JPS6112513Y2 - - Google Patents
Info
- Publication number
- JPS6112513Y2 JPS6112513Y2 JP1981146856U JP14685681U JPS6112513Y2 JP S6112513 Y2 JPS6112513 Y2 JP S6112513Y2 JP 1981146856 U JP1981146856 U JP 1981146856U JP 14685681 U JP14685681 U JP 14685681U JP S6112513 Y2 JPS6112513 Y2 JP S6112513Y2
- Authority
- JP
- Japan
- Prior art keywords
- fan
- motor
- air conditioner
- duct
- differential pressure
- 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.)
- Expired
Links
- 230000003068 static effect Effects 0.000 claims description 33
- 230000001143 conditioned effect Effects 0.000 claims description 4
- 230000007423 decrease Effects 0.000 description 15
- 238000010586 diagram Methods 0.000 description 6
- 238000009429 electrical wiring Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Description
【考案の詳細な説明】
本考案は空気調和装置、詳しくはフアン及び熱
交換器を備えた空気調和機とダクトとから成り、
複数室に、前記ダクトを介して空調空気を供給す
るごとくした空気調和装置に関する。[Detailed description of the invention] The invention consists of an air conditioner, specifically an air conditioner equipped with a fan and a heat exchanger, and a duct.
The present invention relates to an air conditioner that supplies conditioned air to a plurality of rooms through the duct.
一般に、この種空気調和装置においては、第６
図に示すごとく、ダクト１先端側で各室２ａ，２
ｂ，２ｃの入口側にダンパー３…を設けると共
に、これらダンパー３…の開度を各室２ａ，２
ｂ，２ｃに取付ける室内サーモ４…により調節す
べく構成して、前記各室２ａ，２ｂ，２ｃの負荷
に応じた風量を供給すべく成していたのである。 Generally, in this type of air conditioner, the sixth
As shown in the figure, each chamber 2a, 2 on the tip side of the duct 1.
Dampers 3... are provided on the inlet sides of chambers 2a, 2c, and the opening degrees of these dampers 3 are adjusted to the respective chambers 2a, 2c.
The system is configured to be adjusted by indoor thermostats 4 attached to the chambers 2a, 2c, and to supply an air volume corresponding to the load of each chamber 2a, 2b, 2c.
尚５はフアン５１及び熱交換器５２を備えた空
気調和機である。 Note that 5 is an air conditioner equipped with a fan 51 and a heat exchanger 52.
ところが、前記各室２ａ，２ｂ，２ｃの負荷が
減少して、前記ダンパー３…が閉状態に近づくに
つれて、前記ダクト１内の静圧は増大し、騒音が
発生するばかりか、送風量の減少にもかかわらず
フアン動力は削減されず、エネルギーロスを生
じ、不経済となる問題があつたのである。 However, as the load on each of the chambers 2a, 2b, 2c decreases and the dampers 3 approach the closed state, the static pressure within the duct 1 increases, causing not only noise but also a decrease in the amount of air blown. Despite this, the fan power was not reduced, resulting in energy loss and uneconomical problems.
そこで従来においては、前記した問題を解決す
べく、前記ダクト１内の静圧を感知すると共に、
モジユトロールモータＭを介して前記フアン５１
のスクロールダンパー５３の開閉を制御する静圧
調節器Ｓを、ダクト１側と空気調和機５との間に
介装して、前記ダクト１の静圧を一定に制御すべ
く構成していたのである。 Conventionally, in order to solve the above-mentioned problem, the static pressure inside the duct 1 is sensed, and
The fan 51 via the module troll motor M
The static pressure regulator S for controlling the opening and closing of the scroll damper 53 is interposed between the duct 1 side and the air conditioner 5, and the static pressure in the duct 1 is controlled to be constant. be.
しかし前記静圧調節器Ｓは高価なものであり、
該静圧調節器Ｓを用いた空気調和装置は全体とし
てコスト高となるばかりか、前記ダクト１側の静
圧を一定に制御するものであるため、なおフアン
動力の削減については十分でない問題を残してい
たのである。 However, the static pressure regulator S is expensive;
The air conditioner using the static pressure regulator S is not only expensive as a whole, but also has the problem of not being able to reduce the fan power sufficiently because it controls the static pressure on the duct 1 side to a constant level. I had left it behind.
