JP2007120380A - Engine cooling device - Google Patents

Engine cooling device Download PDF

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JP2007120380A
JP2007120380A JP2005312549A JP2005312549A JP2007120380A JP 2007120380 A JP2007120380 A JP 2007120380A JP 2005312549 A JP2005312549 A JP 2005312549A JP 2005312549 A JP2005312549 A JP 2005312549A JP 2007120380 A JP2007120380 A JP 2007120380A
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refrigerant
temperature
heater
control valve
engine
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Masazumi Yoshida
雅澄 吉田
Fujio Inoue
富士夫 井上
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Nippon Thermostat Co Ltd
Aisin Corp
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Aisin Seiki Co Ltd
Nippon Thermostat Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide an engine cooling system for controlling a flow rate corresponding to the temperature of a refrigerant with a simple constitution for improving cooling performance of an engine while providing the sure heating effect. <P>SOLUTION: This engine cooling device has a heater circulating flow passage 20 circulating via a heater core 21 of an air conditioner and a radiator circulating flow passage 10 circulating via a radiator, as a flow passage connected to a water pump P for forcibly feeding the engine cooling refrigerant and flowing the refrigerant, and has a mechanical control valve 22 in the heater circulating flow passage 20 for reducing opening as the temperature of the refrigerant changes to the high temperature side from the low temperature side. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、冷媒が循環する循環流路を有するエンジン冷却装置に関する。   The present invention relates to an engine cooling device having a circulation channel through which a refrigerant circulates.

従来、エンジン冷却水の流量を制御してラジエータの冷却性能を向上させるエンジン冷却装置が公知である。
例えば、特許文献１には、エンジンから流出したエンジン冷却水がラジエータを経由してエンジンに戻る主冷却水経路と、エンジン冷却水が空調設備であるヒータコアを経由してエンジンに戻る副冷却水経路と、副冷却水経路におけるエンジン冷却水の流通を制御する弁とを設けたエンジン冷却装置が開示してある。この装置には、エンジン冷却水の温度が設定温度以上のとき、弁の作動を制御して副冷却水経路におけるエンジン冷却水の流量を制御する制御手段が設けてある。 2. Description of the Related Art Conventionally, an engine cooling device that controls the flow rate of engine cooling water to improve the cooling performance of a radiator is known.
For example, Patent Document 1 discloses a main cooling water path in which engine cooling water flowing out from an engine returns to the engine via a radiator, and a sub cooling water path in which the engine cooling water returns to the engine via a heater core that is an air conditioning facility. And an engine cooling device provided with a valve for controlling the flow of engine cooling water in the sub-cooling water path. This device is provided with control means for controlling the operation of the valve to control the flow rate of the engine cooling water in the sub cooling water path when the temperature of the engine cooling water is equal to or higher than the set temperature.

当該弁の開閉制御は、ヒータコア付近のエンジン冷却水の水温を温度センサにより測定した温度測定値に基づき判断する。即ち、ヒータ作動時にエンジン冷却水とヒータコアとにおいて熱交換が行われる等して、温度測定値が設定値未満であれば副冷却水経路によりヒータコアへエンジン冷却水が供給される。一方、ヒータ不作動時にエンジン冷却水とヒータコアとにおいて熱交換が行われないとき、温度測定値が設定値以上であれば、制御装置が弁の開度を制御して、副冷却水経路によりヒータコアに供給されるエンジン冷却水の流通を停止又は制限する。   The valve opening / closing control is determined based on a temperature measurement value obtained by measuring the temperature of engine coolant near the heater core with a temperature sensor. That is, when the heater is operated, heat exchange is performed between the engine cooling water and the heater core. If the measured temperature value is less than the set value, the engine cooling water is supplied to the heater core through the sub cooling water path. On the other hand, when heat is not exchanged between the engine coolant and the heater core when the heater is not operating, if the measured temperature value is equal to or greater than the set value, the control device controls the opening of the valve, and the heater core is controlled by the sub-cooling water path. Stop or restrict the flow of engine coolant supplied to the engine.

これにより、ヒータ機能を即座に発揮することができると共に、ラジエータによるエンジン冷却機能を向上させることができる。   Thereby, while being able to exhibit a heater function immediately, the engine cooling function by a radiator can be improved.

特開２００２−２３５５４４号公報（特許請求の範囲、段落０００５、００１５、００１６等参照）JP 2002-235544 A (see claims, paragraphs 0005, 0015, 0016, etc.)

