JP2573870B2 - Cooling water flow control device for internal combustion engine - Google Patents
Cooling water flow control device for internal combustion engineInfo
- Publication number
- JP2573870B2 JP2573870B2 JP63278049A JP27804988A JP2573870B2 JP 2573870 B2 JP2573870 B2 JP 2573870B2 JP 63278049 A JP63278049 A JP 63278049A JP 27804988 A JP27804988 A JP 27804988A JP 2573870 B2 JP2573870 B2 JP 2573870B2
- Authority
- JP
- Japan
- Prior art keywords
- cooling water
- water temperature
- temperature
- engine
- flow control
- 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 - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2023/00—Signal processing; Details thereof
- F01P2023/08—Microprocessor; Microcomputer
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
- F01P2025/08—Temperature
- F01P2025/13—Ambient temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
- F01P2025/08—Temperature
- F01P2025/32—Engine outcoming fluid temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
- F01P7/167—Controlling of coolant flow the coolant being liquid by thermostatic control by adjusting the pre-set temperature according to engine parameters, e.g. engine load, engine speed
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Control Of The Air-Fuel Ratio Of Carburetors (AREA)
Description
【発明の詳細な説明】 ［発明の目的］ ＜産業上の利用分野＞ 本発明は、機関の冷却水の流量を制御するための流量
制御弁を有する内燃機関の冷却水流量制御装置に関す
る。The present invention relates to a cooling water flow control device for an internal combustion engine having a flow control valve for controlling the flow rate of cooling water for an engine.
＜従来の技術＞ 一般に自動車用エンジンに於ては、エンジン内のウォ
ータジャケットとラジエータとを連通する冷却水通路の
エンジン側出口部または入口部にサーモスタットを設け
ており、暖機運転中にはラジエータに冷却水が流れない
ようにして暖機を促進させるべく、サーモスタットによ
り冷却水通路を閉じ、暖機後にはオーバヒートを防止す
るべく、冷却水をラジエータに流して循環させるように
冷却水通路を開くようにしている。このサーモスタット
には、感温部材としてサーモワックスを用いており、そ
のサーモワックスの膨脹収縮により弁体を作動させてい
るが、概ね開閉の２位置制御しかできず、高精度な制御
が困難である。<Prior Art> In general, in an automobile engine, a thermostat is provided at an engine-side outlet or an inlet of a cooling water passage communicating between a water jacket and a radiator in the engine. The cooling water passage is closed by a thermostat in order to prevent the cooling water from flowing into the radiator and promote the warm-up, and the cooling water passage is opened so that the cooling water flows to the radiator and circulates after the warm-up to prevent overheating. Like that. In this thermostat, thermowax is used as a temperature-sensitive member, and the valve element is operated by expansion and contraction of the thermowax. However, only two positions of opening and closing can be controlled, and high-precision control is difficult. .
ところで、軽負荷時には熱損失の軽減と排気の浄化を
促進するためにラジエータへの循環水量を比較的少なく
し、高負荷時には吸気充てん効率を向上させるためにラ
ジエータへの循環水量を比較的多くすると良く、運転状
態に応じて冷却水の循環量を変化させることが望まし
い。例えば、特開昭59−226225号公報には、負圧駆動型
の流量制御弁と、制御弁とは別個に設けた水温センサと
を用い、運転状態としてのエンジン回転数及び吸気負圧
により目標水温をデータマップから呼び出して、その目
標水温と上記水温センサにより検出した冷却水温度とを
一致させるように弁開度をフィードバック制御するよう
にしたものが開示されている。By the way, when the load is light, the amount of circulating water to the radiator is relatively small in order to reduce heat loss and promote purification of exhaust gas, and when the load is high, the amount of circulating water to the radiator is relatively large in order to improve intake filling efficiency. It is desirable to change the circulation amount of the cooling water according to the operation state. For example, Japanese Patent Application Laid-Open No. 59-226225 discloses a method in which a negative pressure drive type flow control valve and a water temperature sensor provided separately from the control valve are used, and a target is determined by an engine speed and an intake negative pressure as an operation state. A water temperature is called from a data map, and the valve opening is feedback-controlled so that the target water temperature matches the cooling water temperature detected by the water temperature sensor.
しかしながら、上記構造によると、冷却水のエンジン
入口部に水温センサが設けられており、エンジン内の冷
却水の最大温度を管理することが難しく、運転状態の変
化による冷却水温度の変化に対して最適な制御を行うこ
とが困難である。また、外気温度に関係なく制御するた
め外気温度の違いに対して精度良く制御することができ
ないばかりでなく、フィードバック制御を行っているこ
とから、例えば空調装置としてのヒータコアに冷却水が
流れた際には、その温度変化に対して応答遅れを生じる
虞れがある。However, according to the above structure, the water temperature sensor is provided at the engine inlet of the cooling water, and it is difficult to manage the maximum temperature of the cooling water in the engine. It is difficult to perform optimal control. In addition, since control is performed irrespective of the outside air temperature, it is not only impossible to accurately control the difference in outside air temperature, but also because feedback control is performed, for example, when cooling water flows through a heater core as an air conditioner. May have a response delay with respect to the temperature change.
