KR20020088496A - Fan assembly for refrigerator - Google Patents
Fan assembly for refrigerator Download PDFInfo
- Publication number
- KR20020088496A KR20020088496A KR1020010027021A KR20010027021A KR20020088496A KR 20020088496 A KR20020088496 A KR 20020088496A KR 1020010027021 A KR1020010027021 A KR 1020010027021A KR 20010027021 A KR20010027021 A KR 20010027021A KR 20020088496 A KR20020088496 A KR 20020088496A
- Authority
- KR
- South Korea
- Prior art keywords
- blade
- refrigerator
- fan
- hub
- noise
- Prior art date
Links
Classifications
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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
Landscapes
- 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)
Abstract
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 냉동실과 냉장실로 분리된 수납공간을 형성하는 케이스 (10)및 상기 케이스(10)의 일측에 장착되어 냉동실과 냉장실을 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 is mounted on one side of the case 10 and the freezer compartment to form a storage space separated into a freezer compartment and a refrigerator compartment as shown in FIG. 1. And a refrigerator compartment door 12 for opening and closing the refrigerator compartment, and devices for forming cold air by forming a refrigeration cycle such as a compressor 14, a condenser (not shown), and an evaporator 16.
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(16) 일측에 위치된 송풍팬 어셈블리의 작동으로 냉동 냉장실로 유입되어 냉동 냉장실의 온도를 낮추게 되고, 최종적으로 냉장실에서 배출된 더운 공기는 다시 증발기(16)측으로 유입됨으로써 온도가 낮아지게 되며, 이러한 냉기의 순환이 송풍팬 어셈블리에 의해 지속됨으로써 냉동 냉장실 내의 온도가 안정적으로 저온 유지된다.The air cooled by the evaporator 16 flows into the freezer fridge by operating the blower fan assembly located at one side of the evaporator 16 to lower the temperature of the freezer fridge. The temperature is lowered by flowing into the side), and the circulation of the cold air is continued by the blower fan assembly, whereby the temperature in the freezer refrigerator compartment is kept at a 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(도 2 참조), 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 It consists of a plurality of blades 202 provided on the outer circumferential surface of the hub (201) (see Fig. 2), the flow of cold air before and after the blades 202 of the axial flow fan 20 rotated by the motor 22 It is made by the pressure difference formed on the surface.
여기서, 축류팬(20)의 송풍특성을 결정하는 송풍인자로는 스윕각(sweep angle), 최대 캠버량, 블레이드의 개수 등이 있는데, 도 2의 a에 나타난 것과 같이 상기 스윕각(a)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(도면상 Y 축)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 a of FIG. 2. 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 in the drawing) passing through the center point and the center point of the hub 201 is referred to.
그리고, 최대 캠버량(P)은 도 2의 b에 나타난 것과 같이 블레이드(20)의 리딩 에지(leading edge: L.E)에서 트레일링 에지(trailing edge: T.E)를 잇는 코드(chord)상에서 리딩에지로부터 최대 캠버위치(p)까지를 거리를 뜻한다.And, the maximum camber amount P is from the leading edge on the chord connecting the trailing edge TE at the leading edge LE of the blade 20 as shown in b of FIG. The distance to the maximum camber position (p).
상기 스윕각(a)은 축류팬(20)의 유동소음을 결정하는 인자로서, 스윕각(a)이 크면 허브(201)와 블레이드(202)의 팁 사이에서의 공기유동 위상차가 크게 되고, 스윕각(a)이 작으면 공기유동 위상차가 작게 된다.The sweep angle (a) is a factor for determining the flow noise of the axial fan 20. If the sweep angle (a) is large, the air flow phase difference between the hub 201 and the tip of the blade 202 is increased, and the sweep angle is increased. If the angle a 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, 냉동실과 냉장실이 좌우로 수평배치된 사이드 바이 사이드(side by side)타입 냉장고와 같은 대용량 냉장고의 경우에는 복잡한 유로구조상 냉기의 유동저항이 크기 때문에 직경이 큰 축류팬(20)을 높은 회전속도로 가동시켜 송풍압력을 높이는 방식으로 냉기를 유동시키게 된다.On the other hand, in the case of a large-capacity refrigerator such as a side by side type refrigerator in which the freezer compartment and the refrigerating chamber are arranged horizontally from side to side, a large flow diameter of the axial fan 20 is increased due to the large flow resistance of the cold air due to the complicated flow path structure. The air is flowed in a way that the blowing pressure is increased by operating in the furnace.