上述したエンジン冷却装置における弁は、当該エンジン冷却装置の外部に設けた制御手段によって開閉制御される（特許文献１における図１参照）。この制御手段は、温度測定値と設定値との比較を行うための電子制御回路を有するものである。このような制御手段は、一般に高コストであり、外部に設置スペースを必要とし、さらに、少なくとも制御手段の分の重量が増加するといった問題点を有する。さらに、この制御手段以外にも、例えば前記温度センサが必要不可欠であるため、装置の構成が複雑となる。   The valve in the engine cooling device described above is controlled to open and close by a control means provided outside the engine cooling device (see FIG. 1 in Patent Document 1). This control means has an electronic control circuit for comparing the measured temperature value with the set value. Such a control means is generally high in cost, requires an installation space outside, and has a problem that the weight of at least the control means increases. In addition to this control means, for example, the temperature sensor is indispensable, so that the configuration of the apparatus becomes complicated.

従って、本発明の目的は、確実な暖房効果を得るとともにエンジンの冷却性能を向上させるため、冷媒の温度に応じた流量制御を簡便な構成で行えるエンジン冷却システムを提供することにある。   Accordingly, an object of the present invention is to provide an engine cooling system capable of performing flow rate control according to the temperature of the refrigerant with a simple configuration in order to obtain a reliable heating effect and improve engine cooling performance.

上記目的を達成するための本発明に係るエンジン冷却装置の第１特徴構成は、エンジン冷却用の冷媒を圧送するポンプと接続するとともに前記冷媒を流通させる流路として、空調装置のヒータコアを経由して循環するヒータ循環流路と、ラジエータを経由して循環するラジエータ循環流路とを備え、前記冷媒の温度が低温側から高温側に変化するに従って開度を減少させる機械式の制御弁を前記ヒータ循環流路に備えた点にある。   In order to achieve the above object, a first characteristic configuration of an engine cooling device according to the present invention is connected to a pump that pumps a refrigerant for cooling an engine and passes through the heater core of an air conditioner as a flow path for circulating the refrigerant. A mechanical circulation control valve that decreases the opening degree as the temperature of the refrigerant changes from a low temperature side to a high temperature side, and a heater circulation flow path that circulates through the radiator and a radiator circulation flow path that circulates via a radiator. The heater circulation path is provided.

本構成の装置では、冷媒の温度が低温側から高温側に変化するに従って開度を減少させる機械式の制御弁をヒータ循環流路に備えてある。つまり、エンジン温度が未だ低く車室内温度も低い場合には、ヒータ循環流路を流れる冷媒量を確保し、確実な暖房効果を得る。一般に、ラジエータ循環流路は、エンジンが高温となった際に十分な冷却効果を得ることができるように流通量を確保してある。本構成であれば、エンジンが高温となり冷媒の温度が上昇すると、ヒータ循環流路に流れる冷媒量が減少し、ラジエータ循環流路に流れる冷媒量が増加するため、エンジン冷却性能の向上を図ることができる。
この場合に、本構成の装置では、機械式の制御弁を用いている。つまり、従来の装置のように、別途温度センサや電子制御回路が不要である。このため、本装置は、極めて簡便な構成でありながら冷媒の流通流路を適切に調節することができ、確実な暖房効果を得られるとともにエンジン冷却性能を向上させるエンジン冷却装置を提供することができる。
また、構成が簡便になるため、冷却装置のコストダウン・省スペース化・軽量化を図ることができる。 In the apparatus of this configuration, a mechanical control valve that decreases the opening degree as the refrigerant temperature changes from the low temperature side to the high temperature side is provided in the heater circulation channel. That is, when the engine temperature is still low and the passenger compartment temperature is low, the amount of refrigerant flowing through the heater circulation passage is ensured, and a reliable heating effect is obtained. Generally, the circulation amount of the radiator circulation channel is ensured so that a sufficient cooling effect can be obtained when the temperature of the engine becomes high. With this configuration, when the engine becomes hot and the temperature of the refrigerant rises, the amount of refrigerant flowing through the heater circulation passage decreases and the amount of refrigerant flowing through the radiator circulation passage increases, thereby improving engine cooling performance. Can do.
In this case, the apparatus of this configuration uses a mechanical control valve. That is, unlike the conventional apparatus, a separate temperature sensor and electronic control circuit are not required. For this reason, the present apparatus provides an engine cooling device that can appropriately adjust the flow path of the refrigerant while having an extremely simple configuration, and that can provide a reliable heating effect and improve the engine cooling performance. it can.
In addition, since the configuration is simple, the cost of the cooling device, space saving, and weight reduction can be achieved.

本発明に係るエンジン冷却装置の第２特徴構成は、前記制御弁を前記ヒータコアの下流に設けた点にある。   A second characteristic configuration of the engine cooling device according to the present invention is that the control valve is provided downstream of the heater core.