＜発明が解決しようとする課題＞ このような従来技術の問題点に鑑み、本発明の主な目
的は、機関の運転状態に応じて常に最適な制御が可能な
内燃機関の冷却水流量制御装置を提供することにある。<Problems to be solved by the invention> In view of the problems of the related art, a main object of the present invention is to provide a cooling water flow control device for an internal combustion engine capable of always performing optimal control according to the operating state of the engine. Is to provide.
［発明の構成］ ＜課題を解決するための手段＞ このような目的は、本発明によれば、機関とラジエー
タとを連通する冷却水通路中に介装された流量制御弁
と、冷却水の前記機関の出口部の温度を検出する手段
と、前記機関の運転状態を検出する手段と、外気温度を
検出する手段と、前記運転状態の検出結果に基づいて目
標水温を設定する手段と、前記冷却水温よりも前記目標
水温の方が高い暖機中の場合には両者間の温度偏差が大
きくなるに連れて補正放熱量の正の値から負の値に至る
ように漸減させる第１の関数曲線を選択し、前記冷却水
温が前記目標水温よりも高くかつ所定の上限水温よりも
低い暖機後の場合には両者間の温度偏差が大きくなるに
連れて補正放熱量を漸増させる第２の関数曲線を選択す
る関数選択手段と、前記冷却水温度と前記目標水温との
偏差に基づいて前記第１または第２の関数曲線により求
めた補正放熱量を制御補正放熱量として設定する手段
と、前記制御補正放熱量を達成するべく前記各検出手段
による検出結果に基づいて前記流量制御弁を制御する手
段とを有することを特徴とする内燃機関の冷却水流量制
御装置を提供することにより達成される。特に、前記流
量制御弁が、ラジエータ通路とバイパス通路との開閉状
態を互いに相反する状態にし得るように設けられている
と良い。[Constitution of the Invention] <Means for Solving the Problems> According to the present invention, the object of the present invention is to provide a flow control valve interposed in a cooling water passage communicating an engine and a radiator; Means for detecting the temperature of the outlet of the engine, means for detecting the operating state of the engine, means for detecting the outside air temperature, means for setting a target water temperature based on the detection result of the operating state, In the case of warm-up in which the target water temperature is higher than the cooling water temperature, a first function for gradually decreasing the corrected heat release amount from a positive value to a negative value as the temperature deviation between the two increases. Selecting a curve, and in a case where the cooling water temperature is higher than the target water temperature and lower than a predetermined upper limit water temperature after warm-up, the correction heat release amount is gradually increased as the temperature deviation between the two increases. Function selecting means for selecting a function curve, and the cooling water Means for setting a corrected heat radiation amount determined by the first or second function curve based on a deviation between the temperature and the target water temperature as a control corrected heat radiation amount, and each of the detecting means to achieve the control corrected heat radiation amount And means for controlling the flow control valve based on the detection result of the above. In particular, it is preferable that the flow control valve is provided so that the open / close state of the radiator passage and the bypass passage can be set to mutually opposing states.
＜作用＞ このようにすれば、機関の運転状態の変化に応じた補
正放熱量を冷却水温に対する目標水温の高低の違いを考
慮して求めて、その補正放熱量を達成するべく流量制御
弁により制御することから、冷却水の循環量を運転状態
の変化に応じてフィードフォワード制御することができ
る。また、流量制御弁をラジエータ通路とバイパス通路
との開閉を互いに相反する状態にし得るように設けるこ
とにより、いずれか一方の通路にのみ冷却水を流すこと
ができ、各状態における冷却水の温度変化を早めて制御
速度を高めることができる。<Operation> In this way, a corrected heat radiation amount corresponding to a change in the operating state of the engine is determined in consideration of a difference in the target water temperature with respect to the cooling water temperature, and the flow control valve is used to achieve the corrected heat radiation amount. By performing the control, the amount of circulation of the cooling water can be feedforward controlled in accordance with the change in the operation state. Further, by providing the flow control valve so that the opening and closing of the radiator passage and the bypass passage can be made to be in a state opposite to each other, the cooling water can flow only in one of the passages. And control speed can be increased.
＜実施例＞ 以下、本発明の好適実施例を添付の図面について詳し
く説明する。Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.
第１図は、本発明が適用されたエンジンの冷却水流量
制御装置を模式的に示す全体図であり、エンジン１に設
けられたウォーターポンプ２の吸込通路10とラジエータ
３の下部とが、入口側通路４及び流量制御弁５を介して
互いに連通している。エンジン１内には、ウォータポン
プ２により吐出される冷却水をエンジン１の各部に通す
ためのウォータジャケット７が郭成されており、ウォー
タジャケット７とラジエータ３の上部とが出口側通路６
を介して互いに連通している。FIG. 1 is an overall view schematically showing a cooling water flow control device for an engine to which the present invention is applied, in which a suction passage 10 of a water pump 2 provided in an engine 1 and a lower portion of a radiator 3 have an inlet. They communicate with each other via the side passage 4 and the flow control valve 5. The engine 1 is provided with a water jacket 7 for passing cooling water discharged from the water pump 2 to each part of the engine 1. The water jacket 7 and an upper part of the radiator 3 are connected to an outlet passage 6.
Are in communication with each other.
また、ウォータジャケット７は、バイパス通路８を介
して流量制御弁５に通じており、入口側通路４を閉じる
向きに流量制御弁５が作動した際には、ウォータジャケ
ット７内の冷却水が、図の想像線により示される矢印の
ようにバイパス通路８を介して循環可能なようにされて
いると共に、流量制御弁５により入口側通路４を全開状
態にした際には、バイパス通路８が全閉状態になり、図
の実線により示される矢印のように循環する。なお、ウ
ォータジャケット７内の冷却水は、暖房用のヒータコア
９を介しても循環するようにされており、ヒータ或いは
エアコンディショナを作動させた時には、ウォータジャ
ケット７内の冷却水が、図の破線の矢印のようにヒータ
コア９内を流れることとなる。The water jacket 7 communicates with the flow control valve 5 through the bypass passage 8. When the flow control valve 5 is operated in a direction to close the inlet passage 4, the cooling water in the water jacket 7 is discharged. As shown by an arrow indicated by an imaginary line in the figure, the bypass passage 8 can be circulated through the bypass passage 8, and when the inlet side passage 4 is fully opened by the flow control valve 5, the bypass passage 8 is fully opened. It is closed and circulates as indicated by the solid line arrow. The cooling water in the water jacket 7 is circulated through the heater core 9 for heating. When the heater or the air conditioner is operated, the cooling water in the water jacket 7 It flows inside the heater core 9 as indicated by the dashed arrow.
流量制御弁５は、第２図に良く示されるようにに、入
口側通路４と吸込通路10との間に設けられた弁室14と、
前記したようにラジエータ通路の入口側通路４とバイパ
ス通路８との開閉状態を互いに相反する状態にし得る弁
体11と、その弁体11を直線的に往復動させるための直動
型ステッピングモータ12とからなる。即ち、ステッピン
グモータ12の駆動シャフト16の先端に弁体11が固設され
ていると共に、駆動シャフト16の基部に形成されたねじ
部とロータ13の内ねじ部とが互いに螺合しており、ロー
タ13が正逆転することにより駆動シャフト16が軸線方向
に往復動するようにされている。なお、ステッピングモ
ータ12は、高トルクが得られる所謂ハイブリッド型から
なる。As shown in FIG. 2, the flow control valve 5 includes a valve chamber 14 provided between the inlet side passage 4 and the suction passage 10,
As described above, the valve body 11 that can make the opening and closing states of the inlet side passage 4 and the bypass passage 8 of the radiator passage opposite to each other, and the direct-acting stepping motor 12 for linearly reciprocating the valve body 11 Consists of That is, the valve body 11 is fixedly provided at the tip of the drive shaft 16 of the stepping motor 12, and a screw portion formed at the base of the drive shaft 16 and an inner screw portion of the rotor 13 are screwed together, The drive shaft 16 reciprocates in the axial direction when the rotor 13 rotates forward and backward. Note that the stepping motor 12 is of a so-called hybrid type that can obtain high torque.
また弁体11には、第２図の想像線により示されるよう
に入口側通路４を全閉にした状態に於て、ラジエータ３
側の内圧が異常に高まった際の異常圧力を逃し得る付勢
力をもって閉弁方向にばね付勢された副弁体15が設けら
れている。即ち、副弁体15のばね付勢力以上にラジエー
タ３側の内圧が高まった際には副弁体15が開弁するた
め、入口側通路４内の冷却水を弁体11内を介して吸込通
路10側に流すことができる。In addition, as shown by the imaginary line in FIG. 2, the valve body 11 has the radiator 3 in a state where the inlet side passage 4 is fully closed.
An auxiliary valve body 15 is provided which is spring-biased in the valve closing direction with a biasing force capable of releasing abnormal pressure when the internal pressure on the side abnormally increases. That is, when the internal pressure on the radiator 3 side becomes higher than the spring biasing force of the sub-valve 15, the sub-valve 15 opens, so that the cooling water in the inlet side passage 4 is sucked through the valve 11. It can flow to the passage 10 side.
前記したステッピングモータ12は第１図に示されるよ
うに制御装置17からの出力信号により駆動されるが、本
装置にあっては、入口側通路４の全開状態を流量制御弁
５の初期状態としており、例えばイグニッションをオン
した際に入口側通路４を全開にする向きに弁体11を移動
させるべく、ステッピングモータ12を回転させる。ステ
ッピングモータ12の後端部には例えばリミットスイッチ
型の位置センサ18が設けられており、駆動シャフト16の
後端が位置センサ18に衝当した際にその信号を制御装置
17に送り、弁体11の初期位置とするようにされている。The above-described stepping motor 12 is driven by an output signal from the control device 17 as shown in FIG. 1. In this device, the fully opened state of the inlet side passage 4 is set as the initial state of the flow control valve 5. For example, when the ignition is turned on, the stepping motor 12 is rotated so as to move the valve body 11 in a direction to fully open the inlet side passage 4. At the rear end of the stepping motor 12, for example, a limit switch type position sensor 18 is provided. When the rear end of the drive shaft 16 hits the position sensor 18, a signal from the position sensor 18 is sent to the control device.
17 to be the initial position of the valve body 11.
また、ウォータジャケット７の出口側通路４に臨む出
口部には、冷却水温度を検出するための水温センサ19が
設けられ、外気温度として例えば吸気温度を検出するた
めの吸気温センサ20、及びエンジン１の運転状態を検出
するべく吸気負圧を検出する負圧センサ21が図示されな
い吸気管にそれぞれ設けられていると共に、同様に運転
状態を検出するべくエンジン回転数を検出する公知形式
の回転センサ22がエンジン１に設けられており、それぞ
れ制御装置17に検出信号を送るようにされている。ま
た、制御装置17には、図示されないヒータまたはエアコ
ンディションナをオンすることによりヒータコア９に冷
却水が流れたことを検出する信号が入力されるようにな
っている。Further, a water temperature sensor 19 for detecting a cooling water temperature is provided at an outlet portion facing the outlet side passage 4 of the water jacket 7, and an intake air temperature sensor 20 for detecting, for example, an intake air temperature as an outside air temperature, and an engine. A negative pressure sensor 21 for detecting an intake negative pressure for detecting an operation state is provided in each of intake pipes (not shown), and a rotation sensor of a known type for detecting an engine speed for similarly detecting an operation state. 22 is provided in the engine 1 and sends a detection signal to the control device 17. Further, a signal for detecting that cooling water has flowed into the heater core 9 by turning on a heater or an air conditioner (not shown) is input to the control device 17.
第３図は、制御装置17に於て行なわれる処理のプログ
ラムの流れを示すもので、先ずST1に於て、弁体11の初
期位置からの移動量に応じたステッピングモータ12の現
在のステップ数Ｓを読み込んだ後、ST2に於て、回転セ
ンサ22によるエンジン回転数Ne及び負圧センサ21による
吸気負圧Pbを読み込み、更にST3に於て、吸気温センサ2
0による外気温度Ta及び水温センサ19による冷却水温度T
wを読み込む。次にST4に於て、ST2で読み込んだエンジ
ン回転数Ne及び吸気負圧Pbに基づいて、第４図に示され
るパターンにて記憶されたデータから目標水温Toのルッ
クアップを行なう。そしてST5に於て関数選択手段によ
る判別を行う。ST3で読み込んだ冷却水温度TwとST4で呼
び出した目標水温Toとを比較し、Tw＜Toである暖機中な
らばST6に進み、ST6に於て温度の偏差t1を、 t1＝To−Tw により算出する。次のST7に於て、その偏差t1に応じた
補正放熱量Ｑを、第５図に示される第１の関数曲線に基
づいて求めるルックアップを行なう。FIG. 3 shows a program flow of a process performed by the control device 17. First, in ST1, the current number of steps of the stepping motor 12 according to the moving amount of the valve body 11 from the initial position is shown. After reading S, the engine speed Ne by the rotation sensor 22 and the intake negative pressure Pb by the negative pressure sensor 21 are read in ST2, and the intake temperature sensor 2 is read in ST3.
Outside air temperature Ta by 0 and cooling water temperature T by water temperature sensor 19
Read w. Next, in ST4, based on the engine speed Ne and the intake negative pressure Pb read in ST2, the target water temperature To is looked up from the data stored in the pattern shown in FIG. Then, in ST5, the determination by the function selecting means is performed. The cooling water temperature Tw read in ST3 is compared with the target water temperature To called in ST4. If the temperature is warming up where Tw <To, the process proceeds to ST6, in which the temperature deviation t1 in ST6, t1 = To−Tw It is calculated by: In the next ST7, a lookup is performed to find a corrected heat release amount Q according to the deviation t1 based on the first function curve shown in FIG.
