KR100402477B1 - Fan assembly for refrigerator - Google Patents
Fan assembly for refrigerator Download PDFInfo
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- KR100402477B1 KR100402477B1 KR10-2001-0027020A KR20010027020A KR100402477B1 KR 100402477 B1 KR100402477 B1 KR 100402477B1 KR 20010027020 A KR20010027020 A KR 20010027020A KR 100402477 B1 KR100402477 B1 KR 100402477B1
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- Prior art keywords
- fan
- refrigerator
- blade
- hub
- axial
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Classifications
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- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
- F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/002—Axial flow fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
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- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
- F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
- F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
- F25D2317/0681—Details thereof
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
Abstract
본 발명은 냉장고에서 냉기를 순환시키는 송풍팬 어셈블리에 관한 것으로, 본 발명에 따른 냉장고의 송풍팬 어셈블리는, 허브(201) 및 상기 허브(201)의 외주면에 구비된 블레이드(202)로 구성된 축류팬(20)과, 상기 축류팬(20)을 회전작동시키는 모터(22)를 포함하며, 축류팬(20)의 블레이드(202) 개수가 7개이며, 허브 직경(d)과 팬 외경(D)의 비율이 백분율로 35 ~ 40%이고, 블레이드의 스윕각(α)이 50 ~ 55°이며, 블레이드 폭(b)과 팬 외경(D)의 비율이 백분율로 27 ~ 28%인 것을 특징으로 하여 이루어진다.The present invention relates to a blower fan assembly for circulating cold air in a refrigerator. The blower fan assembly of the refrigerator according to the present invention comprises a hub (201) and an axial flow fan including a blade (202) provided on an outer circumferential surface of the hub (201). 20, and a motor 22 for rotating the axial fan 20, the number of blades 202 of the axial fan 20 is seven, the hub diameter (d) and the fan outer diameter (D) The ratio of 35 to 40% as a percentage, the sweep angle (α) of the blade is 50 to 55 °, the ratio of the blade width (b) and the fan outer diameter (D) is 27 to 28% as a percentage Is done.
상술한 바와 같은 본 발명에 따른 냉장고의 송풍팬 어셈블리에 의하면 축류팬의 송풍인자 특성상 공기유동 소음이 감소하기 때문에 냉장고의 상품성 향상에 도움이 된다.According to the blower fan assembly of the refrigerator according to the present invention as described above, the air flow noise is reduced due to the blowing factor of the axial flow fan, which helps to improve the commercialization of the refrigerator.
Description
본 발명은 냉장고에 관한 것으로서, 보다 상세하게는 냉기를 순환시키는 냉장고용 송풍팬 어셈블리에 관한 것이다.The present invention relates to a refrigerator, and more particularly, to a blowing fan assembly for a refrigerator for circulating cold air.
냉장고는 음식물 등을 냉동시키거나, 냉장보관하기 위해 사용되는 것으로서, 도 1에 나타난 것과 같이 냉동실(10a)과 냉장실(10b)로 분리된 수납공간을 형성하는 케이스 (10)및 상기 케이스(10)의 일측에 장착되어 냉동실(10a)과 냉장실(10b)을 개폐하는 냉동 냉장실 도어(12)와, 압축기(14), 응축기(미도시) 및 증발기(16) 등과 같이 냉동사이클을 이루어 냉기를 형성하는 기기들을 포함하여 구성되어 있다.The refrigerator is used to freeze or refrigerate food or the like, and as shown in FIG. 1, a case 10 and a case 10 forming a storage space separated into a freezing compartment 10a and a refrigerating compartment 10b. It is mounted on one side of the freezer compartment door 12 for opening and closing the freezer compartment (10a) and the refrigerating compartment (10b), and forming a refrigeration cycle, such as a compressor 14, a condenser (not shown) and the evaporator 16 to form cold air It consists of devices.