上記第２特徴構成によれば、空調装置が作動状態のとき、ヒータコアにおいて空調用空気と冷媒との間で熱交換が行われた後、ヒータコアから流出する冷媒の水温は、ヒータコアに流入する前の冷媒の水温より低くなる。一方、空調装置が不作動状態のときは、ヒータコアにおいて空調用空気と冷媒との間で行われる熱交換は僅かである。そのため、ヒータコアから流出する冷媒の水温は、ヒータコアに流入する前の冷媒の水温とほぼ等しい。
このように、ヒータコアの下流における冷媒の水温の変化は、ヒータコアで必要とされる熱量の増減と相関関係がある。従って、制御弁をヒータコアの下流に設けることで、冷媒の流通量をより適切に調節することができる。 According to the second characteristic configuration, when the air conditioner is in an operating state, after the heat exchange is performed between the air-conditioning air and the refrigerant in the heater core, the water temperature of the refrigerant flowing out of the heater core is before flowing into the heater core. It becomes lower than the water temperature of the refrigerant. On the other hand, when the air conditioner is in an inoperative state, heat exchange between the air for air conditioning and the refrigerant in the heater core is slight. Therefore, the water temperature of the refrigerant flowing out of the heater core is substantially equal to the water temperature of the refrigerant before flowing into the heater core.
Thus, the change in the coolant water temperature downstream of the heater core has a correlation with the increase or decrease in the amount of heat required in the heater core. Therefore, by providing the control valve downstream of the heater core, the refrigerant flow rate can be adjusted more appropriately.

本発明に係るエンジン冷却装置の第３特徴構成は、前記制御弁が、前記冷媒が流入する入側開口と、前記冷媒が排出される出側開口とを有する制御弁本体を備えると共に、当該制御弁本体の内部に、前記冷媒の温度に応じて体積変化する熱膨張体を内蔵する感温部と、前記熱膨張体の体積変化に応じて出退する軸部材と、前記軸部材の出退に連動して前記冷媒の流量を調節可能なバルブとを備え、前記入側開口・前記出側開口・前記感温部・前記軸部材・前記バルブを直線的に配置した点にある。   According to a third characteristic configuration of the engine cooling device according to the present invention, the control valve includes a control valve body having an inlet side opening through which the refrigerant flows and an outlet side opening through which the refrigerant is discharged, and the control Inside the valve body, a temperature sensing part containing a thermal expansion body that changes in volume according to the temperature of the refrigerant, a shaft member that moves in and out in response to a volume change in the thermal expansion body, and the movement of the shaft member And a valve capable of adjusting the flow rate of the refrigerant. The inlet opening, the outlet opening, the temperature sensing portion, the shaft member, and the valve are arranged linearly.

上記第３特徴構成によれば、制御弁を構成する各部材を直線的に配置することで、冷媒の流路抵抗の増加を抑制し、流路の圧力損失を低減することができる。よって、圧力損失の影響が出易い小断面の流路配管に対しても取り付けることができ、各種のエンジンの冷却装置として用いることができる。
また、当該制御弁は、ヒータ循環流路の何れの場所にも配置し易いものであり、エンジン冷却装置の設計の自由度が大きく向上する。 According to the third characteristic configuration, by arranging the members constituting the control valve linearly, it is possible to suppress an increase in the flow path resistance of the refrigerant and reduce the pressure loss of the flow path. Therefore, it can also be attached to a small-diameter passage pipe that is susceptible to pressure loss, and can be used as a cooling device for various engines.
In addition, the control valve can be easily placed anywhere in the heater circulation flow path, and the degree of freedom in designing the engine cooling device is greatly improved.

以下、本発明の実施例を図面に基づいて説明する。
本実施形態では、例えば一般車両のエンジン冷却装置を例示する。 Embodiments of the present invention will be described below with reference to the drawings.
In the present embodiment, for example, an engine cooling device for a general vehicle is illustrated.

図１に示すように、エンジン冷却装置Ｘは、エンジンＥから流出したエンジン冷却用の冷媒（以下、一例として「冷却水」を用いる）がラジエータ１１を経由してエンジンＥに戻るラジエータ循環流路１０と、エンジンＥから流出した冷却水が空調装置であるヒータコア２１を経由して循環するヒータ循環流路２０とを備える。   As shown in FIG. 1, the engine cooling device X has a radiator circulation passage in which engine cooling refrigerant (hereinafter, “cooling water” is used as an example) flowing out from the engine E returns to the engine E via the radiator 11. 10 and a heater circulation passage 20 through which cooling water flowing out from the engine E circulates via a heater core 21 that is an air conditioner.