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(202) 폭(b)이 크고, 허브 직경(d)이 최적을 값을 가지고 있지 않은 구조로서, 적정수준의 송풍압력을 형성하는 속도로 회전될 경우, 냉장고 전면측에서 21.1dB(A), 냉장고 후면측에서 25.5dB(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 202 has a large width b and a hub diameter d that does not have an optimal value. When the blade 202 is rotated at a speed for forming an appropriate blowing pressure, it is 21.1 dB (A) at the front side of the refrigerator. In addition, it was measured that airflow noise of 25.5dB (A) was generated at the rear side of the refrigerator.
이와 같은 축류팬(20)의 회전시 발생하는 공기 유동소음은 압축기(14)의 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 상품성을 떨어뜨리는 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 14 and the noise of the condenser cooling fan in the machine room. The operating noise level of about 27.0dB (A) is about, this level of operating noise is enough to disturb the sleep at night, causing a decrease in 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 대용량 냉장고의 냉기유로구조를 개략적으로 나타낸 단면도이다.1 is a cross-sectional view schematically showing a cold air flow path structure of a general large capacity refrigerator.
도 2의 a, b는 대용량 냉장고의 송풍팬 어셈블리를 구성하는 종래 축류팬의 특성인자를 나타낸 평면도와 측면도이다.2 a and b are a plan view and a side view showing the characteristic factors of the conventional axial flow fan constituting the blowing fan assembly of the large-capacity 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 4의 a, b는 본 발명의 실시예에 따른 축류팬의 특성인자 중에서 블레이드 개수 변동에 의한 냉장고 전후면에서의 소음변화를 나타낸 그래프이다.4A and 4B are graphs showing noise changes in front and rear surfaces of refrigerators due to blade number variation among characteristic factors of an axial fan according to an exemplary embodiment of the present invention.
도 5는 본 발명의 실시예에 따른 축류팬의 특성인자 중에서 허브 직경 변경에 의한 냉장고 전면에서의 소음변화를 나타낸 그래프이다.Figure 5 is a graph showing the noise change in the front of the refrigerator by changing the hub diameter among the characteristic factors of the axial flow fan according to an embodiment of the present invention.
도 6은 본 발명의 실시예에 따른 축류팬의 특성인자 중에서 스윕각 변경에 의한 냉장고 전면에서의 소음변화를 나타낸 그래프이다.6 is a graph showing a change in noise in the front of the refrigerator 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 냉장고 전면에서의 소음변화를 나타낸 그래프이다.7 is a graph showing a change in the noise in the front of the refrigerator 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 축류팬의 특성인자 중에서 블레이드의 피치각 변경에 의한 냉장고 전면에서의 소음변화를 나타낸 그래프이다.8 is a graph showing a change in noise in the front of the refrigerator by changing the pitch angle of the blade among the characteristic factors of the axial fan according to an embodiment of the present invention.
도 9는 본 발명의 실시예에 따른 축류팬과 종래기술에 따른 축류팬의 냉장고 전후면에서의 소음 차이를 나타낸 그래프이다.Figure 9 is a graph showing the noise difference in the front and rear of the refrigerator of the axial flow fan and the axial flow 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 12: 도어10: case 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 5개이며, 허브 직경과 팬 외경의 비율이 백분율로 28 ~ 30%이고, 블레이드의 스윕각이 44 ~ 50°이며, 블레이드의 피치각이 33 ~ 39°이고, 블레이드 폭과 팬 외경의 비율이 백분율로 33 ~ 37%인 것을 특징으로 하여 이루어진다.Blower fan assembly of the refrigerator according to the present invention provided to achieve the above object comprises an axial fan consisting of a hub and a blade provided on the outer peripheral surface of the hub, and a motor for rotating the axial fan, The number of blades is 5, the ratio of hub diameter to fan outer diameter is 28 to 30% as a percentage, the blade sweep angle is 44 to 50 °, the blade pitch angle is 33 to 39 °, blade width and fan outer diameter It is characterized in that the ratio of 33 to 37% as a percentage.
이하, 본 발명의 실시예를 첨부된 도 3부터 도 9까지 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 9, and the same reference numerals will be given to the same parts as in the prior art.
본 발명의 실시예에 따른 송풍팬 어셈블리의 축류팬은 상기 도 3에 나타난 것과 같이 블레이드(202)가 5개이며, 허브 직경(d)과 팬 외경(D)의 비율이 백분율로 28 ~ 30%이고, 블레이드(202)의 스윕각(a)이 44 ~ 50°이며, 블레이드(202)의피치각( β)(코드와 X축 사이의 각도)이 33 ~ 39°이고, 블레이드 폭(b)과 팬 외경(D)의 비율이 백분율로 33 ~ 37%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 five blades 202, and the ratio of the hub diameter d and the fan outer diameter D is 28 to 30% as a percentage. The sweep angle a of the blade 202 is 44 to 50 degrees, the pitch angle β of the blade 202 (the angle between the cord and the X axis) is 33 to 39 degrees, and the blade width b is And the ratio of the fan outer diameter (D) is composed of 33 ~ 37% as a percentage.