しかして本考案は以上の如き問題点に鑑み考案
したもので、必要送風量に応じたフアン動力で運
転でき、経済性の向上を計れながら、しかもダク
ト内静圧を適正値に保ち騒音を発生させることも
なく、さらには全体としてコストダウンの計れた
安価な空気調和装置を提供せんとするもので、フ
アンのモータとしてポールチエンジモータを用い
ると共に、前記フアンの吸込側に前記熱交換器を
配設し、フアンと熱交換器との間の空気通路に細
管を設けて、該細管に、前記空気調和機の機内静
圧と大気圧との差圧が設定値より小さくなると動
作する微差圧スイツチを設け、このスイツチの動
作により前記モータを高回転数から低回転数にポ
ールチエンジを行なうごとくしたことを特徴とす
るものである。 However, the present invention was devised in view of the above-mentioned problems, and it can be operated with fan power according to the required air flow, improving economic efficiency while maintaining the static pressure in the duct at an appropriate value and generating no noise. The purpose of the present invention is to provide an inexpensive air conditioner that can reduce the overall cost and reduce the overall cost.A pole change motor is used as the fan motor, and the heat exchanger is arranged on the suction side of the fan. A thin tube is provided in the air passage between the fan and the heat exchanger, and the thin tube is provided with a slight differential pressure that operates when the differential pressure between the internal static pressure of the air conditioner and the atmospheric pressure becomes smaller than a set value. The present invention is characterized in that a switch is provided, and the operation of the switch causes the pole change of the motor from a high rotation speed to a low rotation speed.
以下本考案の実施例を図面に基づいて説明す
る。 Embodiments of the present invention will be described below based on the drawings.
第１図において、５はフアン５１及び熱交換器
５２を備えた空気調和機であつて、前記熱交換器
５２を通過させて空調空気と成したものを、ダク
ト１を介して各室２ａ，２ｂ，２ｃに供給すべく
成しており、また、前記ダクト１の前記各室２
ａ，２ｂ，２ｃの入口側にはダンパー３…を設け
ると共に、これらダンパー３…の開度を、前記各
室２ａ，２ｂ，２ｃの負荷を感知する室内サーモ
４…により調節すべく成している。 In FIG. 1, reference numeral 5 denotes an air conditioner equipped with a fan 51 and a heat exchanger 52, and the air conditioned air is passed through the heat exchanger 52 and sent through a duct 1 to each room 2a, 2b, 2c, and each chamber 2 of the duct 1
Dampers 3... are provided on the inlet sides of the chambers 2a, 2b, 2c, and the opening degrees of these dampers 3 are adjusted by indoor thermostats 4... that sense the loads in the respective chambers 2a, 2b, 2c. There is.
而して本実施例においては、前記フアン５１の
モータ５３として4/6極ポールチエンジモータを
用いる一方、前記フアン５１の吸込側に細管５４
を設け、該細管５４により前記空気調和機５の機
内静圧を検出すると共に、該機内静圧と大気圧と
の差圧で動作する微差圧スイツチ５５を設けて、
該スイツチ５５により前記モータ５３のポールチ
エンジを行なうのである。 In this embodiment, a 4/6 pole chain motor is used as the motor 53 of the fan 51, and a thin tube 54 is provided on the suction side of the fan 51.
is provided, and detects the internal static pressure of the air conditioner 5 through the thin tube 54, and is provided with a slight differential pressure switch 55 that operates based on the differential pressure between the internal static pressure and atmospheric pressure,
The switch 55 is used to change the pole of the motor 53.