冷却水は、エンジンＥのクランクシャフト（図外）によって駆動されるウォータポンプＰによって吸引され、エンジンＥの内部へ圧送される。冷却水はエンジンＥの内部を循環してエンジンＥの熱を吸収した後、ラジエータ循環流路１０、或いは、ヒータ循環流路２０に流出する。
ラジエータ循環流路１０に流出した冷却水は、ラジエータ１１に流入して冷却され、サーモスタット１２を経由してウォータポンプＰへ戻る。 The cooling water is sucked by a water pump P driven by a crankshaft (not shown) of the engine E and is pumped into the engine E. The cooling water circulates inside the engine E and absorbs the heat of the engine E, and then flows out to the radiator circulation passage 10 or the heater circulation passage 20.
The cooling water that has flowed out into the radiator circulation channel 10 flows into the radiator 11 to be cooled, and returns to the water pump P via the thermostat 12.

本実施形態のサーモスタット１２を図２に示す。
当該サーモスタット１２には、冷却水の温度に応じて駆動する感温部１２１を備えている。サーモスタット１２は、例えば、真鍮で形成する等、熱伝導性に優れた金属材料で形成する。当該感温部１２１の内部には、冷却水の温度に応じて膨張・収縮する、例えばワックス等の熱膨張体が内蔵してある。感温部１２１には、筒状のガイド部１２７を一体に形成してあり、このガイド部１２７に、熱膨張体の体積変化に応じて感温部１２１から出退する軸部材１２２を挿入してある。軸部材１２２の突出側端部は、サーモスタット１２の内壁に設けた固定部１３に保持されている。 The thermostat 12 of this embodiment is shown in FIG.
The thermostat 12 includes a temperature sensing unit 121 that is driven according to the temperature of the cooling water. The thermostat 12 is made of a metal material having excellent thermal conductivity, such as brass. Inside the temperature-sensitive part 121, a thermal expansion body such as wax, which expands and contracts according to the temperature of the cooling water, is incorporated. A cylindrical guide part 127 is formed integrally with the temperature sensing part 121, and a shaft member 122 that moves out of the temperature sensing part 121 according to the volume change of the thermal expansion body is inserted into the guide part 127. It is. The protruding side end of the shaft member 122 is held by a fixing portion 13 provided on the inner wall of the thermostat 12.

前記ガイド部１２７には、ラジエータ循環流路１０を開閉する第１バルブ１２３が外挿してある。この第１バルブ１２３とサーモスタット１２の筐体とに亘って第１スプリング１２４が装着してあり、この第１スプリング１２４によって第１バルブは、ラジエータ循環流路１０を閉じ状態とする方向に付勢されている。冷却水の温度が低いとき前記熱膨張体が収縮する。これにより、軸部材１２２が感温部１２１の内部に引退し、第１スプリング１２４によって第１バルブ１２３が閉じ方向に移動する。   A first valve 123 that opens and closes the radiator circulation channel 10 is extrapolated to the guide portion 127. A first spring 124 is mounted across the first valve 123 and the casing of the thermostat 12, and the first valve urges the first valve in a direction to close the radiator circulation passage 10. Has been. When the temperature of the cooling water is low, the thermal expansion body contracts. As a result, the shaft member 122 is retracted into the temperature sensing part 121, and the first valve 123 is moved in the closing direction by the first spring 124.

前記感温部１２１のうちガイド部１２７と反対側には、バイパス流路３０を開閉する第２バルブ１２６を備えている。第２バルブと感温部１２１との間には第２スプリング１２５を設けてある。第２スプリングにより、第２バルブは感温部１２１から離間する方向に付勢される。感温部１２１の熱膨張体が膨張すると、感温部１２１がバイパス流路３０の側に移動し、第２バルブ１２６がバイパス流路を閉塞する。
これら第１バルブ１２３及び第２バルブ１２６により、ラジエータ循環流路１０とバイパス流路３０とに流通する冷却水の流量が適宜調節され、その結果、冷却水の温度が所定の範囲に保持される。 A second valve 126 that opens and closes the bypass flow path 30 is provided on the opposite side of the temperature sensing part 121 from the guide part 127. A second spring 125 is provided between the second valve and the temperature sensing unit 121. The second valve biases the second valve in a direction away from the temperature sensing unit 121 by the second spring. When the thermal expansion body of the temperature sensing unit 121 expands, the temperature sensing unit 121 moves to the bypass channel 30 side, and the second valve 126 closes the bypass channel.
The flow rate of the cooling water flowing through the radiator circulation channel 10 and the bypass channel 30 is appropriately adjusted by the first valve 123 and the second valve 126, and as a result, the temperature of the cooling water is maintained within a predetermined range. .

図２（ａ）に示すごとく、エンジンＥを始動した直後など冷却水が低温状態にあるとき、第１バルブ１２３は閉状態となって、ウォータポンプＰとラジエータ循環流路１０とは遮断される。一方の第２バルブ１２６は開状態となり、ウォータポンプＰによって冷却水がバイパス流路３０を流通する。   As shown in FIG. 2A, when the cooling water is in a low temperature state, such as immediately after the engine E is started, the first valve 123 is closed and the water pump P and the radiator circulation channel 10 are shut off. . One of the second valves 126 is in an open state, and the cooling water flows through the bypass passage 30 by the water pump P.

