JP2009264353A - Waste heat using device of internal combustion engine - Google Patents

Waste heat using device of internal combustion engine Download PDF

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JP2009264353A
JP2009264353A JP2008118431A JP2008118431A JP2009264353A JP 2009264353 A JP2009264353 A JP 2009264353A JP 2008118431 A JP2008118431 A JP 2008118431A JP 2008118431 A JP2008118431 A JP 2008118431A JP 2009264353 A JP2009264353 A JP 2009264353A
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pump
fan
internal combustion
combustion engine
waste heat
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JP5053922B2 (en
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Junichiro Kasuya
潤一郎 粕谷
Yasuaki Kano
靖明 狩野
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Sanden Corp
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a waste heat using device of an internal combustion engine capable of increasing a net power generation quantity, in its turn, capable of effectively increasing an effective energy collection quantity of a waste heat using device. <P>SOLUTION: This waste heat using device of the internal combustion engine 2 has a control means for controlling a rotating speed of a fan 25 and a pump 28 in response to a disturbance element value of a Rankine cycle 6 including an operation state of the internal combustion engine. The control means controls the rotating speed of the fan and the pump so as to increase the net power generation quantity of subtracting electric power consumption of the fan and the pump from a power generation quantity generated by a generator 30. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、車両に組み込まれて好適な内燃機関の廃熱利用装置に関する。   The present invention relates to a waste heat utilization apparatus for an internal combustion engine that is preferably incorporated in a vehicle.

この種の内燃機関の廃熱利用装置は、例えば車両に搭載され、作動流体としての冷媒の循環路に、車両のエンジンを冷却する冷却水を介してエンジンの廃熱により冷媒を加熱する蒸発器、この蒸発器から流出された冷媒を膨張させて駆動力を発生する膨張機、この膨張機から流出された冷媒をファンによる外気送風により凝縮させるコンデンサ、このコンデンサから流出された冷媒を蒸発器に送出して循環路に冷媒を循環させるポンプが介挿されたランキンサイクルを備える。   This type of waste heat utilization device for an internal combustion engine is mounted on a vehicle, for example, and is an evaporator that heats the refrigerant by the waste heat of the engine via a cooling water that cools the engine of the vehicle in a refrigerant circulation path as a working fluid. An expander that expands the refrigerant that has flowed out of the evaporator to generate a driving force, a condenser that condenses the refrigerant that has flowed out of the expander by blowing outside air using a fan, and the refrigerant that has flowed out of the condenser into the evaporator A Rankine cycle in which a pump for sending and circulating the refrigerant in the circulation path is inserted is provided.

そして、熱機関の廃熱量とコンデンサにおける冷媒の放熱量とによって定まる膨張機の駆動力が増大するように冷媒の流量を制御したり（特許文献１）、或いは、蒸発器での冷媒の吸熱量に応じて蒸発器への冷媒の流入量や膨張機の回転数を制御するものや（特許文献２，３）、或いは、エンジンのスロットル開度を制御して膨張機に流入される冷媒の性状を制御する（特許文献４）ことにより、膨張機、発電機を介して回収されるエネルギーの回収効率を高める技術が開示されている。
特開２００６−１７７２６６号公報 特開２００６−２５００７３号公報 特開２００６−２５００７５号公報 特開２００６−２００４９２号公報 Then, the flow rate of the refrigerant is controlled so as to increase the driving force of the expander determined by the waste heat amount of the heat engine and the heat radiation amount of the refrigerant in the condenser (Patent Document 1), or the heat absorption amount of the refrigerant in the evaporator Depending on the amount of refrigerant flowing into the evaporator and the rotation speed of the expander (Patent Documents 2 and 3), or the characteristics of the refrigerant flowing into the expander by controlling the throttle opening of the engine (Patent Document 4) has been disclosed to improve the recovery efficiency of energy recovered through an expander and a generator.
JP 2006-177266 A JP 2006-250073 A JP 2006-250075 A JP 2006-200492 A

ところで、コンデンサにおける冷媒の放熱量、即ちランキンサイクルの放熱量はコンデンサのファンの回転数に依存し、ランキンサイクルにおける冷媒の循環流量はポンプの回転数に依存している。
しかしながら、上記各従来技術は、膨張機を効率良く回転させて発電機にて発電された発電量を増大させることのみに拘泥しており、正味発電量が発電機にて発電された発電量からファン及びポンプの消費電力量を減じたものであって、この正味発電量を増大させる点については格別な配慮がなされておらず、廃熱利用装置の有効エネルギー回収量の増大には依然として課題が残されている。 By the way, the heat release amount of the refrigerant in the condenser, that is, the heat release amount of the Rankine cycle depends on the rotation speed of the condenser fan, and the circulation flow rate of the refrigerant in the Rankine cycle depends on the rotation speed of the pump.
However, each of the above prior arts is only concerned with increasing the power generation amount generated by the generator by efficiently rotating the expander, and the net power generation amount is calculated from the power generation amount generated by the generator. The power consumption of fans and pumps has been reduced, and no special consideration has been given to increasing this net power generation, and there is still a problem in increasing the effective energy recovery amount of waste heat utilization equipment. It is left.