更にST8に於て、ヒータまたはエアコンディショナが
オンされてヒータコア９に冷却水が流れていると判断し
た場合には、ST9に進み、ヒータコア９による必要放熱
量に応じて予め記憶されている補正放熱量Qhを呼び出し
て、ST11に進む。なおST8に於て、ヒータまたはエアコ
ンディショナがオフであると判断した場合には、ST10に
進み、補正放熱量Qhを０にして、ST11に進む。ST11に於
て、ST7で呼び出した補正放熱量Ｑと、ST9またはST10で
呼び出した補正放熱量Qhとに基づいて制御補正放熱量を
設定し、弁体11の閉方向への移動量に応じた補正ステッ
プ数ΔＳを次式により算出する。Further, in ST8, when it is determined that the heater or the air conditioner is turned on and the cooling water is flowing through the heater core 9, the process proceeds to ST9, and the correction stored in advance according to the required heat release amount by the heater core 9 is performed. Call the heat release amount Qh, and proceed to ST11. If it is determined in ST8 that the heater or the air conditioner is off, the process proceeds to ST10, the corrected heat release amount Qh is set to 0, and the process proceeds to ST11. In ST11, the control correction heat release amount is set based on the correction heat release amount Q called in ST7 and the correction heat release amount Qh called in ST9 or ST10, and according to the amount of movement of the valve body 11 in the closing direction. The number of correction steps ΔS is calculated by the following equation.
ΔＳ＝Ｋ（Qh−Ｑ）/Ne（Tw−Ta） なお上記式は、エンジン１の冷却水への放熱量が冷却
水の循環水量に比例することに基づくと共に、循環水量
がエンジン回転数に比例するとして導き出したものであ
り、式中のＫは、補正放熱量に応じた冷却水の循環水量
を確保するために、流量制御弁５の開度に応じた弁体11
の移動量をステップ数に換算するための係数である。ΔS = K (Qh−Q) / Ne (Tw−Ta) The above expression is based on the fact that the amount of heat released to the cooling water of the engine 1 is proportional to the amount of circulating water of the cooling water, and the amount of circulating water is It is derived as proportional, and K in the equation is a valve element 11 corresponding to the opening degree of the flow control valve 5 in order to secure the circulating water amount of the cooling water according to the corrected heat release amount.
Is a coefficient for converting the movement amount of the step into the number of steps.
そして、ST12に於て補正後のステップ数Ｓを算出し、
ST13に於て補正ステップ数ΔＳ分だけステッピングモー
タ12を回転させる。Then, the number of steps S after the correction is calculated in ST12,
In step ST13, the stepping motor 12 is rotated by the number of correction steps ΔS.
ところで、ST5に於て、目標水温Toよりも冷却水温度T
wが高い場合には、ST14に進み、ST14に於て、冷却水の
上限水温T1に対する高低を比較し、低い場合にはST15に
進む。このST15に於て、温度の偏差t2を、 t2＝Tw−To により算出し、次のST16に於て、その偏差t2に応じた補
正放熱量Ｑを、第６図に示される第２の関数曲線に基づ
いて求めるルックアップを行なう。そしてST8に進み、
以後前記と同様の処理を行なう。By the way, in ST5, the cooling water temperature T is higher than the target water temperature To.
If w is high, the process proceeds to ST14, and in ST14, the level of the cooling water with respect to the upper limit water temperature T1 is compared, and if it is low, the process proceeds to ST15. In this ST15, the temperature deviation t2 is calculated by t2 = Tw-To, and in the next ST16, the corrected heat release amount Q corresponding to the deviation t2 is calculated by the second function shown in FIG. Perform a lookup based on the curve. Then proceed to ST8,
Thereafter, the same processing as described above is performed.
またST14に於て、上限水温T1よりも冷却水温度Twが高
い場合にはST17に進み、ST17に於てステップ数Ｓを０と
してからST13に進み、入口側通路４を全開にするべく弁
体11を初期位置に向けて移動させるようにステッピング
モータ12を回転する。In ST14, when the cooling water temperature Tw is higher than the upper limit water temperature T1, the process proceeds to ST17, in which the number of steps S is set to 0 in ST17, and then proceeds to ST13. The stepping motor 12 is rotated so as to move the 11 toward the initial position.
なお、本実施例に於ては、ST4に於て呼び出す目標水
温Toを、第４図に示されるように高温域、中温域及び低
温域の３領域に区分けしており、エンジン回転数Ne及び
吸気負圧Pbの両者の相対関係に応じた目標水温Toを定め
ている。即ち、エンジン回転数Neが高いほど目標水温To
を低くし、かつ高負荷になるほど目標水温Toが低くなる
ようにしており、高回転または高負荷状態の運転時には
ST5からST14に進み易くして、冷却能力を高めるように
している。In the present embodiment, the target water temperature To called in ST4 is divided into three regions of a high temperature region, a medium temperature region and a low temperature region as shown in FIG. The target water temperature To is determined according to the relative relationship between the intake negative pressure Pb and the intake water negative pressure Pb. That is, the higher the engine speed Ne, the higher the target water temperature To
And the higher the load, the lower the target water temperature To is.
It is easy to proceed from ST5 to ST14, and the cooling capacity is increased.
また、ST7に於て呼び出す補正放熱量Ｑを、第５図に
示されるように偏差t1が大きくなるにつれて減少させ、
所定値以上になると負の補正量となる第１の関数曲線に
より導き出すようにしている。これにより、例えば冷間
時に始動する場合には、冷却水をラジエータ３に流さな
いようにして素早く暖めることが望ましいため、入口側
通路４を閉じる向きに弁体11を移動させる必要がある。
即ち、冷間時には冷却水温度Twが低いため温度偏差t1が
大きくなって、上記補正放熱量Ｑが負の値になり、ΔＳ
が正の値となるため、ステップ数Ｓを増やして弁体11を
閉じる向きに駆動する。これに対して暖間時に始動する
場合には、冷却水がある程度暖まっているため水温の上
昇曲線がオーバシュートしないようにするべく、冷却水
をラジエータ３に流すようにすると良い。従って、暖間
時には冷却水温度Twが高いため温度偏差t1が小さくなっ
て、上記補正放熱量Ｑが正の値になり、ΔＳが負の値と
なるため、ステップ数Ｓを減らして、弁体11を開く向き
に駆動する。Further, as shown in FIG. 5, the corrected heat radiation amount Q called in ST7 is reduced as the deviation t1 increases,
The value is derived from a first function curve that becomes a negative correction amount when the value exceeds a predetermined value. Thus, for example, when the engine is started in a cold state, it is desirable to quickly warm the cooling water without flowing the cooling water to the radiator 3. Therefore, it is necessary to move the valve body 11 in a direction to close the inlet side passage 4.
That is, in the cold state, the cooling water temperature Tw is low, so the temperature deviation t1 becomes large, and the corrected heat release amount Q becomes a negative value, ΔS
Is a positive value, the number of steps S is increased, and the valve element 11 is driven in the closing direction. On the other hand, when the engine is started during a warm period, the cooling water is preferably caused to flow to the radiator 3 so that the rising curve of the water temperature does not overshoot because the cooling water has warmed to some extent. Therefore, when the temperature is warm, the cooling water temperature Tw is high, so that the temperature deviation t1 becomes small, and the corrected heat release amount Q becomes a positive value, and ΔS becomes a negative value. Drive 11 to open.
また、ST16に於て呼び出す補正放熱量Ｑを、第６図に
示されるように、温度偏差t2が大きくなるつれて増加す
る第２の関数曲線により求めるようにしている。この場
合にはエンジン１が暖機後の状態にあり、冷却水をラジ
エータ３に大量に流して冷却する必要がある。従って、
冷却水温度Twが高くなるにつれて温度偏差t2が大きくな
るため、補正放熱量Ｑが大きくなり、全開位置に向けて
弁体11を駆動することとなる。Further, as shown in FIG. 6, the corrected heat radiation amount Q called in ST16 is obtained from a second function curve which increases as the temperature deviation t2 increases. In this case, the engine 1 is in a state after warming up, and it is necessary to cool the cooling water by flowing a large amount of cooling water through the radiator 3. Therefore,
Since the temperature deviation t2 increases as the cooling water temperature Tw increases, the corrected heat release amount Q increases, and the valve body 11 is driven toward the fully open position.
このように、冷却水温度の高低に応じて、冷却水温よ
りも目標水温が高い暖機中の場合（ST5からST6に進む場
合）には暖機を促進する制御を行い、暖機後でありかつ
冷却水温が上限水温よりも高い場合（ST14からST17に進
む場合）にはラジエータに流す冷却水が最大となるよう
に制御している。また、暖機後であって冷却水温が上限
水温よりも低い通常の暖機後温度範囲である場合（ST14
からST15に進む場合）には、負荷の大きさに応じた適切
な放熱を行うように制御するため、熱損失の軽減及び排
気の浄化を向上し得ると共に、エンジンの運転状態に応
じた必要放熱量を基準として所謂フィードフォワード制
御を行うため、フィードバック制御による制御遅れがな
い。また、サーモスタットを用いるものに対して制御弁
の取付け自由度が大きく、その設計が容易であるばかり
でなく、ステッピングモータ12を用いることにより弁体
11を高精度に位置制御できるため、半開状態に於ける流
量の制御を極めて精度良くかつ容易に行うことができ
る。In this way, according to the level of the cooling water temperature, if the target water temperature is higher than the cooling water temperature during warm-up (when proceeding from ST5 to ST6), control is performed to promote warm-up. When the cooling water temperature is higher than the upper limit water temperature (when proceeding from ST14 to ST17), the cooling water flowing to the radiator is controlled to be maximum. Also, after the warm-up, when the cooling water temperature is in the normal post-warm-up temperature range lower than the upper limit water temperature (ST14).
When the process proceeds from step ST15 to step ST15), control is performed so as to perform appropriate heat radiation in accordance with the magnitude of the load, so that heat loss can be reduced and exhaust gas purification can be improved. Since so-called feedforward control is performed on the basis of the amount of heat, there is no control delay due to feedback control. In addition, the degree of freedom in mounting the control valve is larger than that using a thermostat, so that the design is easy.
Since the position of 11 can be controlled with high accuracy, the flow rate control in the half-open state can be performed extremely accurately and easily.
また、系全体の応答性がそれはど早くないと共にハン
チングを防止するためにも、比較的長いサイクルタイム
をもって制御を行なえば充分であり、例えば他の制御装
置のCPUを用いることも可能である。なお、エンジンコ
ントロール装置に冷却水温度、吸気温度、及び吸気負圧
用の各センサを設けているエンジンについては、新に各
センサを設ける必要がないため、部品コストの高騰を抑
制できるなどの効果もある。In addition, in order to prevent the responsiveness of the entire system from being very fast and to prevent hunting, it is sufficient to perform the control with a relatively long cycle time. For example, it is possible to use a CPU of another control device. In the case of an engine in which the engine control device is equipped with sensors for cooling water temperature, intake air temperature, and intake negative pressure, there is no need to provide additional sensors. is there.
［発明の効果］ このように本発明によれば、冷却水温に対する目標水
温の高低の違いを考慮して補正放熱量を求めることによ
り、機関の運転状態の変化による補正放熱量を精度良く
算出でき、その補正放熱量を達成するべく流量制御弁の
開度を制御するため、常に最適な冷却効果が得られると
共に、燃費及び排気の浄化を向上することができる。ま
た、流量制御弁によりラジエータ通路とバイパス通路と
の開閉を互いに相反する状態にすることにより、いずれ
か一方の通路にのみ冷却水を流すことができ、各状態に
おける冷却水の温度変化を早めて制御速度を高めること
ができる等、その効果は極めて大である。[Effect of the Invention] As described above, according to the present invention, the corrected heat radiation amount due to a change in the operating state of the engine can be accurately calculated by determining the corrected heat radiation amount in consideration of the difference between the target water temperature and the cooling water temperature. Since the opening degree of the flow control valve is controlled to achieve the corrected heat release amount, an optimal cooling effect can be always obtained, and the fuel consumption and the purification of exhaust gas can be improved. Further, by setting the opening and closing of the radiator passage and the bypass passage to be opposite to each other by the flow control valve, the cooling water can flow only in one of the passages, and the temperature change of the cooling water in each state is accelerated. The effect is extremely large, for example, the control speed can be increased.
第１図は、本発明が適用された冷却水流量制御装置の全
体を模式的に示す図である。 第２図は、本発明に基づく流量制御弁を示す要部拡大図
である。 第３図は、本発明に基づく流量制御装置のプログラムの
流れを示すフロー図である。 第４図は、第３図に示すST4に於ける制御パターンの一
例を示す図である。 第５図は、第３図に示すST7に於ける制御関数曲線の一
例を示す図である。 第６図は、第３図に示すST16に於ける制御関数曲線の一
例を示す図である。 １……エンジン、２……ウォータポンプ ３……ラジエータ、４……入口側通路 ５……流量制御弁、６……出口側通路 ７……ウォータジャケット ８……バイパス通路、９……ヒータコア 10……吸込通路、11……弁体 12……ステッピングモータ 13……ロータ、14……弁室 15……副弁体、16……駆動シャフト 17……制御装置、18……位置センサ 19……水温センサ、20……吸気温センサ 21……負圧センサ、22……回転センサFIG. 1 is a diagram schematically showing an entire cooling water flow control device to which the present invention is applied. FIG. 2 is an enlarged view of a main part showing a flow control valve according to the present invention. FIG. 3 is a flowchart showing a program flow of the flow rate control device according to the present invention. FIG. 4 is a diagram showing an example of a control pattern in ST4 shown in FIG. FIG. 5 is a diagram showing an example of a control function curve in ST7 shown in FIG. FIG. 6 is a diagram showing an example of a control function curve in ST16 shown in FIG. DESCRIPTION OF SYMBOLS 1 ... Engine, 2 ... Water pump 3 ... Radiator, 4 ... Inlet side passage 5 ... Flow control valve, 6 ... Outlet side passage 7 ... Water jacket 8 ... Bypass passage, 9 ... Heater core 10 …… Suction passage, 11… Valve body 12 …… Stepping motor 13 …… Rotor, 14 …… Valve room 15 …… Sub valve body, 16 …… Drive shaft 17 …… Control device, 18 …… Position sensor 19… … Water temperature sensor, 20 …… intake air temperature sensor 21 …… negative pressure sensor, 22 …… rotation sensor
Claims (2)
中に介装された流量制御弁と、冷却水の前記機関の出口
部の温度を検出する手段と、前記機関の運転状態を検出
する手段と、外気温度を検出する手段と、前記運転状態
の検出結果に基づいて目標水温を設定する手段と、前記
冷却水温よりも前記目標水温の方が高い暖機中の場合に
は両者間の温度偏差が大きくなるに連れて補正放熱量の
正の値から負の値に至るように漸減させる第１の関数曲
線を選択し、前記冷却水温が前記目標水温よりも高くか
つ所定の上限水温よりも低い暖機後の場合には両者間の
温度偏差が大きくなるに連れて補正放熱量を漸増させる
第２の関数曲線を選択する関数選択手段と、前記冷却水
温度と前記目標水温との偏差に基づいて前記第１または
第２の関数曲線により求めた補正放熱量を制御補正放熱
量として設定する手段と、前記制御補正放熱量を達成す
るべく前記各検出手段による検出結果に基づいて前記流
量制御弁を制御する手段とを有することを特徴とする内