尚、図示は省略するが、第１バルブ１２３が開いていない低温時（図２（ａ）の状態）において、仮にラジエータ循環流路１０の水圧が高まった場合には、冷却水がスプリング１２４の付勢力に抗して第１バルブ１２３を開方向に押し、冷却水がラジエータ循環流路１０を流通する。これにより、ラジエータ循環流路１０の水圧が高まって配管の接続部等に漏れ等の不都合が生じるのを防止している。   Although illustration is omitted, if the water pressure in the radiator circulation passage 10 is increased at a low temperature when the first valve 123 is not open (the state shown in FIG. 2A), the cooling water is supplied to the spring 124. The first valve 123 is pushed in the opening direction against the urging force, and the cooling water flows through the radiator circulation passage 10. As a result, the water pressure in the radiator circulation flow path 10 is increased, thereby preventing the occurrence of inconveniences such as leakage at the pipe connection portion.

一方、第１バルブ１２３が開くほどエンジンＥが暖まると、図２（ｂ）に示すごとく、感温部１２１の熱膨張体が膨張し、第１バルブ１２３が開状態となり、第２バルブ１２６が閉状態となる。冷却水はラジエータ循環流路１０を流通し、バイパス流路３０の流通が停止する。   On the other hand, when the engine E is warmed as the first valve 123 is opened, as shown in FIG. 2B, the thermal expansion body of the temperature sensing unit 121 is expanded, the first valve 123 is opened, and the second valve 126 is opened. Closed. The cooling water flows through the radiator circulation passage 10 and the circulation of the bypass passage 30 is stopped.

本発明のエンジン冷却装置においては、ヒータ循環流路２０にも当該流路における冷媒の流通量を決定する制御弁２２を設けている。ヒータ循環流路２０はラジエータ循環流路１０およびバイパス流路３０と並列であり、車室内の空調を行なうためのヒータコア２１を備えている。   In the engine cooling device of the present invention, the heater circulation channel 20 is also provided with a control valve 22 for determining the refrigerant flow rate in the channel. The heater circulation flow path 20 is in parallel with the radiator circulation flow path 10 and the bypass flow path 30 and includes a heater core 21 for air conditioning the vehicle interior.

ヒータコア２１は、例えば冷却水が流れる複数のパイプ（図示省略）に多数のフィンを設けて形成してある。ヒータコア２１の近傍には送風ファン（図示省略）を設けてあり、この送風ファンから供給する空調用空気を冷却水によって加熱する。この加熱空気を車室内に送風して室内を暖房する。   The heater core 21 is formed, for example, by providing a plurality of fins on a plurality of pipes (not shown) through which cooling water flows. A blower fan (not shown) is provided in the vicinity of the heater core 21, and the air-conditioning air supplied from the blower fan is heated by cooling water. This heated air is blown into the passenger compartment to heat the interior.

特に冬場等においては、エンジンＥを始動したのち、できるだけ早く車室内の温度を上昇させる必要がある。しかし、低温からの暖気運転中は冷却水の熱量が少ないため、ヒータコア２１に多くの冷却水を流すことで、暖房性能を高めることができる。一方、暖房完了後は、冷却水の熱量が多いため、ヒータコア２１には少しの冷却水を流すだけでよい。
ヒータ循環流路２０に制御弁２２を設けることにより、例えば、エンジン始動直後の暖機運転中には、ヒータ循環流路２０に冷却水を多く流すように調節し、一方、エンジンＥの温度が十分に高まった状態では、ヒータ循環流路２０の冷却水量を少なく設定して、ラジエータ循環流路１０に流す冷却水の量を増大させる。このような制御弁２２を用いることで、車室内の温度を迅速に高めるとともにエンジンの冷却性能を高めることができる。 Particularly in winter, it is necessary to raise the temperature in the passenger compartment as soon as possible after starting the engine E. However, since the amount of heat of the cooling water is small during the warm-up operation from a low temperature, the heating performance can be improved by flowing a large amount of cooling water through the heater core 21. On the other hand, after heating is completed, the amount of heat of the cooling water is large.
By providing the control valve 22 in the heater circulation channel 20, for example, during the warm-up operation immediately after engine startup, adjustment is made so that a large amount of cooling water flows through the heater circulation channel 20. In a sufficiently high state, the amount of cooling water flowing through the radiator circulation passage 10 is increased by setting the amount of cooling water in the heater circulation passage 20 small. By using such a control valve 22, the temperature in the passenger compartment can be quickly increased and the cooling performance of the engine can be increased.