本発明は、このような課題に鑑みてなされたもので、正味発電量を増大し、ひいては廃熱利用装置の有効エネルギー回収量を効果的に増大することができる内燃機関の廃熱利用装置を提供することを目的とする。   The present invention has been made in view of such a problem, and provides a waste heat utilization device for an internal combustion engine that can increase the net power generation amount, and thus effectively increase the effective energy recovery amount of the waste heat utilization device. The purpose is to provide.

上記の目的を達成するべく、請求項１記載の内燃機関の廃熱利用装置は、作動流体の循環路に、内燃機関の廃熱により作動流体を加熱する蒸発器、該蒸発器から流出された作動流体を膨張させて駆動力を発生する膨張機、該膨張機から流出された作動流体をファンによる外気送風により凝縮させるコンデンサ、該コンデンサから流出された作動流体を蒸発器に送出して循環路に作動流体を循環させるポンプが介挿されたランキンサイクルと、膨張機に連結され、該膨張機にて発生した駆動力を電力に変換して発電する発電機と、内燃機関の作動状態を含むランキンサイクルの外乱要素値に応じてファン及びポンプの回転数を制御する制御手段とを備え、制御手段は、発電機にて発電された発電量からファン及びポンプの消費電力を減じた正味発電量を増大させるようにファン及びポンプの回転数を制御することを特徴としている。   In order to achieve the above object, an internal combustion engine waste heat utilization device according to claim 1 is discharged from the evaporator for heating the working fluid by the waste heat of the internal combustion engine in the working fluid circulation path. An expander that expands the working fluid to generate a driving force, a condenser that condenses the working fluid that has flowed out of the expander by outside air blowing by a fan, and a circulation path that sends the working fluid that has flowed out of the condenser to the evaporator Including a Rankine cycle in which a pump for circulating a working fluid is inserted, a generator connected to the expander and converting the driving force generated in the expander into electric power to generate electric power, and an operating state of the internal combustion engine Control means for controlling the rotation speed of the fan and the pump according to the disturbance element value of the Rankine cycle, and the control means is a net value obtained by subtracting the power consumption of the fan and the pump from the amount of power generated by the generator. It is characterized by controlling the rotation speed of the fan and the pump so as to increase the coulometric.

また、請求項２記載の発明では、請求項１において、制御手段は、外乱要素値の変化に対してポンプ回転数を遅れて制御する遅延制御を行うことを特徴としている。
更に、請求項３記載の発明では、請求項２において、制御手段は、ポンプ回転数の加減速度を所定の加減速度制限値に制限することにより遅延制御を行うことを特徴としている。 Further, the invention according to claim 2 is characterized in that, in claim 1, the control means performs delay control for delaying and controlling the pump rotational speed with respect to a change in the disturbance element value.
Further, the invention according to claim 3 is characterized in that, in claim 2, the control means performs the delay control by limiting the acceleration / deceleration of the pump rotational speed to a predetermined acceleration / deceleration limit value.

更にまた、請求項４記載の発明では、請求項２において、制御手段は、時系列的に検出される所定数の外乱要素値から算出される外乱要素値の移動平均値に基づいてポンプの回転数を制御することにより遅延制御を行うことを特徴としている。
また、請求項５記載の発明では、請求項３または４において、制御手段は、外乱要素値やその変化量に応じて、所定の加減速度制限値、または、移動平均値を算出するための外乱要素値の所定数を決定することを特徴としている。 Furthermore, in the invention described in claim 4, in claim 2, the control means rotates the pump based on a moving average value of disturbance element values calculated from a predetermined number of disturbance element values detected in time series. It is characterized by performing delay control by controlling the number.
According to a fifth aspect of the present invention, in the third or fourth aspect, the control means is a disturbance for calculating a predetermined acceleration / deceleration limit value or a moving average value in accordance with the disturbance element value and its change amount. It is characterized in that a predetermined number of element values is determined.

更に、請求項６記載の発明では、請求項１乃至５の何れかにおいて、制御手段は、正味発電量が所定時間に亘って所定値以下となるとき、ファン及びポンプの駆動を停止することを特徴としている。
更にまた、請求項７記載の発明では、請求項６において、内燃機関の廃熱によって加熱された冷却水を蒸発器に流入させるとともに、該蒸発器から流出された冷却水をファンによる外気送風により冷却させるラジエータを有する冷却水回路と、内燃機関を経由した冷却水の温度を検出する冷却水温度検出手段とを備え、制御手段は、冷却水温度検出手段にて検出された冷却水温度が所定温度以上となるとき、駆動を停止されたファンを再駆動し、冷却水温度を所定温度未満に保持するべくファンの回転数を制御することを特徴としている。 Further, in the invention described in claim 6, in any one of claims 1 to 5, the control means stops the driving of the fan and the pump when the net power generation amount becomes a predetermined value or less over a predetermined time. It is a feature.
Furthermore, in the invention of claim 7, in claim 6, the cooling water heated by the waste heat of the internal combustion engine is caused to flow into the evaporator, and the cooling water that has flowed out of the evaporator is blown to the outside air by a fan. A cooling water circuit having a radiator for cooling; and a cooling water temperature detecting means for detecting a temperature of the cooling water passing through the internal combustion engine, wherein the control means has a predetermined cooling water temperature detected by the cooling water temperature detecting means. When the temperature exceeds the temperature, the fan that has been stopped is re-driven, and the number of rotations of the fan is controlled so as to keep the cooling water temperature below a predetermined temperature.