이러한 냉장고에서는 압축기(14)에 의해 저온 저압의 기상 냉매가 고온 고압으로 압축되고, 압축된 고온 고압의 기상 냉매가 응축기를 지나는 과정에서 냉각 응축되어 고압의 액상으로 전환되며, 고압의 액체상태로 된 냉매는 모세관(미도시)을 통과하면서 그 온도와 압력이 낮아진 다음, 계속해서 증발기(16)에서 저온 저압의 기체상태로 변하면서 주위로부터 열을 빼앗아 그 주위의 공기를 냉각시키게 된다.In such a refrigerator, the low-temperature low-pressure gaseous refrigerant is compressed to high temperature and high pressure by the compressor 14, and the compressed high-temperature high-pressure gas phase refrigerant is cooled and condensed in the course of passing through the condenser and converted into a high-pressure liquid state. As the refrigerant passes through a capillary tube (not shown), its temperature and pressure are lowered, and then the evaporator 16 is changed into a low temperature low pressure gas state to take heat from the surroundings to cool the air around it.
증발기(16)에 의해 냉각된 공기는 증발기 일측에 위치된 송풍팬 어셈블리의 작동으로 냉동 냉장실(10a)(10b)로 유입되어 냉동 냉장실(10a)(10b)의 온도를 낮추게 되고, 최종적으로 냉장실(10b)에서 배출된 더운 공기는 다시 증발기(16)측으로 유입됨으로써 온도가 낮아지게 되며, 이러한 냉기의 순환이 송풍팬 어셈블리에 의해 지속됨으로써 냉동 냉장실(10a)(10b) 내의 온도가 안정적으로 저온 유지된다.The air cooled by the evaporator 16 flows into the freezer refrigerating compartments 10a and 10b by the operation of the blower fan assembly located on one side of the evaporator to lower the temperature of the freezer refrigerating compartments 10a and 10b. The temperature of the hot air discharged from 10b) is lowered by flowing back to the evaporator 16 side, and the circulation of the cold air is continued by the blower fan assembly, so that the temperature in the freezer compartments 10a and 10b is kept at a stable low temperature. .
상기 송풍팬 어셈블리는 축류팬(20)과 상기 축류팬(20)을 구동시키기 위한 모터(22)로 이루어져 있으며, 상기 축류팬(20)은 모터(22)의 회전축과 연결되는 허브(201) 및 상기 허브(201)의 외주면에 구비된 다수개의 블레이드(202)로 구성되어 있으며, 냉기의 유동은 모터(22)에 의해 회전작동되는 축류팬(20)의 블레이드(202) 전후면에 형성되는 압력차이에 의해 이루어진다.The blower fan assembly is composed of an axial fan 20 and a motor 22 for driving the axial fan 20, the axial fan 20 is a hub 201 connected to the rotating shaft of the motor 22 and Composed of a plurality of blades 202 provided on the outer circumferential surface of the hub 201, the flow of cold air is formed on the front and rear surfaces of the blades 202 of the axial flow fan 20 rotated by the motor 22 Is made by difference.
여기서, 축류팬(20)의 송풍특성을 결정하는 송풍인자로는 스윕각(sweep angle), 최대 캠버량, 블레이드의 개수 등이 있는데, 도 2의 a에 나타난 것과 같이 상기 스윕각(α)은 블레이드(202)의 내측단 중심, 즉 블레이드(202)가 허브(201)와 접하는 부분의 중심과 블레이드(202)의 외측단(팁) 중심점을 연결하는 선이, 상기 블레이드(202)의 내측단 중심점 및 허브(201)의 중심점을 통과하는 선(Y축)과 이루는 각을 말한다.Here, the blowing factors that determine the blowing characteristics of the axial fan 20 include a sweep angle, a maximum camber amount, the number of blades, and the like. As shown in FIG. The inner end of the blade 202, that is, the line connecting the center of the portion where the blade 202 is in contact with the hub 201 and the center of the outer end (tip) of the blade 202, is the inner end of the blade 202. An angle formed with a line (Y axis) passing through the center point and the center point of the hub 201 is referred to.
그리고, 도 2의 b에 나타난 것과 같이 최대 캠버량(P)은 블레이드(202)의 리딩 에지(leading edge)에서 트레일링 에지(trailing edge)를 잇는 코드(chord)상에서 최대 캠버위치(p)까지를 거리를 뜻한다.As shown in b of FIG. 2, the maximum camber amount P is from the leading edge of the blade 202 to the maximum camber position p on a chord connecting the trailing edge. Means distance.