当該制御弁２２の具体的構成と機能とを図３に基づいて説明する。
この制御弁２２は、冷却水の温度が低温側から高温側に変化するに従って開度を減少させる機械式の弁である。この制御弁２２の内部にも、冷却水の温度に応じて体積変化する熱膨張体を備えた感温部２２１を設けてある。この感温部２２１は、制御弁２２の筐体に固定してある。さらに、制御弁２２は、熱膨張体の体積変化により感温部２２１から出退する軸部材２２２と、当該軸部材２２２の出退に連動するリテーナ２２８とを備えている。当該リテーナ２２８には、ヒータ循環流路２０を開閉するバルブ２２３を備えている。リテーナ２２８と制御弁２２の筐体との間には第１スプリング２２４を設けてある。この第１スプリング２２４は、前記熱膨張体が収縮する際に、バルブ２２３が開状態となるようリテーナ２２８を感温部２２１の側に付勢する。 A specific configuration and function of the control valve 22 will be described with reference to FIG.
The control valve 22 is a mechanical valve that decreases the opening as the temperature of the cooling water changes from the low temperature side to the high temperature side. Inside the control valve 22 is also provided a temperature sensing part 221 provided with a thermal expansion body whose volume changes according to the temperature of the cooling water. The temperature sensing part 221 is fixed to the housing of the control valve 22. Further, the control valve 22 includes a shaft member 222 that moves out and withdraws from the temperature sensing part 221 due to a change in the volume of the thermal expansion body, and a retainer 228 that is interlocked with the shaft member 222 being moved in and out. The retainer 228 includes a valve 223 that opens and closes the heater circulation channel 20. A first spring 224 is provided between the retainer 228 and the housing of the control valve 22. The first spring 224 biases the retainer 228 toward the temperature sensing part 221 so that the valve 223 is opened when the thermal expansion body contracts.

冷却水が高温になると熱膨張体が膨脹し、第１スプリング２２４の付勢力に抗ってリテーナ２２８が移動する。リテーナ２２８の先端部には、第２スプリング２２５を介して前記バルブ２２３を設けてある。よって、リテーナ２２８が所定距離だけ移動するとバルブ２２３がヒータ循環流路２０を閉塞する。尚、ヒータ循環流路２０が閉塞されたのちに、ヒータ循環流路２０の内圧が高まった場合には、前記第２スプリング２２５が収縮して冷却水を流すことができる。   When the cooling water reaches a high temperature, the thermal expansion body expands, and the retainer 228 moves against the urging force of the first spring 224. The valve 223 is provided at the tip of the retainer 228 via a second spring 225. Therefore, when the retainer 228 moves by a predetermined distance, the valve 223 closes the heater circulation channel 20. In addition, when the internal pressure of the heater circulation channel 20 increases after the heater circulation channel 20 is closed, the second spring 225 contracts to allow cooling water to flow.

ただし、感温部１２１、２２１に冷却水の温度を感知させるため、第１バルブ１２３および第２バルブ２２３を完全に閉じないように構成する。例えば、バルブ２２３に微小な穴（直径２ｍｍ）を設ける、あるいは、制御弁本体Ｙの内側に複数の溝を設けておくと、バルブ２２３が閉状態となっても、少量の水を流通させることにより、感温部２２１の動作が機敏になり、ヒータ循環流路２０の流量調節をより適切に行うことができる。   However, the first valve 123 and the second valve 223 are configured not to be completely closed in order to cause the temperature sensing units 121 and 221 to sense the temperature of the cooling water. For example, if a minute hole (diameter 2 mm) is provided in the valve 223 or a plurality of grooves are provided inside the control valve body Y, a small amount of water can be circulated even when the valve 223 is closed. Thus, the operation of the temperature sensing unit 221 becomes agile and the flow rate of the heater circulation channel 20 can be adjusted more appropriately.

図３に示した如く、本制御弁２２を構成する各部材及び各部、例えば、冷却水を流入排出する入側開口２２６・出側開口２２７をはじめ、感温部２２１・軸部材２２２・バルブ２２３等は直線的に配置してある。このため、冷却水の流路抵抗を低減し、制御弁２２における圧力損失を最小に留めることができる。よって、圧力損失の影響が出易い小断面の流路配管に対しても特段の支障なく組み込むことができる。直線的な形状であれば、ヒータ循環流路２０の何れの場所にも配設し易くなり、ヒータ循環流路２０を設計する際の自由度が増す。   As shown in FIG. 3, each member and each part constituting the control valve 22, such as an inlet side opening 226 and an outlet side opening 227 through which cooling water flows in and out, a temperature sensing part 221, a shaft member 222, and a valve 223. Etc. are arranged linearly. For this reason, the flow path resistance of the cooling water can be reduced, and the pressure loss in the control valve 22 can be minimized. Therefore, it can be incorporated without any particular trouble into a small-diameter channel pipe that is easily affected by pressure loss. If it is a linear shape, it will be easy to arrange in any place of the heater circulation channel 20, and the degree of freedom when designing the heater circulation channel 20 will increase.