また、請求項８記載の発明では、請求項７において、制御手段は、ファンが再駆動された後には、駆動を停止されたポンプを再駆動し、発電量からポンプ消費電力を減じた第２正味発電量を増大させるようにポンプの回転数を制御することを特徴としている。
更に、請求項９記載の発明では、請求項８において、制御手段は、第２正味発電量が第２所定時間に亘って所定値以下となるとき、ポンプの駆動を停止することを特徴としている。 According to an eighth aspect of the present invention, in the seventh aspect, after the fan is re-driven, the control unit re-drives the pump that has been stopped to reduce the pump power consumption from the power generation amount. It is characterized by controlling the rotational speed of the pump so as to increase the net power generation amount.
Further, the invention according to claim 9 is characterized in that, in claim 8, the control means stops the driving of the pump when the second net power generation amount becomes a predetermined value or less over the second predetermined time. .

更にまた、請求項１０記載の発明では、請求項９において、制御手段は、正味発電量が第３所定時間に亘って所定値より大となるとき、正味発電量を増大させるようにファン及びポンプの回転数を制御することを特徴としている。   Furthermore, in the invention described in claim 10, in claim 9, the control means includes a fan and a pump so as to increase the net power generation amount when the net power generation amount becomes larger than a predetermined value over a third predetermined time. The number of rotations is controlled.

従って、請求項１記載の本発明の内燃機関の廃熱利用装置によれば、内燃機関の作動状態を含むランキンサイクルの外乱要素値に応じてコンデンサのファン、及び循環路に作動流体を循環させるポンプの回転数を制御する制御手段を備え、制御手段は、発電機にて発電された発電量からファン及びポンプの消費電力量を減じた正味発電量を増大させるようにファン及びポンプの回転数を制御する。これにより、単に発電機の発電量を増大させるのではなく正味発電量を極力増大することができ、廃熱利用装置の有効エネルギー回収量を増大することができ、ひいては、廃熱利用装置外で有効利用できるエネルギー量を増大することができる。   Therefore, according to the waste heat utilization apparatus for an internal combustion engine of the first aspect of the present invention, the working fluid is circulated in the condenser fan and the circulation path in accordance with the disturbance element value of the Rankine cycle including the operation state of the internal combustion engine. Control means for controlling the number of revolutions of the pump is provided, and the means for controlling the number of revolutions of the fan and the pump so as to increase the net amount of power generated by subtracting the power consumption of the fan and the pump from the amount of power generated by the generator. To control. As a result, instead of simply increasing the power generation amount of the generator, the net power generation amount can be increased as much as possible, the effective energy recovery amount of the waste heat utilization device can be increased, and as a result, outside the waste heat utilization device. The amount of energy that can be used effectively can be increased.

また、請求項２記載の発明によれば、制御手段は、外乱要素値の変化に対してポンプ回転数を遅れて制御する遅延制御を行う。
ここで、制御手段は、内燃機関の廃熱量に合わせて蒸発器の吸熱量を増減させるためにポンプ回転数を増減して循環路における作動流体の循環量を増減させるが、内燃機関の廃熱量の増減にポンプ回転数を同期させるべくポンプ回転を増大させても、ランキンサイクルは冷媒を急激に蒸発させることはできないため、その分のポンプの駆動に要したポンプ消費電力が無駄になる。 According to the second aspect of the present invention, the control means performs the delay control for controlling the pump rotational speed with a delay with respect to the change in the disturbance element value.
Here, the control means increases or decreases the pump rotation speed to increase or decrease the heat absorption amount of the evaporator according to the waste heat amount of the internal combustion engine, and increases or decreases the circulation amount of the working fluid in the circulation path. Even if the pump rotation is increased in order to synchronize the pump rotation speed with the increase / decrease, the Rankine cycle cannot evaporate the refrigerant abruptly, so that the pump power consumption required for driving the pump is wasted.

一方、内燃機関の廃熱量の増減にポンプ回転数を完全に同期させるべくポンプ回転を減少させると、作動流体の余熱で作動流体の蒸発が未だ充分に可能であるにも拘わらず、蒸発器へ流入する作動流体が不足し、本来得られたはずの発電量を得ることができない。
かかる場合において、上記遅延制御を行うことにより、正味発電量を効果的に増大することができ、廃熱利用装置の有効エネルギー回収量をより一層増大することができる。 On the other hand, if the pump rotation is decreased to completely synchronize the pump rotation speed with the increase or decrease in the amount of waste heat of the internal combustion engine, the working fluid can still evaporate due to the residual heat of the working fluid, but the The working fluid that flows in is insufficient, and the power generation amount that should have been obtained cannot be obtained.
In such a case, by performing the delay control, the net power generation amount can be effectively increased, and the effective energy recovery amount of the waste heat utilization apparatus can be further increased.