상기 스윕각(α)은 축류팬(20)의 유동소음을 결정하는 인자로서, 스윕각(α)이 크면 허브(201)와 블레이드(202)의 팁 사이에서의 공기유동 위상차가 크게 되고, 스윕각(α)이 작으면 공기유동 위상차가 작게 된다.The sweep angle α is a factor for determining the flow noise of the axial fan 20. When the sweep angle α is large, the air flow phase difference between the hub 201 and the tip of the blade 202 is increased, and the sweep angle α is increased. If the angle α is small, the air flow phase difference becomes small.
공기유동의 위상차이로 인해 블레이드(202)의 외측단에서 발생하는 소음과 내측단에서 발생하는 소음에도 위상차이가 발생하게 되는데, 이러한 위상차이가 클 수록 블레이드(202)를 통과하는 공기유동 주파수가 감소되어 소음이 작아진다.Due to the phase difference of the air flow, the phase difference occurs in the noise generated at the outer end of the blade 202 and the noise generated at the inner end, and the larger the phase difference, the higher the air flow frequency passing through the blade 202 is. It is reduced and the noise becomes smaller.
한편, 냉동실(10a)과 냉장실(10b)이 분리된 대용량 냉장고(도 1 참조)의 경우에는 복잡한 유로구조상 냉기의 유동저항이 크기 때문에 직경이 큰 축류팬을 높은 회전속도로 가동시켜 송풍압력을 높이는 방식으로 냉기를 유동시키게 된다.On the other hand, in the case of a large-capacity refrigerator (see FIG. 1) in which the freezing compartment 10a and the refrigerating compartment 10b are separated, the flow resistance of the cold air is large due to the complicated flow path structure. Cold air in a manner.
여기서, 상기 대용량 냉장고에 적용되는 축류팬(20)은 블레이드(202)가 4개이고, 블레이드(202) 사이의 간격은 적당하나 블레이드(202)의 곡률이 크고, 스윕각(a)이 작으며, 블레이드 폭(b)이 크고, 허브 직경(d)이 최적을 값을 가지고 있지 않은 구조로서, 적정수준의 송풍압력을 형성하는 속도로 회전될 경우, 냉장고 전방에서 약 22.7dB(A)의 공기 유동소음을 유발하는 것으로 측정되었다.Here, the axial fan 20 is applied to the large-capacity refrigerator has four blades 202, the interval between the blades 202 is suitable, but the curvature of the blade 202 is large, the sweep angle (a) is small, The blade width b is large and the hub diameter d does not have an optimal value. When the blade is rotated at a speed to form an appropriate blowing pressure, about 22.7 dB (A) of air flows in front of the refrigerator. It was measured to cause noise.
이와 같은 축류팬(20)의 회전시 발생하는 공기 유동소음은 압축기의 소음 및 기계실의 응축기 냉각팬의 소음과 함께 냉장고의 작동소음을 형성하는 요인으로서, 타 소음원인과 함께 최종적인 냉장고의 작동소음 정도는 약 27.0dB(A) 정도가 되는데, 이 정도의 작동소음은 야간에는 수면을 방해할 정도로서, 냉장고의 상품성을떨어뜨리는 한 원인이 된다.The air flow noise generated during the rotation of the axial fan 20 is a factor that forms the operation noise of the refrigerator together with the noise of the compressor and the noise of the condenser cooling fan of the machine room, and the operation noise of the final refrigerator together with other noise sources. The level is about 27.0dB (A), and this level of operation noise disturbs sleep at night, which is a cause of deteriorating the commerciality of the refrigerator.
본 발명은 상기한 종래 문제점을 해결하고자 안출된 것으로서, 구조적인 특성상 공기유동 소음이 적은 축류팬을 구비함으로써 냉장고의 상품성 향상에 도움이 되는 냉장고의 송풍팬 어셈블리 제공을 목적으로 한다.SUMMARY OF THE INVENTION The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a blower fan assembly of a refrigerator, which is helpful in improving the merchandise of the refrigerator by providing an axial fan with less airflow noise due to its structural characteristics.
도 1은 일반적인 냉장고의 냉기유로구조를 개략적으로 나타낸 단면도이다.1 is a cross-sectional view schematically showing a cold air flow path structure of a general refrigerator.
도 2의 a, b는 냉장고의 송풍팬 어셈블리를 구성하는 종래 축류팬의 특성인자를 나타낸 평면도와 측면도이다.2A and 2B are a plan view and a side view showing characteristic factors of a conventional axial flow fan constituting a blower fan assembly of a refrigerator.