当該制御弁２２は、ヒータ循環流路２０の何れの個所に設けても良い。ただし、図１に示すごとく、ヒータコア２１の下流に設けるのが最も好ましい。ヒータの作動時には、ヒータコア２１から流出する冷却水の温度は、熱を放出した分だけ流入前の水温より低くなる。一方、ヒータを作動させていないときは、熱交換が行われないため、ヒータコア２１から流出する冷却水の水温は、流入前の水温とほぼ等しい。このように、ヒータコア２１の下流の水温は、ヒータの稼動状況をよく反映する。よって、この部位に制御弁２２を設けて、冷却水の流量を迅速に調節することで、使用者の要求に応じた暖房効果を得ることができる。   The control valve 22 may be provided at any location of the heater circulation channel 20. However, as shown in FIG. 1, it is most preferably provided downstream of the heater core 21. During the operation of the heater, the temperature of the cooling water flowing out of the heater core 21 is lower than the water temperature before the inflow by the amount of heat released. On the other hand, since the heat exchange is not performed when the heater is not operated, the water temperature of the cooling water flowing out from the heater core 21 is substantially equal to the water temperature before the inflow. Thus, the water temperature downstream of the heater core 21 well reflects the operating status of the heater. Therefore, the heating effect according to a user's request | requirement can be acquired by providing the control valve 22 in this site | part and adjusting the flow volume of cooling water rapidly.

本発明の制御弁２２を用いた効果を図４及び図５に示す。
図４は、制御弁２２をヒータコア２２の下流に設けた場合の、ヒータ出口水温と、ヒータ出口通路径との関係を示している。ヒータ出口での冷却水の水温が閾値Ａよりも低い場合、バルブ２２３を全開してヒータ循環流路２０の流量を最大に設定する。一方、水温が閾値Ｂよりも高い場合には、バルブ２２３が全絞り状態となって流量を最少に設定する。
ヒータ出口温度が閾値Ａと閾値Ｂとの間では、制御弁２２の開度は連続的に変化する。この図では、ヒータ出口水温が十分に高まった状態でもヒータ出口通路径が閉じられず、所定の流量が得られる場合を示している。これら閾値Ａ・Ｂ、あるいは、全絞り時の流水量は、その他のエンジン構成や、そのエンジンを利用する地域の気象条件等に応じて適宜変更自在である。 The effect of using the control valve 22 of the present invention is shown in FIGS.
FIG. 4 shows the relationship between the heater outlet water temperature and the heater outlet passage diameter when the control valve 22 is provided downstream of the heater core 22. When the coolant temperature at the heater outlet is lower than the threshold A, the valve 223 is fully opened to set the flow rate of the heater circulation passage 20 to the maximum. On the other hand, when the water temperature is higher than the threshold value B, the valve 223 is fully throttled to set the flow rate to the minimum.
When the heater outlet temperature is between the threshold value A and the threshold value B, the opening degree of the control valve 22 changes continuously. This figure shows a case where the heater outlet passage diameter is not closed and a predetermined flow rate is obtained even when the heater outlet water temperature is sufficiently increased. These thresholds A and B or the amount of water flow at the time of full throttle can be changed as appropriate according to other engine configurations, the weather conditions in the area where the engine is used, and the like.

図５には、制御弁２２を全開状態或いは全絞り状態に切り換えたとき、冷却水の流量がヒータ循環流路２０およびラジエータ循環流路１０においてどのように増減するかを示している。何れの流路においても、エンジン回転数が増大するに連れて、ウォータポンプＰの回転数が増加し、流量が増すことがわかる。制御弁２２を全開状態と全絞り状態とに切り換えると、各流路における流量が増減する。   FIG. 5 shows how the flow rate of the cooling water increases and decreases in the heater circulation passage 20 and the radiator circulation passage 10 when the control valve 22 is switched to the fully open state or the full throttle state. It can be seen that, in any flow path, as the engine speed increases, the water pump P speed increases and the flow rate increases. When the control valve 22 is switched between the fully open state and the fully throttled state, the flow rate in each flow path increases or decreases.