また、第２図は前記モータ５３の電気回路を示
しており、前記微差圧スイツチ５５の作動により
補助継電器Ｒ１が連動し、高速用電磁開閉器Ｒ２
と低速用電磁開閉器Ｒ３の切換えが行なえるごと
くに成つており、図中実線で示した状態では、前
記高速用電磁開閉器Ｒ２が閉じられ、前記モータ
５３が４極でおよそ1800r.p.m.の高速回転してお
り、また前記微差圧スイツチ５５が図中点線に示
した状態では、前記低速用電磁開閉器Ｒ３が閉じ
られ前記モータ５３が６極でおよそ1200r.p.m.の
低速回転することになる。 Further, FIG. 2 shows the electric circuit of the motor 53, in which the auxiliary relay R1 is operated in conjunction with the operation of the slight differential pressure switch 55, and the high-speed electromagnetic switch R2
In the state shown by the solid line in the figure, the high speed electromagnetic switch R2 is closed and the motor 53 has four poles and operates at approximately 1800 rpm. When the motor is rotating at high speed and the slight differential pressure switch 55 is in the state shown by the dotted line in the figure, the low speed electromagnetic switch R3 is closed and the motor 53 has six poles and rotates at a low speed of about 1200 rpm. Become.
尚、前記微差圧スイツチ５５は３乃50〓Aqの
差圧範囲で作動するものであり、また、前記モー
タ５３が４極運転から６極運転に切換わる場合
と、６極運転から４極運転に切換わる場合との間
に第３図に示すごとくのデイフアレンシヤルを設
定して、前記モータ５３の極数が頻繁に変換する
ことを防止している。 The slight differential pressure switch 55 operates within a differential pressure range of 3 to 50 Aq, and also when the motor 53 is switched from 4-pole operation to 6-pole operation, and when the motor 53 is switched from 4-pole operation to 4-pole operation. A differential as shown in FIG. 3 is set between the switching to operation and the number of poles of the motor 53 is prevented from changing frequently.
以上の如く構成した空気調和装置においては、
前記各室２ａ，２ｂ，２ｃの負荷が減少し、前記
室内サーモ４…により前記ダンパー３…が閉じる
方向に作動すると、前記ダクト１内抵抗は増大
し、該抵抗の増大により前記ダクト１内への前記
フアン５１による送風量は減少する。該送風量の
減少に伴ない、機内側静圧と大気圧との差圧も減
少することになり、該差圧の減少により前記微差
圧スイツチ５５が第２図中の点線位置に切換わ
り、前記モータ５３が４極運転から６極運転に、
換言すれば高速回転から低速回転に切換わるので
ある。 In the air conditioner configured as above,
When the load on each of the chambers 2a, 2b, 2c decreases and the indoor thermostat 4 operates the damper 3 in the closing direction, the resistance inside the duct 1 increases, and due to the increase in resistance, the internal resistance of the duct 1 increases. The amount of air blown by the fan 51 decreases. As the air flow rate decreases, the differential pressure between the static pressure inside the machine and the atmospheric pressure also decreases, and due to the decrease in differential pressure, the slight differential pressure switch 55 is switched to the dotted line position in FIG. 2. , the motor 53 changes from 4-pole operation to 6-pole operation,
In other words, high speed rotation is switched to low speed rotation.
一方、前記各室２ａ，２ｂ，２ｃの負荷が増大
し、前記室内サーモ４…により前記ダンパー３…
が開く方向に作動すると、前記ダクト１側抵抗は
減少し、該抵抗の減少により前記ダクト１内への
送風量は増大する。該送風量の増大に伴ない、前
記空調機５内静圧と大気圧との差圧も増大するこ
とになり、該差圧の増大により前記微差圧スイツ
チ５５が第２図中実線位置に切換わり、前記モー
タ５３が６極運転から４極運転に、換言すれば低
速回転から高速回転に切換わるのである。 On the other hand, the load on each of the chambers 2a, 2b, 2c increases, and the indoor thermostat 4 causes the damper 3...
When the duct 1 operates in the opening direction, the resistance on the duct 1 side decreases, and the amount of air blown into the duct 1 increases due to the decrease in resistance. With the increase in the amount of air blown, the differential pressure between the static pressure inside the air conditioner 5 and the atmospheric pressure also increases, and due to the increase in the differential pressure, the slight differential pressure switch 55 moves to the solid line position in FIG. As a result, the motor 53 switches from six-pole operation to four-pole operation, in other words, from low-speed rotation to high-speed rotation.
次に以上の動きを第４図に示した風量一静圧曲
線に基づいて説明する。 Next, the above movement will be explained based on the air volume vs. static pressure curve shown in FIG.