도 3의 a, b는 본 발명의 실시예에 따른 송풍팬 어셈블리를 구성하는 축류팬의 특성인자를 나타낸 평면도와 측면도이다.3 is a plan view and a side view showing the characteristic factors of the axial flow fan constituting the blower fan assembly according to an embodiment of the present invention.
도 4는 본 발명의 실시예에 따른 축류팬의 특성인자 중에서 블레이드의 개수 에 변동에 의한 소음변화를 나타낸 그래프이다.Figure 4 is a graph showing the noise change by the variation in the number of blades among the characteristic factors of the axial fan according to an embodiment of the present invention.
도 5는 본 발명의 실시예에 따른 축류팬의 특성인자 중에서 허브 직경 변경에 의한 소음변화를 나타낸 그래프이다.5 is a graph showing a change in noise by changing the hub diameter among the characteristic factors of the axial fan according to an embodiment of the present invention.
도 6은 본 발명의 실시예에 따른 축류팬의 특성인자 중에서 스윕각 변경에 의한 소음변화를 나타낸 그래프이다.6 is a graph showing a change in noise by changing the sweep angle among the characteristic factors of the axial fan according to an embodiment of the present invention.
도 7은 본 발명의 실시예에 따른 축류팬의 특성인자 중에서 블레이드 폭 변경에 의한 소음변화를 나타낸 그래프이다.7 is a graph showing a change in noise by changing the blade width among the characteristic factors of the axial fan according to an embodiment of the present invention.
도 8은 본 발명의 실시예에 따른 축류팬과 종래기술에 따른 축류팬의 소음차이를 나타낸 그래프이다.Figure 8 is a graph showing the noise difference between the axial fan and the axial fan according to the prior art according to an embodiment of the present invention.
<도면의 주요 부분에 대한 부호의 설명><Explanation of symbols for the main parts of the drawings>
10: 케이스 10a: 냉동실10: case 10a: freezer
10b: 냉장실 12: 도어10b: refrigerator 12: door
14: 압축기 16: 증발기14: Compressor 16: Evaporator
20: 축류팬 201: 허브20: axial fan 201: hub
202: 블레이드 22: 모터202: blade 22: motor
상기 목적을 달성하기 위하여 제공되는 본 발명에 따른 냉장고의 송풍팬 어셈블리는 허브 및 상기 허브의 외주면에 구비된 블레이드로 구성된 축류팬과, 상기 축류팬을 회전작동시키는 모터를 포함하며; 상기 축류팬의 블레이드 개수가 7개이며, 허브 직경과 팬 외경의 비율이 백분율로 35 ~ 40%이고, 블레이드의 스윕각이 50 ~ 55°이며, 블레이드 폭과 팬 외경의 비율이 백분율로 27 ~ 28%인 것을 특징으로 하여 이루어진다.Blowing fan assembly of the refrigerator according to the present invention provided to achieve the above object comprises an axial flow fan consisting of a hub and a blade provided on the outer peripheral surface of the hub, and a motor for rotating the axial flow fan; The number of blades of the axial fan is seven, the ratio of the hub diameter and the fan outer diameter is 35 to 40% as a percentage, the sweep angle of the blade is 50 to 55 °, the ratio of the blade width and fan outer diameter is 27 ~ as a percentage 28%.
이하, 본 발명의 실시예를 첨부된 도 3부터 도 8까지 참조로 하여 상세하게 설명하며, 본 발명의 내용 중 종래구성과 동일한 부분에 대해서는 동일한 부호를 부여하기로 한다.Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to FIGS. 3 to 8, and the same reference numerals will be given to the same parts as those in the prior art.
본 발명의 실시예에 따른 송풍팬 어셈블리의 축류팬은 상기 도 3에 나타난 것과 같이 블레이드(202)가 7개이며, 허브 직경(d)과 팬 외경(D)의 비율이 백분율로 35 ~ 40%이고, 블레이드의 스윕각(α)이 50 ~ 55°이며, 블레이드 폭(b)과 팬 외경(D)의 비율이 백분율로 27 ~ 28%인 구조로 이루어진다.As shown in FIG. 3, the axial fan of the blower fan assembly according to the embodiment of the present invention has seven blades 202, and the ratio of the hub diameter d and the fan outer diameter D is 35 to 40% as a percentage. And the sweep angle α of the blade is 50 to 55 °, and the ratio of the blade width b and the fan outer diameter D is 27 to 28% as a percentage.