具体的には、請求項３，４記載の発明によれば、制御手段は、ポンプの回転数の加減速度を所定の加減速度制限値に制限したり（請求項３）、或いは、所定数の外乱要素値から算出される移動平均値に基づいてポンプの回転数を制御する（請求項４）ことにより遅延制御を行う。
更にまた、請求項５記載の発明によれば、制御手段は、外乱要素値やその変化量に応じて、所定の加減速度制限値、または、移動平均値を算出するための外乱要素値の所定数を決定することにより、ランキンサイクルの外乱要素値の大きさ、変動幅、変動方向に応じて精度良く遅延制御を行うことができるため、正味発電量を更に効果的に増大することができる。 Specifically, according to the third and fourth aspects of the invention, the control means limits the acceleration / deceleration of the rotational speed of the pump to a predetermined acceleration / deceleration limit value (invention 3), or a predetermined number of Delay control is performed by controlling the rotational speed of the pump based on the moving average value calculated from the disturbance element value.
Furthermore, according to the fifth aspect of the present invention, the control means determines a predetermined acceleration / deceleration limit value or a predetermined disturbance element value for calculating a moving average value according to the disturbance element value and the amount of change. By determining the number, the delay control can be performed with high accuracy according to the magnitude, fluctuation range, and fluctuation direction of the disturbance element value of the Rankine cycle, so that the net power generation amount can be increased more effectively.

また、請求項６記載の発明によれば、制御手段は、正味発電量が所定時間に亘って所定値以下となるとき、ファン及びポンプの駆動を停止する。これにより、例えば内燃機関のアイドリング時などに内燃機関の廃熱量、即ちランキンサイクルの吸熱量が減少するとき、ファン及びポンプの駆動を停止して正味発電量が継続的に所定値以下になるのを防止することができる。ここで、正味発電量が所定値以下となるのが所定時間に亘ることを条件とすることから、外乱要素値の変動により正味発電量が一時的に所定値以下となる場合を除外することができるため、正味発電量を効果的に増大することができる。   According to the sixth aspect of the present invention, the control means stops the driving of the fan and the pump when the net power generation amount becomes a predetermined value or less over a predetermined time. As a result, when the amount of waste heat of the internal combustion engine, that is, the amount of heat absorbed by the Rankine cycle, decreases, for example, when the internal combustion engine is idling, the fan and the pump are stopped and the net power generation amount continuously falls below a predetermined value. Can be prevented. Here, since it is a condition that the net power generation amount is equal to or less than a predetermined value over a predetermined time, the case where the net power generation amount is temporarily equal to or less than a predetermined value due to fluctuations in disturbance element values may be excluded. Therefore, the net power generation amount can be effectively increased.

更に、請求項７記載の発明によれば、制御手段は、冷却水温度検出手段にて検出された冷却水温度が所定温度以上となるとき、駆動を停止されたファンを再駆動し、冷却水温度を所定温度未満に保持するべくファンの回転数を制御する。これにより、内燃機関の作動中にランキンサイクルの機能を停止しても、ラジエータへの外気送風により冷却水回路の冷却水を冷却することができるため、内燃機関の過熱を防止することができる。   According to the seventh aspect of the present invention, when the cooling water temperature detected by the cooling water temperature detecting means is equal to or higher than the predetermined temperature, the control means re-drives the fan that has been stopped to drive the cooling water. The fan speed is controlled to keep the temperature below a predetermined temperature. Thus, even if the Rankine cycle function is stopped during the operation of the internal combustion engine, the cooling water in the cooling water circuit can be cooled by the outside air blown to the radiator, so that the internal combustion engine can be prevented from being overheated.

更にまた、請求項８記載の発明によれば、制御手段は、ファンが再駆動された後には、駆動を停止されたポンプを再駆動し、発電量からポンプ消費電力を減じた第２正味発電量を増大させるようにポンプの回転数を制御する。これにより、内燃機関の過熱を防止するためにファンを駆動し、ポンプを再駆動してランキンサイクルを再作動した場合であって、単に発電機の発電量を増大させるのではなく、ランキンサイクルの作動に関係ないファン消費電力を除いた第２正味発電量を極力増大することができ、廃熱利用装置の有効エネルギー回収量を増大することができる。   Furthermore, according to the eighth aspect of the present invention, after the fan is re-driven, the control unit re-drives the pump whose driving is stopped, and reduces the pump power consumption from the power generation amount. The number of revolutions of the pump is controlled so as to increase the amount. This is the case where the fan is driven to prevent overheating of the internal combustion engine, the pump is re-driven and the Rankine cycle is restarted, and the power generation amount of the generator is not simply increased. The second net power generation amount excluding fan power consumption not related to the operation can be increased as much as possible, and the effective energy recovery amount of the waste heat utilization device can be increased.