여기서, 상기 축류팬의 외경(D)은 145 ±1mm 이고, 허브 직경(d)은 41 ±1mm 이며, 블레이드(202)의 스윕각(a)은 45.5 ±1°이고, 블레이드 폭(b)은 50.7 ±1mm 로 이루어진다.Here, the outer diameter (D) of the axial fan is 145 ± 1mm, the hub diameter (d) is 41 ± 1mm, the sweep angle (a) of the blade 202 is 45.5 ± 1 °, the blade width (b) is 50.7 ± 1mm.
상술한 바와 같은 축류팬(20)의 각 송풍인자는 사이드 바이 사이드 타입 냉장고와 같은 대용량 냉장고에서 요구하는 적절한 송풍량(약 0.959CMM)을 발생시키는 것을 기준으로 하여 실험결과에 의해 선정된 것으로서, 먼저, 블레이드(202)의 개수에 따른 소음측정을 위해 각각 5개, 7개, 9개의 블레이드가 구비된 축류팬으로 실험한 결과, 도 4의 a, b에 나타난 것과 같이 블레이드 개수가 5개인 축류팬의 공기유동 소음이 냉장고 전후방에서 공히 가장 작은 것으로 나타났다.Each blowing factor of the axial fan 20 as described above is selected by the experimental results on the basis of generating the appropriate blowing amount (about 0.959CMM) required in a large-capacity refrigerator such as a side-by-side type refrigerator, first, In order to measure the noise according to the number of blades 202, five, seven and nine blades were experimented with the axial fan. As shown in a and b of FIG. Airflow noise was the smallest in front of and behind the refrigerator.
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)과 팬 외경(D)의 비율이 0.283(백분율로 환산하면 약 28%) 인 경우에 공기유동 소음이 가장 작은 것으로 나타났는데, 이는 전술한 것처럼 허브 직경(d)이 약 41mm 이고, 축류팬의 직경(D)이 약 145mm 일 때 만족하는 수치이다.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 FIG. 5, the ratio of the hub diameter (d) and the fan outer diameter (D) is 0.283 (in terms of percentage, about 28%). ), The airflow noise was found to be the smallest, which is satisfied when the hub diameter (d) is about 41 mm and the diameter (D) of the axial fan is about 145 mm, as described above.
또한, 블레이드의 스윕각(a) 변화에 따른 냉장고 전방에서의 소음변화를 측정한 결과, 도 6에 나타난 것과 같이 스윕각(a)이 45.5°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 (a) of the blade, it was found that the lowest airflow noise occurs when the sweep angle (a) is 45.5 ° as shown in FIG. .
블레이드 폭(b) 변화에 따른 냉장고 전방에서의 소음변화를 측정한 결과에 따르면, 도 7에 나타난 것과 같이 블레이드 폭(b)과 팬 직경(D)의 비율이 0.35(백분율로 환산하면 35%) 일 때 가장작은 공기유동 소음이 발생하는 것을 알 수 있는데, 이는 앞에서 말한 것처럼 블레이드 폭(b)이 약 50.7mm 이고, 축류팬의 직경(D)이 약 145mm 일 때 만족하게 되는 수치이다.As a result of measuring the noise change in the front of the refrigerator according to the blade width (b) change, as shown in Figure 7, the ratio of the blade width (b) and the fan diameter (D) is 0.35 (35% in terms of percentage) It can be seen that the smallest airflow noise occurs when the blade width (b) is about 50.7mm, and the diameter (D) of the axial fan is about 145mm.
마지막으로 블레이드의 피치각( β) 변화에 따른 냉장고 전방에서의 공기유동 소음변화를 측정한 결과, 도 8에 나타난 것과 같이 약 35°의 피치각에서 가장 낮은 공기유동 소음이 유발되는 것으로 나타났다.Finally, as a result of measuring the airflow noise change in front of the refrigerator according to the pitch angle β of the blade, as shown in FIG. 8, the lowest airflow noise was induced at the pitch angle of about 35 °.