前記ダンパー３…を全開にした時の前記ダクト
１側の抵抗を表わす曲線をT0とし、前記空気調
和機５内の静圧を表わす曲線をT1とし、また４
極運転による前記フアン５１の特性曲線をF1、
６極運転による特性曲線をF2とした場合、前記
ダンパー３…を全開にして４極運転を行なうと、
前記曲線T0とF1との交点Ａにて運転が行なわ
れ、このときの風量がQ1で、ダクト１側静圧が
P0、機内側静圧がP1である。 A curve representing the resistance on the duct 1 side when the damper 3 is fully opened is T 0 , a curve representing the static pressure inside the air conditioner 5 is T 1 , and 4
The characteristic curve of the fan 51 due to polar operation is F 1 ,
If the characteristic curve for 6-pole operation is F 2 , if the damper 3 is fully opened and 4-pole operation is performed,
Operation is performed at the intersection A of the curves T 0 and F 1 , the air volume at this time is Q 1 , and the static pressure on the duct 1 side is
P 0 , and the static pressure inside the machine is P 1 .
そして前記各室２ａ，２ｂ，２ｃの負荷の減少
に伴ない、前記ダンパー３…は閉じられ、結果ダ
クト１側抵抗は増大してゆき、曲線T0は曲線T2
へと移ることになる。また前記ダクト１側抵抗の
増大に伴ない、前記フアン５１の風量は減少する
ことになり、即ち、前記特性曲線F1上をＡ点よ
りＢ点へと移動することになり、風量はQ1より
Q2に減少する。また風量の減少に伴なつて前記
機内側静圧と大気圧との差圧は前記曲線T1上を
移動して小さくなりP1の絶対値からP2の絶対値に
なる。そしてこの差圧がある設定値ＰC1より小さ
くなると前記微差圧スイツチ５５が作動して、前
記モータ５３は４極より６極に切換わり、前記
T2曲線とF1曲線の交点Ｂは、F2曲線上の点Ｃに
移転するのである。 As the load on each chamber 2a, 2b, 2c decreases, the dampers 3... are closed, and as a result, the resistance on the duct 1 side increases, and the curve T0 changes to the curve T2 .
will move to. Further, as the resistance on the duct 1 side increases, the air volume of the fan 51 decreases, that is, it moves from point A to point B on the characteristic curve F1 , and the air volume becomes Q1. Than
Q decreases to 2 . Further, as the air volume decreases, the differential pressure between the static pressure inside the machine and the atmospheric pressure moves on the curve T1 and decreases, changing from the absolute value of P1 to the absolute value of P2 . When this differential pressure becomes smaller than a certain set value P C1 , the slight differential pressure switch 55 is activated, the motor 53 is switched from 4 poles to 6 poles, and the motor 53 is switched from 4 poles to 6 poles.
The intersection point B of the T 2 curve and the F 1 curve is moved to the point C on the F 2 curve.
しかして前記フアン５１は特性曲線F2上を最
適風量値をとるべく移動するのである。 Thus, the fan 51 moves on the characteristic curve F2 to take the optimum air volume value.
一方、６極運転でかつ前記ダンパー３…をある
程度閉状態のＤ点で運転していて、前記各室２
ａ，２ｂ，２ｃの負荷が増大した場合には、まず
前記ダンパー３…が開かれ、ダクト１側抵抗曲線
はT2よりT0に移動し、該移動に伴ない前記Ｄ点
は曲線F2上を図中右方Ｅ点に移動してゆき、風
量はQ3よりQ4に増大すると共に機内側静圧はP3
よりP4へ減少する。そして前記機内側静圧と大気
圧との差圧が設定値ＰC2に達すると、前記微差圧
スイツチ５５が作動して前記モータ５３は６極運
転より４極運転に切換わるのである。該切換わり
によりＥ点はＦ点へと移転するのであり、該Ｆ点
は、その後曲線F1上を移動して風量最適位置に
落着くのである。 On the other hand, the 6-pole operation is performed and the damper 3 is operated at point D where the damper 3 is in a somewhat closed state, and each of the chambers 2
When the load on a, 2b, 2c increases, the dampers 3... are first opened, and the resistance curve on the duct 1 side moves from T 2 to T 0 , and with this movement, the D point changes to the curve F 2 As we move above to point E on the right side of the diagram, the air volume increases from Q 3 to Q 4 and the static pressure inside the machine increases to P 3
decreases to P 4 . When the differential pressure between the static pressure inside the machine and the atmospheric pressure reaches a set value P C2 , the slight differential pressure switch 55 is activated and the motor 53 is switched from 6-pole operation to 4-pole operation. As a result of this switching, point E moves to point F, which then moves on the curve F1 and settles at the optimum air volume position.