また、請求項９記載の発明によれば、制御手段は、第２正味発電量が第２所定時間に亘って所定値以下となるとき、ポンプの駆動を停止する。これにより、例えば内燃機関のアイドリング時などに内燃機関の廃熱量、即ちランキンサイクルの吸熱量が減少するとき、ポンプの駆動を停止して第２正味発電量が継続的に所定値以下になるのを防止することができる。ここで、第２正味発電量が所定値以下となるのが所定時間に亘ることを条件とすることから、外乱要素値の変動により第２正味発電量が一時的に所定値以下となる場合を除外することができるため、第２正味発電量を効果的に増大することができる。   According to the ninth aspect of the present invention, the control means stops the driving of the pump when the second net power generation amount becomes a predetermined value or less over the second predetermined time. As a result, when the amount of waste heat of the internal combustion engine, that is, the amount of heat absorbed by the Rankine cycle, decreases, for example, when the internal combustion engine is idling, the driving of the pump is stopped and the second net power generation amount continuously falls below a predetermined value. Can be prevented. Here, since it is a condition that the second net power generation amount becomes a predetermined value or less over a predetermined time, the case where the second net power generation amount temporarily becomes a predetermined value or less due to fluctuation of the disturbance element value. Since it can exclude, a 2nd net electric power generation amount can be increased effectively.

更に、請求項１０記載の発明によれば、制御手段は、正味発電量が第３所定時間に亘って所定値より大となるとき、正味発電量を増大させるようにファン及びポンプの回転数を制御する。これにより、ラジエータへの外気送風により内燃機関の過熱を防止しつつ第２正味発電量を増大させるためのポンプ回転数のみの制御から、正味発電量を増大させるためのファン及びポンプの回転数の制御に迅速に復帰させることができるため、正味発電量を効果的に増大することができ、ひいては廃熱利用装置の有効エネルギー回収量を大幅に増大することができる。   Furthermore, according to the invention described in claim 10, when the net power generation amount becomes larger than a predetermined value over a third predetermined time, the control means controls the rotation speeds of the fan and the pump so as to increase the net power generation amount. Control. Thus, from the control of only the pump rotation speed for increasing the second net power generation amount while preventing the internal combustion engine from being overheated by the outside air blown to the radiator, the rotation speed of the fan and the pump for increasing the net power generation amount is increased. Since it is possible to quickly return to the control, it is possible to effectively increase the net power generation amount, and consequently to significantly increase the effective energy recovery amount of the waste heat utilization device.

以下、図面により本発明の一実施形態について説明する
図１は内燃機関の廃熱利用装置の一例を模式的に示しており、この廃熱利用装置は例えば車両に搭載され、車両のエンジン２を冷却する冷却水回路４と、エンジン２の廃熱を回収するランキンサイクル６（以下、ＲＣ回路という）とを備えている。
冷却水回路４は、エンジン２から延設される冷却水の循環路５に、冷却水の流れ方向から順に蒸発器１０、ラジエータ１２、サーモスタット１４、水ポンプ１６が介挿されて閉回路を構成している。 DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 schematically shows an example of a waste heat utilization device for an internal combustion engine. This waste heat utilization device is mounted on a vehicle, for example. A cooling water circuit 4 for cooling and a Rankine cycle 6 (hereinafter referred to as an RC circuit) for recovering waste heat of the engine 2 are provided.
The cooling water circuit 4 forms a closed circuit by inserting an evaporator 10, a radiator 12, a thermostat 14, and a water pump 16 into a cooling water circulation path 5 extending from the engine 2 in order from the flow direction of the cooling water. is doing.

蒸発器１０は、冷却水回路４を循環する冷却水とＲＣ回路６を循環する冷媒とを熱交換させることにより、エンジン２で加熱された冷却水、すなわち温水を熱媒体としてエンジン２の廃熱をＲＣ回路６側に吸熱させて回収している。一方、蒸発器１０を通過して冷媒に吸熱された冷却水は、エンジン２を冷却することにより再び加熱された温水となる。また、蒸発器１０出口には蒸発器１０を経由した冷却水の温度を検出する冷却水温度センサ
（冷却水温度検出手段）１１が設置されている。 The evaporator 10 exchanges heat between the cooling water that circulates in the cooling water circuit 4 and the refrigerant that circulates in the RC circuit 6, thereby using the cooling water heated by the engine 2, that is, warm water as a heat medium as waste heat of the engine 2. Is recovered by absorbing heat to the RC circuit 6 side. On the other hand, the cooling water absorbed by the refrigerant after passing through the evaporator 10 becomes warm water heated again by cooling the engine 2. A cooling water temperature sensor (cooling water temperature detecting means) 11 for detecting the temperature of the cooling water passing through the evaporator 10 is installed at the outlet of the evaporator 10.

ラジエータ１２は、蒸発器１０と直列に配列され、蒸発器１０を通過して冷媒に吸熱された冷却水を外気の送風による熱交換により更に冷却し、ひいてはエンジン２を所望の温度に冷却している。
サーモスタット１４は、冷却水温度に応じてラジエータ１２へ通水される冷却水量を制御する機械式の三方弁であって、２つの入口ポートと１つの出口ポートとを有している。２つの入口ポートには、ラジエータ１２から延設される流路５ａと、蒸発器１０とラジエータ１２との間の流路５ｂからラジエータ１２を迂回して接続されるバイパス路５ｃとがそれぞれ接続され、これにより、冷却水温度に応じてラジエータ１２へ通水される冷却水量が増減されて冷却水温度が適正に保持される。 The radiator 12 is arranged in series with the evaporator 10, further cools the cooling water that has passed through the evaporator 10 and is absorbed by the refrigerant by heat exchange by blowing outside air, and thereby cools the engine 2 to a desired temperature. Yes.
The thermostat 14 is a mechanical three-way valve that controls the amount of cooling water that is passed to the radiator 12 according to the cooling water temperature, and has two inlet ports and one outlet port. The two inlet ports are connected to a flow path 5a extending from the radiator 12 and a bypass path 5c connected to bypass the radiator 12 from the flow path 5b between the evaporator 10 and the radiator 12, respectively. Thus, the amount of cooling water passed to the radiator 12 is increased or decreased according to the cooling water temperature, and the cooling water temperature is appropriately maintained.