여기서, 상기 팬의 외경(D)은 100 ±1mm 이고, 허브 직경(d)은 40 ±1mm 이며, 블레이드의 스윕각(α)은 51.8 ±1°이고, 블레이드 폭(b)은 27.8 ±1mm 로 이루어진다.Here, the outer diameter (D) of the fan is 100 ± 1mm, the hub diameter (d) is 40 ± 1mm, the sweep angle (α) of the blade is 51.8 ± 1 °, the blade width (b) is 27.8 ± 1mm Is done.
상술한 바와 같은 축류팬의 각 송풍인자는 냉동실과 냉장실이 분리된 대용량 냉장고에서 요구하는 적절한 송풍량(약 0.65CMM)을 발생시키는 것을 기준으로 하여 실험결과에 의해 선정된 것으로서, 먼저, 블레이드의 개수에 따른 소음측정을 위해 각각 5개, 7개, 9개의 블레이드가 구비된 축류팬으로 실험한 결과, 도 4에 나타난 것과 같이 블레이드 개수가 7개인 축류팬의 공기유동 소음이 가장 작은 것으로 나타났다.Each blowing factor of the axial fan as described above is selected by the experimental results on the basis of generating the appropriate blowing amount (about 0.65CMM) required in the large-capacity refrigerator separated from the freezer compartment and the refrigerating compartment, first, the number of blades As a result of experiments with axial fans equipped with five, seven and nine blades, respectively, for the noise measurement according to the present invention, as shown in FIG.
여기서, 홀수개의 블레이드가 구비된 축류팬만으로 실험한 이유는 짝수개의 블레이드가 구비된 축류팬을 사용할 경우에는 모터에서 발생하는 주파수와 축류팬에서 발생하는 주파수가 공진현상에 의해 증폭되기 때문에 이를 방지하기 위해서이다.Here, the reason why the experiment was performed only with an axial fan having an odd number of blades is to prevent the frequency generated from the motor and the axial fan amplified by the resonance phenomenon when using an axial fan with an even number of blades. For that.
그리고, 허브 직경(d)변화에 따른 냉장고 전방에서의 소음변화를 측정한 결과, 도 5에 나타난 것과 같이 허브 직경(d)이 약 35 ~ 40mm 인 경우에 공기유동 소음이 가장 작은 것으로 나타났는데, 이는 전술한 것처럼 축류팬의 외경(D)이 100 ±1mm 인 경우에 허브 직경(d)과 팬 외경(D)과의 적절한 비율(35 ~ 40%)을 만족하는 수치이다.And, as a result of measuring the noise change in the front of the refrigerator according to the change in the hub diameter (d), as shown in Figure 5, when the hub diameter (d) is about 35 ~ 40mm, the airflow noise is the smallest, This is a numerical value satisfying an appropriate ratio (35-40%) of the hub diameter d and the fan outer diameter D when the outer diameter D of the axial fan is 100 ± 1 mm as described above.
또한, 블레이드의 스윕각(α) 변화에 따른 냉장고 전방에서의 소음변화를 측정한 결과, 도 6에 나타난 것과 같이 스윕각(α)이 50 ~ 55°일 때 가장 낮은 공기유동 소음이 발생하는 것으로 밝혀졌다.In addition, as a result of measuring the noise change in front of the refrigerator according to the change of the sweep angle (α) of the blade, as shown in Figure 6, the lowest airflow noise occurs when the sweep angle (α) is 50 ~ 55 ° Turned out.
블레이드 폭(b) 변화에 따른 냉장고 전방에서의 소음변화를 측정한 결과에 따르면, 도 7에 나타난 것과 같이 블레이드 폭(b)이 27 ~ 28mm 인 경우에 가장 작은 공기유동 소음이 발생하고, 27mm 보다 작은 경우에는 공기유동 소음이 약간 증가하는 것을 알 수 있는데, 이는 앞에서 말한 것처럼 축류팬의 외경(D)이 약 100 ±1mm 일 때 축류팬 외경(D)과 블레이드 폭(b)의 적절한 비율(27 ~ 28%)을 만족하는 수치이다.According to the result of measuring the noise change in front of the refrigerator according to the blade width b change, as shown in FIG. 7, the smallest airflow noise occurs when the blade width b is 27 to 28 mm, and is larger than 27 mm. In small cases, the airflow noise is slightly increased, which is the proper ratio of the axial fan outer diameter (D) to the blade width (b) when the outer diameter (D) of the axial fan is about 100 ± 1 mm, as mentioned earlier. ~ 28%).