尚第３図にて説明したごとく、前記差圧の設定
値ＰC1とＰC2との間には適当なデイフアレンシヤ
ルを設けてあり、ＰC2＞ＰC1である。 As explained with reference to FIG. 3, an appropriate differential is provided between the set values P C1 and P C2 of the differential pressure, and P C2 > P C1 .
そして前記フアン５１の制御方式の相違による
フアン入力（KW）量の比較を行なつたものが第
５図であり、スクロールダンパーの開度調節によ
る場合ａ、サクシヨンベーンの開度調節による場
合ｂ、インバータ方式による場合ｃ、にくらべて
ポールチエンジによる場合ｄがフアン動力の削減
といつた点からいかに優れているかがよく表われ
ている。 FIG. 5 compares the amount of fan input (KW) due to the difference in the control method of the fan 51. A is a case where the scroll damper opening is adjusted, and b is a case where the suction vane opening is adjusted. , it clearly shows how superior case d, which uses a pole change, is in terms of reduction in fan power compared to case c, which uses an inverter system.
しかも前記微差圧スイツチ５５の作動を、前記
ダクト１側の静圧で制御する場合には、前記モー
タ５３の高速回転から低速回転へ移す場合と、低
速回転から高速回転へ移す場合との間に、前記し
たごとくのデイフアレンシヤルを設定しようとす
ると、該デイフアレンシヤル間における前記ダク
ト１側の静圧の差は大きいため、微差圧スイツチ
１つでは制御できず、２つの微差圧スイツチを要
することになる。 Moreover, when the operation of the slight differential pressure switch 55 is controlled by the static pressure on the duct 1 side, the difference between when the motor 53 is shifted from high-speed rotation to low-speed rotation and when it is shifted from low-speed rotation to high-speed rotation is When trying to set a differential as described above, the difference in static pressure on the duct 1 side between the differentials is large, so it cannot be controlled with one differential pressure switch, and two differential pressures are required. A differential pressure switch will be required.
これに対し、前記機内静圧と大気圧との差圧に
より前記微差圧スイツチ５５を制御する本考案の
ものでは、前記差圧の移動がわずかであるため、
１つの微差圧スイツチ５５で前記モータ５３のポ
ールチエンジを適切に行なえるのであり、コスト
ダウンが計れるのみならず、現地にて前記微差圧
スイツチ５５の静圧をセツトする場合にも１つの
セツトですみ、手間がかゝらないのである。 On the other hand, in the device of the present invention in which the slight differential pressure switch 55 is controlled by the differential pressure between the internal static pressure and the atmospheric pressure, the differential pressure moves only slightly.
The pole change of the motor 53 can be performed appropriately with one micro-differential pressure switch 55, which not only reduces costs, but also allows for setting the static pressure of the micro-differential pressure switch 55 on-site. All you need to do is set it up, and it doesn't take much time.
しかしてこの実施例の空気調和装置によれば、
前記各室２ａ，２ｂ，２ｃの負荷に応じて極めて
経済的に前記フアン５１の動力を適正値に制御で
きるのであり、また前記ダクト１側静圧も送風量
に応じた適切な静圧となすことができるので騒音
が発生することもなく、しかも前記微差圧スイツ
チ５５等の極数変換機構は、前記静圧調節器Ｓ等
のおよそ1/4程度の価格で装備可能であり、よつ
て空気調和装置全体としてもコストダウンの計れ
た安価なものとして提供できるのである。 However, according to the air conditioner of this embodiment,
The power of the fan 51 can be extremely economically controlled to an appropriate value according to the load of each chamber 2a, 2b, 2c, and the static pressure on the duct 1 side can also be adjusted to an appropriate static pressure according to the amount of air blown. Since it is possible to do this, no noise is generated, and the pole number changing mechanism such as the micro differential pressure switch 55 can be installed at about 1/4 the price of the static pressure regulator S, etc. The air conditioner as a whole can be provided at a low cost with reduced costs.