水ポンプ１６は、エンジン２に装着され、エンジン２の回転数に応じて駆動されて冷却水回路４に冷却水を好適に循環させる。
一方、ＲＣ回路６は、冷媒の循環路７に、冷媒の流れ方向から順に蒸発器１０、膨張機２０、再生器２２、コンデンサ２４、気液分離器２６、冷媒ポンプ２８が順に介挿されて閉回路を構成している。 The water pump 16 is attached to the engine 2 and is driven according to the rotational speed of the engine 2 to circulate the cooling water in the cooling water circuit 4 appropriately.
On the other hand, in the RC circuit 6, the evaporator 10, the expander 20, the regenerator 22, the condenser 24, the gas-liquid separator 26, and the refrigerant pump 28 are inserted in this order in the refrigerant circulation path 7 from the refrigerant flow direction. A closed circuit is configured.

膨張機２０は、蒸発器１０で加熱されて過熱蒸気の状態となった冷媒を膨張させ、回転駆動力を発生する流体機器であって、膨張機２０には、発生した回転駆動力を電力変換して廃熱利用装置の外部で利用可能とする発電機３０が機械的に連結されている。
再生器２２は、膨張機２０出口の冷媒で蒸発器１０入口の冷媒を加熱するＲＣ回路６の内部熱交換器であって、膨張機２０出口側の熱量を膨張機２０入口側に積極的に供給することにより、ＲＣ回路６における回収エネルギーを増大させている。 The expander 20 is a fluid device that expands the refrigerant heated to the superheated steam state by the evaporator 10 and generates a rotational driving force. The expander 20 converts the generated rotational driving force into electric power. Thus, the generator 30 that can be used outside the waste heat utilization apparatus is mechanically connected.
The regenerator 22 is an internal heat exchanger of the RC circuit 6 that heats the refrigerant at the inlet of the evaporator 10 with the refrigerant at the outlet of the expander 20, and positively transfers the heat amount at the outlet of the expander 20 to the inlet side of the expander 20. By supplying, the recovered energy in the RC circuit 6 is increased.

コンデンサ２４は、再生器２２を経由した冷媒をファン２５による外気の送風により凝縮液化させる放熱器であり、ファン２５はその駆動部に入力される信号に応じて駆動される電動ファンである。また、ファン２５は車両の前面側から順にコンデンサ２４、ラジエータ１２を介して配置されており、ラジエータ１２への外気の送風にも兼用されている。
気液分離器２６は、コンデンサ２４にて凝縮された冷媒を気液二層に分離するレシーバであり、ここで分離された液冷媒のみが冷媒ポンプ２８側に流出される。 The condenser 24 is a heat radiator that condenses and liquefies the refrigerant that has passed through the regenerator 22 by blowing outside air from the fan 25, and the fan 25 is an electric fan that is driven in accordance with a signal input to its drive unit. Further, the fan 25 is disposed in order from the front side of the vehicle via the condenser 24 and the radiator 12, and is also used for blowing outside air to the radiator 12.
The gas-liquid separator 26 is a receiver that separates the refrigerant condensed by the capacitor 24 into two layers of gas and liquid, and only the liquid refrigerant separated here flows out to the refrigerant pump 28 side.

冷媒ポンプ２８は、その駆動部に入力される信号に応じて駆動される電動ポンプであり、気液分離器２６から流出された液冷媒は冷媒ポンプ２８によって蒸発器１０側に圧送され、ＲＣ回路６を好適に循環させる。
このように構成される冷却水回路４及びＲＣ回路６は、車両を総合的に制御する電子制御装置である図示しないＥＣＵ（制御手段）により制御される。具体的には、ＥＣＵには、ファン２５及び冷媒ポンプ２８の各駆動部とともに、冷却水温度センサ１１、図示しない外気温度センサ、車速センサなどが電気的に接続されており、ＥＣＵは、これらセンサからの入力信号に応じてファン２５及び冷媒ポンプ２８の各駆動部に出力信号を出力し、冷却水回路４及びＲＣ回路６、即ち廃熱利用装置を制御している。 The refrigerant pump 28 is an electric pump that is driven in accordance with a signal input to the drive unit, and the liquid refrigerant that has flowed out of the gas-liquid separator 26 is pumped to the evaporator 10 side by the refrigerant pump 28, and an RC circuit. 6 is suitably circulated.
The cooling water circuit 4 and the RC circuit 6 configured as described above are controlled by an ECU (control means) (not shown) which is an electronic control device that comprehensively controls the vehicle. Specifically, the cooling water temperature sensor 11, an outside air temperature sensor (not shown), a vehicle speed sensor, and the like are electrically connected to the ECU together with the drive units of the fan 25 and the refrigerant pump 28. Output signals are output to the drive units of the fan 25 and the refrigerant pump 28 in response to the input signal from the fan 25, and the cooling water circuit 4 and the RC circuit 6, that is, the waste heat utilization device are controlled.