본 실시예에 따른 송풍팬 어셈블리에 의하면, 도 8에 나타난 것과 같이 축류팬의 송풍인자 구성상 종래의 송풍팬 어셈블리에 비해, 동일한 송풍량(0.65CMM)을 기준으로, 공기유동 소음이 22.7dB(A)에서 19.0dB(A)로 낮아졌으며, 냉장고의 전체소음은 27dB(A)에서 25.6dB(A)로 낮아졌다.According to the blowing fan assembly according to the present embodiment, as shown in FIG. 8, the airflow noise is 22.7 dB (A) based on the same blowing amount (0.65CMM), compared to the conventional blowing fan assembly in terms of the configuration of the blowing factor of the axial flow fan. ), And the overall noise of the refrigerator was lowered from 27dB (A) to 25.6dB (A).
이상에서 설명한 바와 같이 본 발명에 따른 냉장고의 송풍팬 어셈블리에 의하면 축류팬의 구조적인 특성상 공기유동 소음이 감소하기 때문에 냉장고의 상품성 향상에 도움이 된다.As described above, according to the blower fan assembly of the refrigerator according to the present invention, since the airflow noise is reduced due to the structural characteristics of the axial fan, it is helpful to improve the commercialization of the refrigerator.
Claims (2)
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR10-2001-0027020A KR100402477B1 (en) | 2001-05-17 | 2001-05-17 | Fan assembly for refrigerator |
| CNB011236760A CN1183332C (en) | 2001-05-17 | 2001-09-03 | Fan assembly for refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR10-2001-0027020A KR100402477B1 (en) | 2001-05-17 | 2001-05-17 | Fan assembly for refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| KR20020088495A KR20020088495A (en) | 2002-11-29 |
| KR100402477B1 true KR100402477B1 (en) | 2003-10-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| KR10-2001-0027020A KR100402477B1 (en) | 2001-05-17 | 2001-05-17 | Fan assembly for refrigerator |
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| KR (1) | KR100402477B1 (en) |
| CN (1) | CN1183332C (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100484828B1 (en) * | 2002-11-27 | 2005-04-22 | 엘지전자 주식회사 | Refrigerator's cool air circulation axial flow fan |
| KR20050052151A (en) * | 2003-11-29 | 2005-06-02 | 엘지전자 주식회사 | Fan of refrigerator |
| KR100641111B1 (en) * | 2004-06-02 | 2006-11-02 | 엘지전자 주식회사 | Fan for cooling |
| CN101988522B (en) * | 2010-12-01 | 2012-08-29 | 鑫贺精密电子(东莞)有限公司 | Cooling fan |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0849698A (en) * | 1994-08-08 | 1996-02-20 | Yamaha Motor Co Ltd | Axial fan |
| KR19980048744A (en) * | 1996-12-18 | 1998-09-15 | 구자홍 | Axial flow fan for HSM cooling |
| JP2001059499A (en) * | 1999-07-22 | 2001-03-06 | Lg Electronics Inc | Axial flow fan for cold air circulation |
| KR20010026488A (en) * | 1999-09-07 | 2001-04-06 | 구자홍 | Out door unit axial flow fan for airconditioner |
-
2001
- 2001-05-17 KR KR10-2001-0027020A patent/KR100402477B1/en not_active IP Right Cessation
- 2001-09-03 CN CNB011236760A patent/CN1183332C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0849698A (en) * | 1994-08-08 | 1996-02-20 | Yamaha Motor Co Ltd | Axial fan |
| KR19980048744A (en) * | 1996-12-18 | 1998-09-15 | 구자홍 | Axial flow fan for HSM cooling |
| JP2001059499A (en) * | 1999-07-22 | 2001-03-06 | Lg Electronics Inc | Axial flow fan for cold air circulation |
| KR20010026488A (en) * | 1999-09-07 | 2001-04-06 | 구자홍 | Out door unit axial flow fan for airconditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1386984A (en) | 2002-12-25 |
| KR20020088495A (en) | 2002-11-29 |
| CN1183332C (en) | 2005-01-05 |
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