図５に示すように、ヒータ循環流路２０の流量は、ラジエータ循環流路１０の流量に比べて少ない。しかし、制御弁２２を絞ることにより、ヒータ循環流路２０の流量は減少し、その分、ラジエータ循環流路１０の流量が増加することを示している。つまり、本発明の制御弁２２は、従来、ヒータ循環流路２０に余剰に流れていた冷却水をラジエータ循環流路１０に流すことができるため、エンジン冷却性能を向上できる。エンジンの冷却性能に余剰がある場合には、ウォータポンプＰを小型化することで、コスト低減に貢献できる。   As shown in FIG. 5, the flow rate of the heater circulation channel 20 is smaller than the flow rate of the radiator circulation channel 10. However, it is shown that the flow rate of the heater circulation channel 20 is decreased by restricting the control valve 22, and the flow rate of the radiator circulation channel 10 is increased correspondingly. That is, the control valve 22 of the present invention can flow the cooling water that has conventionally flowed excessively into the heater circulation channel 20 to the radiator circulation channel 10, and therefore can improve the engine cooling performance. If there is a surplus in the cooling performance of the engine, the water pump P can be reduced in size to contribute to cost reduction.

本発明は、車両用のエンジン冷却装置に適用できる他、空調用のヒータ循環流路と、ラジエータ循環流路とを備えた装置であれば、何れの装置に対しても適用可能である。   The present invention can be applied to any device as long as it is a device provided with a heater circulation channel for air conditioning and a radiator circulation channel, in addition to being applicable to an engine cooling device for a vehicle.

本発明のエンジン冷却装置の概略図Schematic of the engine cooling device of the present invention ラジエータ循環流路に設けたサーモスタットの断面図Cross section of the thermostat installed in the radiator circulation flow path ヒータ循環流路に設けた制御弁の断面図Cross-sectional view of the control valve provided in the heater circulation flow path 制御弁の効果を示すグラフGraph showing the effect of the control valve 制御弁の効果を示すグラフGraph showing the effect of the control valve

符号の説明Explanation of symbols

Ｘ エンジン冷却装置
Ｐ ウォータポンプ
１０ ラジエータ循環流路
１１ ラジエータ
２０ ヒータ循環流路
２１ ヒータコア
２２ 制御弁
２２１ 感温部
２２２ 軸部材
２２３ バルブ
２２６ 入側開口
２２７ 出側開口 X Engine cooling device P Water pump 10 Radiator circulation passage 11 Radiator 20 Heater circulation passage 21 Heater core 22 Control valve 221 Temperature sensing part 222 Shaft member 223 Valve 226 Inlet side opening 227 Outlet side opening

Claims (3)

エンジン冷却用の冷媒を圧送するポンプと接続するとともに前記冷媒を流通させる流路として、空調装置のヒータコアを経由して循環するヒータ循環流路と、ラジエータを経由して循環するラジエータ循環流路とを備え、
前記冷媒の温度が低温側から高温側に変化するに従って開度を減少させる機械式の制御弁を前記ヒータ循環流路に備えたエンジン冷却装置。 A heater circulation path that circulates via a heater core of an air conditioner and a radiator circulation path that circulates via a radiator are connected to a pump that pumps a coolant for engine cooling and distributes the refrigerant. With
An engine cooling device provided with a mechanical control valve in the heater circulation flow path for reducing the opening degree as the temperature of the refrigerant changes from a low temperature side to a high temperature side. 前記制御弁を前記ヒータコアの下流に設けてある請求項１に記載のエンジン冷却装置。   The engine cooling device according to claim 1, wherein the control valve is provided downstream of the heater core. 前記制御弁は、前記冷媒が流入する入側開口と、前記冷媒が排出される出側開口とを有する制御弁本体を備えると共に、当該制御弁本体の内部に、前記冷媒の温度に応じて体積変化する熱膨張体を内蔵する感温部と、前記熱膨張体の体積変化に応じて出退する軸部材と、前記軸部材の出退に連動して前記冷媒の流量を調節可能なバルブとを備え、
前記入側開口・前記出側開口・前記感温部・前記軸部材・前記バルブを直線的に配置してある請求項１又は２に記載のエンジン冷却装置。 The control valve includes a control valve body having an inlet opening through which the refrigerant flows and an outlet opening through which the refrigerant is discharged, and has a volume in the control valve body according to the temperature of the refrigerant. A temperature sensing part containing a changing thermal expansion body, a shaft member that moves out and in accordance with a volume change of the thermal expansion body, and a valve that can adjust the flow rate of the refrigerant in conjunction with the movement of the shaft member With
The engine cooling device according to claim 1 or 2, wherein the inlet side opening, the outlet side opening, the temperature sensing portion, the shaft member, and the valve are linearly arranged.
JP2005312549A 2005-10-27 2005-10-27 Engine cooling device Pending JP2007120380A (en)

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WO2009104623A1 (en) * 2008-02-20 2009-08-27 トヨタ自動車株式会社 Thermostat device
JP2010031880A (en) * 2008-02-20 2010-02-12 Toyota Motor Corp Support member for thermostat device
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US10707497B2 (en) 2015-07-03 2020-07-07 Nissan Motor Co., Ltd. Fuel cell
JP2019138227A (en) * 2018-02-09 2019-08-22 本田技研工業株式会社 Internal combustion engine
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