燃機関の冷却水流量制御装置。A flow control valve interposed in a cooling water passage communicating the engine with a radiator; a means for detecting a temperature of cooling water at an outlet of the engine; and detecting an operating state of the engine. Means, means for detecting an outside air temperature, means for setting a target water temperature based on the detection result of the operating state, and between the two when the target water temperature is higher than the cooling water temperature during warm-up. A first function curve that gradually decreases from a positive value to a negative value of the corrected heat release as the temperature deviation increases is selected, and the cooling water temperature is higher than the target water temperature and higher than a predetermined upper limit water temperature. Also after a low warm-up, a function selecting means for selecting a second function curve for gradually increasing the corrected heat radiation as the temperature deviation between the two increases, and a deviation between the cooling water temperature and the target water temperature. To the first or second function curve based on Means for setting the corrected heat radiation amount obtained as a control corrected heat radiation amount, and means for controlling the flow rate control valve based on a detection result by each of the detecting means to achieve the control corrected heat radiation amount. A cooling water flow control device for an internal combustion engine.
パス通路との開閉状態を互いに相反する状態にし得るよ
うに設けられていることを特徴とする請求項１に記載の
内燃機関の冷却水流量制御装置。2. The cooling water flow rate of an internal combustion engine according to claim 1, wherein the flow control valve is provided so that the open / close state of the radiator passage and the bypass passage can be set to be opposite to each other. Control device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63278049A JP2573870B2 (en) | 1988-11-02 | 1988-11-02 | Cooling water flow control device for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63278049A JP2573870B2 (en) | 1988-11-02 | 1988-11-02 | Cooling water flow control device for internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02125910A JPH02125910A (en) | 1990-05-14 |
| JP2573870B2 true JP2573870B2 (en) | 1997-01-22 |
Family
ID=17591942
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63278049A Expired - Fee Related JP2573870B2 (en) | 1988-11-02 | 1988-11-02 | Cooling water flow control device for internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2573870B2 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10048792B4 (en) * | 2000-10-02 | 2016-02-18 | Mahle International Gmbh | thermostatic valve |
| KR100361305B1 (en) * | 2000-11-30 | 2002-11-21 | 현대자동차주식회사 | Cooling water temperature control system of a car and Method thereof |
| US6684826B2 (en) | 2001-07-25 | 2004-02-03 | Toyota Jidosha Kabushiki Kaisha | Engine cooling apparatus |
| JP4146372B2 (en) * | 2004-03-05 | 2008-09-10 | 三菱電機株式会社 | Cooling system control method for vehicle power source |
| FR2882397B1 (en) * | 2005-02-21 | 2007-05-18 | Peugeot Citroen Automobiles Sa | SYSTEM FOR REDUCING THE AMOUNT OF GASOLINE IN THE LUBRICATING OIL OF A DIESEL ENGINE OF A MOTOR VEHICLE |
| JP5168379B2 (en) * | 2011-03-28 | 2013-03-21 | トヨタ自動車株式会社 | Cooling water control device for internal combustion engine |
| DE102013211333A1 (en) * | 2013-06-18 | 2014-12-18 | Bayerische Motoren Werke Aktiengesellschaft | Thermostatic rotary valve and cooling system |
| JP6604349B2 (en) * | 2017-03-16 | 2019-11-13 | トヨタ自動車株式会社 | Engine cooling system |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59226225A (en) * | 1983-06-08 | 1984-12-19 | Nissan Motor Co Ltd | Apparatus for controlling temperature of cooling water in internal-combustion engine for automobile |
| JPS60166712A (en) * | 1984-02-09 | 1985-08-30 | Mazda Motor Corp | Cooling device of water-cooled engine |
| JPS62237024A (en) * | 1986-04-07 | 1987-10-17 | Mazda Motor Corp | Cooling water controller for engine |
| JPH0726534B2 (en) * | 1986-04-07 | 1995-03-29 | マツダ株式会社 | Engine cooling water controller |
| JPS62237023A (en) * | 1986-04-07 | 1987-10-17 | Mazda Motor Corp | Cooling water controller for engine |
| JPS62247114A (en) * | 1986-04-18 | 1987-10-28 | Toyota Motor Corp | Cooling water temperature control device for internal combustion engine |
| JPS6387223U (en) * | 1986-11-28 | 1988-06-07 |
-
1988
- 1988-11-02 JP JP63278049A patent/JP2573870B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH02125910A (en) | 1990-05-14 |
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