以上の説明により明らかなごとく、本考案で
は、フアン５１及び熱交換器５２を備えた空気調
和機５とダクト１とから成り、複数室２ａ，２
ｂ，２ｃ…に、各室内サーモ４により開度を調節
される各ダンパー３から前記ダクト１を介して空
調空気を供給するごとくした空気調和装置におい
て、前記フアン５１のモータ５３としてポールチ
エンジモータを用いると共に、前記フアン５１の
吸込側に前記熱交換器５２を配設し、フアン５１
と熱交換器５２との間の空気通路に細管５４を設
けて、該細管５４に、前記空気調和機５の機内静
圧と大気圧との差圧が設定値より小さくなると動
作する微差圧スイツチ５５を設け、このスイツチ
５５の動作により前記モータ５３を高回転数から
低回転数にポールチエンジを行なうごとくしたか
ら、各ダンパ３が全開から閉じる方向に作動し
て、ダクト１を介して各室へ供給する必要な送風
量が現象した場合には、フアン５１のモータ５３
を高回転数から低回転数にポールチエンジを行な
うことにより、前記必要送風量に応じたフアン動
力で運転でき、従つて、前記フアン５１の動力を
削減することができて、エネルギーロスを小さく
でき、経済性を向上できたのである。 As is clear from the above explanation, the present invention consists of an air conditioner 5 equipped with a fan 51 and a heat exchanger 52, and a duct 1, and has multiple rooms 2a, 2.
b, 2c..., in an air conditioner in which conditioned air is supplied through the duct 1 from each damper 3 whose opening degree is adjusted by each indoor thermostat 4, a pole change motor is used as the motor 53 of the fan 51. In addition, the heat exchanger 52 is disposed on the suction side of the fan 51, and the fan 51
A thin tube 54 is provided in the air passage between the air conditioner 5 and the heat exchanger 52, and the thin tube 54 is provided with a slight differential pressure that operates when the differential pressure between the internal static pressure of the air conditioner 5 and the atmospheric pressure becomes smaller than a set value. A switch 55 is provided, and the operation of the switch 55 pole-changes the motor 53 from a high rotation speed to a low rotation speed. If the necessary amount of air to be supplied to the room is insufficient, the motor 53 of the fan 51
By changing the pole from a high rotation speed to a low rotation speed, it is possible to operate the fan 51 with a power corresponding to the required airflow amount, and therefore, the power of the fan 51 can be reduced, and energy loss can be reduced. This made it possible to improve economic efficiency.
しかも、前記したポールチエンジに伴ない、前
記ダクト１内の静圧も低下させることができるの
で、該ダクト１にて発生する騒音を防止できるの
である。 Moreover, since the static pressure inside the duct 1 can be reduced due to the above-mentioned pole change, noise generated in the duct 1 can be prevented.
その上、フアン５１の吸込側の静圧を検知する
ことにより、空気調和機５の機内静圧と大気圧と
の差圧によつて微差圧スイツチ５５を制御するよ
うにしたから、ダクト１側の静圧で制御する場合
に比し、前記差圧の移動（変化量）がわずかであ
るため、モータ５３をポールチエンジさせるに際
し、例えば高速回転から低速回転へ移す場合と、
低速回転から高速回転へ移す場合との間で、デイ
フアレンシヤルを設定する場合でも、１つの微差
圧スイツチ５５で前記モータ５３のポールチエン
ジを適切に行なえるのであり、これによりコスト
ダウンが計れるのみならず、現地にて前記微差圧
スイツチ５５の設定値をセツトする場合にも１つ
のセツトで済み、手間がかゝらないのである。 Furthermore, by detecting the static pressure on the suction side of the fan 51, the slight differential pressure switch 55 is controlled based on the differential pressure between the internal static pressure of the air conditioner 5 and the atmospheric pressure. Since the movement (amount of change) of the differential pressure is small compared to when controlling using the static pressure on the side, when changing the pole of the motor 53, for example, when moving from high speed rotation to low speed rotation,
Even when setting a differential between low-speed rotation and high-speed rotation, the pole change of the motor 53 can be performed appropriately with one small differential pressure switch 55, thereby reducing costs. Not only can it be measured, but even when setting the setting value of the slight differential pressure switch 55 at the site, only one setting is required, which saves time and effort.
さらにはフアン動力の制御機構は特に安価に装
備可能なものであり、空気調和装置全体としても
コストダウンが計れた安価なものと成すことがで
きたのである。 Furthermore, the fan power control mechanism can be installed at a particularly low cost, making it possible to reduce the cost of the entire air conditioner and make it inexpensive.
第１図は本考案の実施例を示す概略説明図、第
２図はモータの電気配線図、第３図はデイフアレ
ンシヤル説明図、第４図は風量−静圧曲線を示す
グラフ、第５図は風量変化に伴なう所要動力の比
較図、第６図は従来例を示す概略説明図である。
１……ダクト、５……空気調和機、２ａ，２
ｂ，２ｃ……室、５１……フアン、５２……熱交
換器、５３……モータ、５４……細管、５５……
微差圧スイツチ。
Fig. 1 is a schematic diagram showing an embodiment of the present invention, Fig. 2 is a motor electrical wiring diagram, Fig. 3 is a differential diagram, Fig. 4 is a graph showing an air volume-static pressure curve, and Fig. 4 is a graph showing an air volume-static pressure curve. FIG. 5 is a comparison diagram of the required power as the air volume changes, and FIG. 6 is a schematic explanatory diagram showing a conventional example. 1... Duct, 5... Air conditioner, 2a, 2
b, 2c...Chamber, 51...Fan, 52...Heat exchanger, 53...Motor, 54...Thin tube, 55...
Fine differential pressure switch.
Claims (1)
機５とダクト１とから成り、複数室２ａ，２ｂ，
２ｃ…に、各室内サーモ４により開度を調節され
る各ダンパー３から前記ダクト１を介して空調空
気を供給するごとくした空気調和装置において、
前記フアン５１のモータ５３としてポールチエン
ジモータを用いると共に、前記フアン５１の吸込
側に前記熱交換器５２を配設し、フアン５１と熱
交換器５２との間の空気通路に細管５４を設け
て、該細管５４に、前記空気調和機５の機内静圧
と大気圧との差圧が設定値より小さくなると動作
する微差圧スイツチ５５を設け、このスイツチ５
５の動作により前記モータ５３を高回転数から低
回転数にポールチエンジを行なうごとくしたこと
を特徴とする空気調和装置。 It consists of an air conditioner 5 equipped with a fan 51 and a heat exchanger 52, and a duct 1, and has multiple rooms 2a, 2b,
2c..., in an air conditioner in which conditioned air is supplied via the duct 1 from each damper 3 whose opening degree is adjusted by each indoor thermostat 4,
A pole change motor is used as the motor 53 of the fan 51, the heat exchanger 52 is disposed on the suction side of the fan 51, and a thin tube 54 is provided in the air passage between the fan 51 and the heat exchanger 52. , a fine differential pressure switch 55 is provided in the thin tube 54 and operates when the differential pressure between the internal static pressure of the air conditioner 5 and the atmospheric pressure becomes smaller than a set value.
5. An air conditioner characterized in that the operation of step 5 causes the motor 53 to perform a pole change from a high rotation speed to a low rotation speed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14685681U JPS5851133U (en) | 1981-10-01 | 1981-10-01 | air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14685681U JPS5851133U (en) | 1981-10-01 | 1981-10-01 | air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5851133U JPS5851133U (en) | 1983-04-06 |
| JPS6112513Y2 true JPS6112513Y2 (en) | 1986-04-18 |
Family
ID=29939739
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14685681U Granted JPS5851133U (en) | 1981-10-01 | 1981-10-01 | air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5851133U (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5326447A (en) * | 1976-08-24 | 1978-03-11 | Tokujiyu Kougiyou Kk | Duct interior static pressure controller in air conditioning system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51105859U (en) * | 1975-02-14 | 1976-08-24 |
-
1981
- 1981-10-01 JP JP14685681U patent/JPS5851133U/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5326447A (en) * | 1976-08-24 | 1978-03-11 | Tokujiyu Kougiyou Kk | Duct interior static pressure controller in air conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5851133U (en) | 1983-04-06 |
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