図２は、車両が所定の車速にて走行中にファン２５によりコンデンサ２４に送風される外気の風量Ｆに応じた、ファン２５のファン消費電力Ｅｆ、冷媒ポンプ２８のポンプ消費電力Ｅｐ、膨張機２０を介して発電機３０にて発電される発電量Ｅｇ、発電量Ｅｇからファン消費電力Ｅｆ、及びポンプ消費電力Ｅｐを減じた正味発電量Ｅｎ（＝Ｅｇ−Ｅｆ−Ｅｐ）、蒸発器１０にて冷却水回路４からＲＣ回路６に向けて吸熱されたエバ吸熱量Ｑｉｎを示している。 FIG. 2 shows the fan power consumption E f of the fan 25 and the pump power consumption E p of the refrigerant pump 28 according to the air volume F of the outside air blown to the condenser 24 by the fan 25 while the vehicle is traveling at a predetermined vehicle speed. power generation amount E g that is generated by the generator 30 via the expander 20, the power generation amount E g from the fan power E f, and net power generation amount E n by subtracting the pump power consumption E p (= E g -E f− E p ), the evaporator endothermic amount Q in absorbed by the evaporator 10 from the cooling water circuit 4 toward the RC circuit 6 is shown.

電力量Ｅｆ、Ｅｐ、Ｅｇ、Ｅｎ、及びエバ吸熱量Ｑｉｎは、コンデンサ２４における放熱量Ｑｏｕｔが風量Ｆ、即ちファン２５の回転数に依存することから、ファン２５の回転数が決まると略一義的に決まり、また、車両の車速や型式、排気量などで決まる固有のデータである。
ＥＣＵでは、ファン２５及びポンプ２８を正味発電量Ｅｎが増大するように、例えば最大値Ｅｎｍａｘ（図２では約５１０Ｗ）となる風量Ｆ（例えば、図２では約２８．６ｍ３／ｍｉｎ）を得る回転数で駆動するためのファン２５及びポンプ２８の印加電圧・印加電流や駆動デューティなどの制御値が算出され、これらの制御値は、エンジン２の作動状態を含むＲＣ回路６の外乱要素値Ｆｄの変化に基づき、ＥＣＵの図示しない外部メモリに格納されたマップにマッピングされている。そして、このマップを参照することにより、車速センサにて検出される車速やエバ吸熱量Ｑｉｎなどから算出されるエンジン２の廃熱量Ｑｗといった外乱要素値Ｆｄの変化に応じて最適な制御値が都度選定され、ファン２５及びポンプ２８の回転数は正味発電量Ｅｎを最大値Ｅｎｍａｘとするべく制御される。 The amount of electric power E f , E p , E g , E n , and the amount of heat absorption Q in are equal to the number of revolutions of the fan 25 because the amount of heat dissipation Q out in the capacitor 24 depends on the amount of air F, ie, the number of revolutions of the fan 25. This is unique data determined by the vehicle speed, type, displacement, etc. of the vehicle.
In ECU, the fan 25 and the pump 28 as the net power generation amount E n increases, for example, the maximum value E nmax (in FIG. 2 about 510W) become airflow F (e.g., approximately in FIG. 2 28.6m 3 / min) Control values such as the applied voltage / current and drive duty of the fan 25 and the pump 28 for driving at a rotational speed to obtain the engine 2 are calculated. These control values are disturbance elements of the RC circuit 6 including the operating state of the engine 2. based on the change in the value F d, is mapped to the map stored in the external memory (not shown) of the ECU. Then, by referring to this map, the optimum control in accordance with a change in the waste heat amount Q w such disturbance element value F d of the engine 2 is calculated from the vehicle speed and evaporator heat absorption amount Q in detected by the vehicle speed sensor value is selected each time, the rotational speed of the fan 25 and the pump 28 is controlled to a maximum value E nmax net power generation amount E n.

図３は、外乱要素値Ｆｄの一つである車速の変化に対するポンプ２８の回転数の変化を時系列的に示している。車両を例えば約２５ｋｍ／ｈから約５０ｋｍ／ｈに加速した後、更に約２５ｋｍ／ｈに減速した場合、上記マップのみを参照すると、車両の加減速過程におけるポンプ回転数は、図３中破線で示すような所定の傾斜、即ち所定の加減速度で車両の加減速度に対して比例的に変化する。なお、このようなポンプ回転数の加減速度は、循環路７を流動可能な冷媒量、即ち、循環路７の流路断面積や、循環路７に封入される冷媒量、蒸発器１０の伝熱面積などに依存している。 Figure 3 is a time series shows the rotation speed of the change of the pump 28 with respect to the vehicle speed change which is one of the disturbance element value F d. For example, when the vehicle is accelerated from about 25 km / h to about 50 km / h and then further decelerated to about 25 km / h, referring to only the above map, the pump speed in the acceleration / deceleration process of the vehicle is indicated by a broken line in FIG. It changes in proportion to the acceleration / deceleration of the vehicle at a predetermined inclination as shown, that is, at a predetermined acceleration / deceleration. Note that the acceleration / deceleration of the pump rotation speed depends on the amount of refrigerant that can flow in the circulation path 7, that is, the cross-sectional area of the circulation path 7, the amount of refrigerant sealed in the circulation path 7, and the transmission of the evaporator 10. It depends on the thermal area.

