JPS59176500A - Cooling fan device for internal-combustion engine - Google Patents
Cooling fan device for internal-combustion engineInfo
- Publication number
- JPS59176500A JPS59176500A JP4867983A JP4867983A JPS59176500A JP S59176500 A JPS59176500 A JP S59176500A JP 4867983 A JP4867983 A JP 4867983A JP 4867983 A JP4867983 A JP 4867983A JP S59176500 A JPS59176500 A JP S59176500A
- Authority
- JP
- Japan
- Prior art keywords
- fan
- fan device
- cooling fan
- combustion engine
- internal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/541—Specially adapted for elastic fluid pumps
- F04D29/545—Ducts
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
口比範囲を有する冷却効率の高い冷却ファン装置に関す
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a cooling fan device having a range of mouth ratios and having high cooling efficiency.
ファンは一般に薄肉鋼板をプレス成形して作シブレード
は円弧翼の２．４．６枚のものが多く、その半径は１５
０ｍｍ〜３００ｍｍ前後である。捷た最近はこの他に可
変速ファ７、可撓翼ファン、合成樹脂材ファンなどが騒
音防止、高速回転時の吸収馬力低減のために使用されて
いる。Fans are generally press-formed from thin-walled steel plates, and most of the blades are circular arc blades with a radius of 15.
It is around 0 mm to 300 mm. In addition to these, variable speed fans, flexible blade fans, synthetic resin fans, etc. are now being used to prevent noise and reduce absorbed horsepower during high speed rotation.
一定回転数におけるファン直径（ Ｄｆ）と送風量（Ｑ
）との関係は第２図に示す傾向をもち、なお冷却空気は
ファンと車速によって得られるものであり、低速時でも
必要量を確保できると同時に、高速時には動力消費を低
減し、過冷却を防止しかつ騒音発生を抑止するため所定
回転速度以上にならないように制限される。Fan diameter (Df) and air flow rate (Q) at a constant rotation speed
) has the tendency shown in Figure 2. Cooling air is obtained by the fan and vehicle speed, and the required amount can be secured even at low speeds, while at the same time reducing power consumption and preventing overcooling at high speeds. In order to prevent this and suppress the generation of noise, the rotation speed is limited so that it does not exceed a predetermined rotation speed.
第１図からも明らかなように、従来はファンの効率を萬
めるためにファン径を増してこれに対処してきたが、極
めて小型かつコンパクトな機関設訓と、はなはだしく制
約された装備空間のためファン径の増大には自ら限度が
ある。As is clear from Figure 1, in the past this has been dealt with by increasing the diameter of the fan in order to improve fan efficiency, but this has required extremely small and compact engine construction and extremely limited equipment space. Therefore, there is a limit to the increase in fan diameter.
一般に第１図に示すようにファ／を装置する機関の前端
の形状および該端、ファ７およびラフエータ間の相対間
隔は、車輛型式によシ多種多様であるが巨視的には大同
小異のパターンに納まるものと判断され、効率向上手段
の一つとしてファン装置の開口比、即ち冷却空気の流れ
がラジェータおよび機関前端との相対関係から好適な風
向きとなるようにして設計されたときの、流入側通流面
積に対する流出側通流面積の比が１を含めてこれば近い
前後の値を採らしめることが考えられる。Generally, as shown in Fig. 1, the shape of the front end of an engine equipped with a fan and the relative spacing between this end, the fan 7, and the luffator vary depending on the vehicle model, but macroscopically they follow a pattern that is largely the same. The inflow side is determined to be within the range of 100%, and the opening ratio of the fan device is designed as one means of improving efficiency, that is, the flow of cooling air is designed in a suitable direction from the relative relationship with the radiator and the front end of the engine. It is conceivable that the ratio of the flow area on the outflow side to the flow area may take a value close to 1, including 1.
本発明は上述の考察からラジェータ後方に接続するファ
ノンユラウドを利用して上記開口比の範囲に限定すると
とによってファ／の効率を向」ニすることを目的とする
。Based on the above considerations, it is an object of the present invention to improve the efficiency of the radiator by limiting the aperture ratio to the above range using a Fanon cloud connected to the rear of the radiator.
即ち、本発明の要旨は、
内燃機関用冷却ファン装置において、該冷却ファン装置
を通流する空気量に対する冷却ファン装置０９５乃至１
１５の範囲内にあることを特徴とする内燃機関用冷却フ
ァン装置にある。That is, the gist of the present invention is as follows: In a cooling fan device for an internal combustion engine, the cooling fan devices 095 to 1 with respect to the amount of air flowing through the cooling fan device.
15. A cooling fan device for an internal combustion engine, characterized in that the cooling fan device is within the range of 15.
図面を参照しつつ以下に本発明を説明する。The present invention will be explained below with reference to the drawings.
第１図は機関冷却／ステムの一般配置を示し、ラジェー
タ４、冷却ファン２および機関か整列配置すれ、ここに
３はファノノユラウドである。FIG. 1 shows the general arrangement of the engine cooling/stem, with the radiator 4, cooling fan 2, and engine aligned, where 3 is a fan head.
上記の配列を採る限り、前述のようにこれらの装置１，
２．４の相対間隔および相互形状関係は巨視的におおむ
ね画一的と判断され、ファン装置の開口比をファン効率
の最も高く維持できる範囲の値に限定することが本発明
の要旨である。As long as the above arrangement is adopted, these devices 1,
The relative spacing and mutual shape relationship of 2.4 is determined to be generally uniform macroscopically, and the gist of the present invention is to limit the aperture ratio of the fan device to a value within a range that can maintain the highest fan efficiency.
第３図はファンおよびファンンユラウドを含むファン装
置の部分側面図で、ボス部５に装着されたファ／２が図
の如（ラジェータから後続するファ／ンユラウド３によ
って囲われ空気流が案内される。図の左方が空気流入側
（添字■で示す）、右方が空気流出側（添字りで示す）
である。図から明らかなように、Ｉ）１３およびＤｌｌ
をそれぞれ流入側ンユラウドの径およびボス部の径、
またＤＤｓおよび１）Ｄｌをそれぞれ流出側のシュラウ
ドの径およＯ・ボス部の径とすれば、ファン装置の開口
比μであられされる。FIG. 3 is a partial side view of the fan device including the fan and the fan loudspeaker, in which the fan 2 mounted on the boss 5 is surrounded by the fan louds 3 following the radiator and the airflow is guided. The left side of the figure is the air inflow side (indicated by the subscript ■), and the right side is the air outflow side (indicated by the subscript ■).
It is. As is clear from the figure, I) 13 and Dll
are the diameter of the inflow side roundabout and the diameter of the boss part, respectively.
Further, if DDs and 1)Dl are the diameter of the shroud on the outflow side and the diameter of the O/boss portion, respectively, then the aperture ratio μ of the fan device is calculated.
実機についての数多くの統計的実験の結果、開口比とフ
ァン効率との関係は第４図の如くなシ、本発明はμを図
の０．９５から１１５の間に限定することにより、ファ
ンの高効率が得られる。As a result of numerous statistical experiments on actual machines, the relationship between the aperture ratio and the fan efficiency is as shown in Figure 4.The present invention improves the efficiency of the fan by limiting μ between 0.95 and 115 as shown in the figure. High efficiency can be obtained.
本発明は以」−のように構成されているから、ファン径
を増大することなく、構成機器の相対間隔および相互形
状関係を勘案しつつ上記の開口比値をファン装置に付与
させることにょシフアノの最高効率を得るととがてきる
。Since the present invention is configured as follows, it is possible to give the above-mentioned aperture ratio value to the fan device without increasing the fan diameter while taking into consideration the relative spacing and mutual shape relationship of the component devices. When you get the highest efficiency, you get the point.
第１図は、機関冷却ノステムの一般配置図、第２図は各
羽根数（Ｉ））をもっファ／の直径（、Ｄｆ）と送風量
（Ｑ）との関係図、第３図はファン装置の部分側面図、
第４図は開口比（μ）とファン効率（η、〕との関係図
である。
■・・機関
２・・ファン
３ ファノノユラウド
４・・ラジェータ
５・・・ボス部
第１図
Ｄｆ
第２図
第３図
〃
第４図Figure 1 is a general layout diagram of the engine cooling nostem, Figure 2 is a diagram of the relationship between the number of blades (I) and the diameter (Df) of each blade and the airflow rate (Q), and Figure 3 is a diagram of the relationship between the number of blades (I) and the air flow rate (Q). Partial side view of the device;
Fig. 4 is a diagram showing the relationship between the aperture ratio (μ) and fan efficiency (η, ).■...Engine 2...Fan 3...Radiator 5...Boss part Fig. 1Df Fig. 2 Figure 3 Figure 4
Claims (1)
を通流する空気量に対する冷却ファン装０９５乃至１１
５の範囲内にあることを特徴とする内燃機関用冷却ファ
ン装置。In a cooling fan device for an internal combustion engine, the cooling fan devices 095 to 11 correspond to the amount of air flowing through the cooling fan device.
5. A cooling fan device for an internal combustion engine, characterized in that the cooling fan device is within the range of 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4867983A JPS59176500A (en) | 1983-03-25 | 1983-03-25 | Cooling fan device for internal-combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4867983A JPS59176500A (en) | 1983-03-25 | 1983-03-25 | Cooling fan device for internal-combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS59176500A true JPS59176500A (en) | 1984-10-05 |
Family
ID=12810001
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4867983A Pending JPS59176500A (en) | 1983-03-25 | 1983-03-25 | Cooling fan device for internal-combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59176500A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61106913A (en) * | 1984-10-30 | 1986-05-24 | Hino Motors Ltd | Axial flow type cooling fan used in vehicle |
-
1983
- 1983-03-25 JP JP4867983A patent/JPS59176500A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61106913A (en) * | 1984-10-30 | 1986-05-24 | Hino Motors Ltd | Axial flow type cooling fan used in vehicle |
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