본 실시예에 따른 송풍팬 어셈블리에 의하면, 도 9에 나타난 것과 같이 축류팬(20)의 송풍인자 구성상 종래의 송풍팬 어셈블리에 비해 공기유동 소음이 냉장고의 전방에서는 22.1dB(A)에서 18.8dB(A)로 낮아졌으며, 냉장고의 후방에서는 25.5dB(A)에서 22.7dB(A)로 낮아졌음을 알 수 있다.According to the blower fan assembly according to the present embodiment, as shown in FIG. 9, the airflow noise is 18.8dB at 22.1dB (A) at the front of the refrigerator in comparison with the blower assembly of the conventional blower fan. It has been lowered to (A), and from the rear of the refrigerator to 22.7 dB (A) to 25.5 dB (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 helps to improve the merchandise of the refrigerator.
Claims (2)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR10-2001-0027021A KR100402478B1 (en) | 2001-05-17 | 2001-05-17 | Fan assembly for refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR10-2001-0027021A KR100402478B1 (en) | 2001-05-17 | 2001-05-17 | Fan assembly for refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| KR20020088496A true KR20020088496A (en) | 2002-11-29 |
| KR100402478B1 KR100402478B1 (en) | 2003-10-22 |
Family
ID=27705290
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| KR10-2001-0027021A KR100402478B1 (en) | 2001-05-17 | 2001-05-17 | Fan assembly for refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| KR (1) | KR100402478B1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105257597A (en) * | 2015-11-12 | 2016-01-20 | 珠海格力电器股份有限公司 | Axial flow fan and axial flow fan blades thereof |
| CN109854533A (en) * | 2019-01-30 | 2019-06-07 | 广东美的制冷设备有限公司 | Fan blade, fan assembly, ducting part and air conditioner |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR970001999A (en) * | 1995-06-13 | 1997-01-24 | 구자홍 | Axial flow fan of microwave |
| JPH1089289A (en) * | 1996-09-13 | 1998-04-07 | Ebara Corp | Impeller for axial flow blower |
| KR100275045B1 (en) * | 1997-08-27 | 2001-01-15 | 구자홍 | Axial fan structure for room air conditioner |
-
2001
- 2001-05-17 KR KR10-2001-0027021A patent/KR100402478B1/en not_active IP Right Cessation
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105257597A (en) * | 2015-11-12 | 2016-01-20 | 珠海格力电器股份有限公司 | Axial flow fan and axial flow fan blades thereof |
| CN105257597B (en) * | 2015-11-12 | 2018-04-20 | 珠海格力电器股份有限公司 | Axial flow blower and its axial-flow leaf |
| CN109854533A (en) * | 2019-01-30 | 2019-06-07 | 广东美的制冷设备有限公司 | Fan blade, fan assembly, ducting part and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| KR100402478B1 (en) | 2003-10-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20030024264A1 (en) | Cooling air blowing apparatus of refrigerator | |
| KR100347050B1 (en) | Axial flow fan of refrigerator | |
| KR100484828B1 (en) | Refrigerator's cool air circulation axial flow fan | |
| KR20050024158A (en) | The fan of air-conditioner outdoor unit | |
| KR100525401B1 (en) | refrigerator | |
| KR100402477B1 (en) | Fan assembly for refrigerator | |
| KR100402478B1 (en) | Fan assembly for refrigerator | |
| JP2001124453A (en) | Refrigerator | |
| JP2002266796A (en) | Axial flow fan for condenser for refrigerator | |
| KR100473945B1 (en) | Refrigerator with efficient air circulation system | |
| KR100377623B1 (en) | Fan assembly for condenser of refrigerator | |
| KR20220077569A (en) | Centrifugal fan | |
| KR100525400B1 (en) | refrigerator | |
| KR100402885B1 (en) | Axial fan for Indoor unit of airconditioner | |
| KR100447405B1 (en) | Evaporation structure of refrigerator | |
| KR100273385B1 (en) | Axial fan for refrigerator | |
| KR100347890B1 (en) | Axial flow fan for refrigerator | |
| KR100347889B1 (en) | Axial flow fan of refrigerator | |
| KR100370044B1 (en) | fan with multi flow passage and structure of cool air passage with it in refrigerator | |
| KR100296294B1 (en) | Refrigerator | |
| KR100226840B1 (en) | Refrigerating cycle in refrigerator | |
| KR20220060844A (en) | Centrifugal fan for refrigerator | |
| KR200394146Y1 (en) | Refrigeration cycle of air conditioner | |
| KR100457568B1 (en) | Refrigerator's cool-air circulation blower | |
| KR100290850B1 (en) | Heat exchanger for refrigerator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A201 | Request for examination | ||
| N231 | Notification of change of applicant | ||
| E902 | Notification of reason for refusal | ||
| E701 | Decision to grant or registration of patent right | ||
| GRNT | Written decision to grant | ||
| FPAY | Annual fee payment |
Payment date: 20080926 Year of fee payment: 6 |
|
| LAPS | Lapse due to unpaid annual fee |