ここで、本実施形態ではポンプ回転数の遅延制御を行っており、例えば、ポンプ回転数の加減速度を５００ｒｐｍ／ｓの加減速度制限値に制限することにより、ポンプ回転数を上記マップを単に参照する場合の傾斜よりも緩やかな傾斜（図３中、実線で示す）、即ち上記マップを単に参照する場合の破線で示す加減速度よりも低減された加減速度で遅れて変化させる。   Here, in this embodiment, delay control of the pump speed is performed. For example, by limiting the acceleration / deceleration of the pump speed to the acceleration / deceleration limit value of 500 rpm / s, the pump speed is simply referred to the above map. In this case, the slope is changed more slowly than an inclination (indicated by a solid line in FIG. 3), that is, with an acceleration / deceleration that is lower than an acceleration / deceleration indicated by a broken line when the map is simply referred to.

また、図４の一点鎖線で示すように、車速を例えば６区間に亘ってサンプリングして車速の移動平均値を求め、この移動平均値を車速センサにて検出された車速として上記マップに基づいてポンプ２８の回転数を制御することにより、ポンプ回転数を上記マップを単に参照する場合の加減速度（図４中、破線で示す）よりも低減された加減速度（図４中、実線で示す）で遅れて変化させることができ、結果としてポンプ回転数の加減速度を制限する場合と同等の遅延制御を行うこともできる。   Further, as shown by a one-dot chain line in FIG. 4, the vehicle speed is sampled over, for example, six sections to obtain a moving average value of the vehicle speed, and this moving average value is determined as a vehicle speed detected by the vehicle speed sensor based on the above map. By controlling the rotation speed of the pump 28, the acceleration / deceleration (indicated by a solid line in FIG. 4) is reduced compared to the acceleration / deceleration (indicated by a broken line in FIG. 4) when the pump rotation speed is simply referred to the map. As a result, it is possible to perform delay control equivalent to the case where the acceleration / deceleration of the pump rotation speed is limited.

そして、このような加減速度制限値、または、移動平均値を算出するためのサンプリング数は車速を含む外乱要素値Ｆｄやその変化量に応じて決定される。
以下、図５に示されるフローチャートを参照して、上述したようなポンプ回転数の遅延制御を行いながら正味発電量Ｅｎを最大値Ｅｎｍａｘとするべくファン２５及びポンプ２８の回転数を制御するファン・ポンプ回転数制御の制御ルーチンについて更に詳しく説明する。 Then, such acceleration limit value, or, the number of samples for calculating the moving average value is determined according to the disturbance element value F d and the amount of change including vehicle speed.
Hereinafter, with reference to the flowchart shown in FIG. 5, to control the rotational speed of the fan 25 and the pump 28 to the net power generation amount E n and the maximum value E nmax while pump speed of the delay control as described above The fan / pump rotation speed control routine will be described in more detail.

先ず、本回転数制御がスタートされるとＳ１に移行し、Ｓ１では、上記マップを参照したり、特にポンプ回転数の加減速過程においては上記遅延制御を行いつつ、ファン２５及びポンプ２８は車速センサにより検出された車両の車速に応じた回転数にて駆動され、Ｅｎを最大値Ｅｎｍａｘに追従させる制御を行った後（Ｅｎ→Ｅｎｍａｘ）、Ｓ２に移行する。 First, when the rotational speed control is started, the process proceeds to S1. In S1, the fan 25 and the pump 28 are operated at the vehicle speed while referring to the map or performing the delay control in the acceleration / deceleration process of the pump rotational speed. It is driven at a rotational speed corresponding to the speed of the vehicle detected by the sensor, after the control to follow the E n to the maximum value E nmax (E n → E nmax ), the process proceeds to S2.

Ｓ２では、正味発電量Ｅｎが所定値、例えばゼロ以下（Ｅｎ≦０）となるか否かを判定し、判定結果が真（Ｙｅｓ）でＥｎ≦０が成立すると判定された場合にはＳ３に移行し、判定結果が偽（Ｎｏ）でＥｎ≦０が成立しないと判定された場合には再びＳ１に戻ってＥｎ→Ｅｎｍａｘとするべく通常のファン・ポンプ回転数制御を行う。
Ｓ３では、Ｅｎ≦０が所定のｔ時間（所定時間）の間継続されるか否かを判定し、判定結果が真（Ｙｅｓ）でＥｎ≦０がｔ時間継続されると判定された場合にはＳ４に移行し、判定結果が偽（Ｎｏ）でＥｎ≦０がｔ時間継続されないと判定された場合には再びＳ１に戻ってＥｎ→Ｅｎｍａｘとするべく通常のファン・ポンプ回転数制御を行う。 In S2, the net power generation amount E n is a predetermined value, for example, determines whether a zero or less (E n ≦ 0), if the determination result is E n ≦ 0 is determined to be satisfied in true (Yes) Shifts to S3, and if the determination result is false (No) and it is determined that E n ