 10 formed on one side of the main bearing 7, and the closed curved groove 10 and the discharge passage 9 are connected to each other by a connecting passage 11. .

즉, 헬륨홀츠 공명기로서의 작용을 하는 폐곡선 홈(10)과 주베어링(7)의 토출통로(9)가 연결통로(11)에 의해 연결되어 헬름헬츠 공명기의 효과와 동시에 상기 폐곡선 홈(10)의 평균길이(제6도에 점선으로 표시한 부분:L)의 반파장에 해당하는 주파수의 소음도 저감할 수 있도록 함으로써 압축기의 잔체적인 소음을 감소시키도록 구성한 것이다.That is, the closed curve groove 10 which acts as a helium holz resonator and the discharge passage 9 of the main bearing 7 are connected by the connection passage 11, so that the closed curve groove 10 The noise of the frequency corresponding to the half-wave length of the average length (part shown by the dotted line in FIG. 6) can also be reduced to reduce the residual noise of the compressor.

일반적으로 공명기가 일정길이(L)를 가지는 파이프와 같이 양단의 경계면이 개방되어 있는 경우, 평면파(standing wave)는 다음과 같이 진행 방향의 길이만의 함수로 해당 주파수가 결정된다.In general, when the boundary of both ends of the resonator is open, such as a pipe having a certain length (L), the standing wave is determined as a function of only the length of the traveling direction as follows.

즉, 파이프 형사의 균일단면 공간속에서는 순수한 평면파 진행을 한다고 할 수 있으므로 상기 식과 같은 공명주파수를 나타내며, 염연히 볼륨(volume)이 존재하므로 헬름휼츠 공명 주파수 특성도 동시에 나타나게 된다.That is, in the uniform cross-sectional space of the pipe detective, it can be said that a pure plane wave propagation shows the resonance frequency as shown in the above equation, and since the volume exists indefinitely, the Helmhetz resonance frequency characteristic also appears at the same time.

만약에 양단중 한 면이 막혀 있다면가 된다.If either side is blocked Becomes

서지 홀(surge hole)이나 기존의 볼륨형 헬름휼츠 공명기의 경우에도 이러한 길이만의 함수에 의한 공명주파수 특징을 가질 수 있으나 형상적으로 파이프와 같지 않을 때(즉, 길이이외의 다른 함수의 영향을 받을 경우)는 통상적인 헬름휼츠 공명주파수식에 의해 공명 주파수가 결정된다.Surge holes or conventional volumetric Helmhetz resonators can also have resonant frequency characteristics as a function of this length, but they are not shaped like pipes (i.e., may be affected by functions other than length). The typical Helmhetz resonance frequency The resonance frequency is determined by the equation.

즉, 본 발명의 링형 공명기는 양단이 오픈되어 있는 파이프 형상의 공명기를 응용함으로써 ∞개의 하모닉(harmonics)성분 주파수에 대한 효과를 동시에 누릴수 있으며, 음파가 평면파라고 볼 수 있으므로 균일 단편의 파이프상에서 공간확보를 위해 링처럼 구부려 놓은 것이라고 볼 수 있다.That is, the ring-type resonator of the present invention can simultaneously enjoy the effects on the frequency of ∞ harmonic components by applying a pipe-shaped resonator with both ends open, and the sound wave can be regarded as a plane wave to secure space on the pipe of uniform fragments. It can be said to be bent like a ring.

이와 같은 본 발명의 구성에서 상기 홈(10)은 도시예와 같이 주베어링(7)에 형성 할 수도 있고, 또 도시하지는 않았으나, 실린더에 형성할 수도 있는 바, 실린더에 형성하는 경우, 홈은 실린더의 토출포트(6)에 연결되어 구성된다.In the configuration of the present invention as described above, the groove 10 may be formed in the main bearing 7 as shown in the example, and not shown, but may be formed in the cylinder bar, when formed in the cylinder, the groove is a cylinder It is configured to be connected to the discharge port (6) of.

또한 상기 폐곡선 홈(10)은 타원 형상의 링타입으로 형성할 수도 있고, 제7도 와 같이 사각 형상으로 형성할 수도 있으며, 제8도와 같이 원형의 링타입으로도 형성할 수 있다. 이때, 상기 폐곡선 홈(10)을 어떠한 형상, 즉 타원 형상, 사각 형상 및 링 형상으로 할 경우 이들의 평균길이(L)을 동일하게 한다면 동일한 주파수에 대하여 작용될 수 있는 것이다.In addition, the closed curved groove 10 may be formed in an elliptic ring type, may be formed in a rectangular shape as shown in FIG. 7, or may be formed in a circular ring type as shown in FIG. 8. In this case, when the closed curve groove 10 is formed in any shape, that is, an ellipse shape, a square shape, and a ring shape, the average length L of the closed curve groove 10 may be applied to the same frequency.

이와 같이 구성되는 본 발명에 의한 소음 저감장치의 기본 작용은 종래와 같다. 즉 헬름헬츠 공명기의 원리에 의해 가스 토출시 발생하는 소음을 저감시키는 것이다. 이와 같은 작용에서 종래에는 특정 주파수 대역의 소음 저감만이 가능했으나, 본 발명은 헬름헤츠 공명기의 효과와 동시에 다른 주파수 대역의 소음도 감소시킬 수 있다.The basic operation of the noise reduction device according to the present invention configured as described above is the same as the conventional one. In other words, by the principle of the Helm Helms resonator to reduce the noise generated during gas discharge. In this operation, only noise reduction of a specific frequency band has been possible in the related art, but the present invention can reduce noise of another frequency band at the same time as the effect of the Helmhetz resonator.

뿐만아니라 본 발명은 냉매 흡입시 홈(10)속의 냉매가 압축실로 재팽창될 경우, 홈내의 상호 반대편의 유로(제6도의 화살표 참조)에서 만나게 되어 압축실로의 재흡입이 억제된다. 따라서 종래와 같이 냉매가 압축실로 재팽창됨으로써 압축기의 효율이 저하되는 것을 방지할 수 있게 된다.In addition, in the present invention, when the refrigerant in the groove 10 is re-expanded into the compression chamber when the refrigerant is sucked, it meets in the flow paths (see the arrow in FIG. 6) opposite to each other in the groove to suppress re-suction into the compression chamber. Therefore, as the conventional refrigerant is re-expanded into the compression chamber, the efficiency of the compressor can be prevented from being lowered.

이상에서 상세히 설명한 바와 같이, 본 발명에 의하면, 헬름헬츠 공명기의 효과와 동시에 환상홈의 둘레길이에 따른 주파수 대역의 소음도 감소시킬 수 있으므로 압축기의 전체적인 소음을 감소시킬 수 있다. 또한 본 발명은 홈의 유로가 둘로 갈라져 있어 압축후, 냉매가 압축실로 재팽창되는 경우, 상호 저항에 의해 재팽창이 힘들게 되어 압축기의 효율 상승 효과도 있다.As described in detail above, according to the present invention, the noise of the frequency band according to the circumferential length of the annular groove can be reduced at the same time as the effect of the Helmheltz resonator, so that the overall noise of the compressor can be reduced. In addition, in the present invention, when the flow path of the groove is divided into two and the refrigerant is re-expanded into the compression chamber, the re-expansion is difficult due to mutual resistance, thereby increasing the efficiency of the compressor.

Claims (3)

실린더 또는 주베어링에 폐곡선 홈을 형성하고, 이 홈과 토출구 근처의 압축실과 통하는 연결통로를 구성하여, 헬름헬츠 공명기의 효과와 동시에 상기 홈의 둘레 길이에 따른 주파수의 소음도 저감토록 한 것을 특징으로 하는 로타리 압축기의 소음 저감장치.A closed curve groove is formed in the cylinder or the main bearing, and a connection passage communicating with the groove and the compression chamber near the discharge port is formed, so that the noise of the frequency along the circumferential length of the groove can be reduced at the same time as the effect of the Helmheltz resonator. Noise reduction device of rotary compressor. 제1항에 있어서, 상기 홈은 타원, 또는 원형상의 링 타입인 것을 특징으로 하는 로타리 압축기의 소음 저감장치.The noise reduction apparatus of claim 1, wherein the groove is an ellipse or a circular ring type. 제1항에 있어서, 상기 홈은 사각형상의 폐곡선 홈인 것을 특징으로 하는 로타리 압축기의 소음 저감장치.The noise reduction apparatus of claim 1, wherein the groove is a rectangular closed curve groove.
KR1019940031271A 1994-11-25 1994-11-25 Noise reducing equipment of rotary compressor KR0121144B1 (en)

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KR0121144B1 true KR0121144B1 (en) 1997-11-10

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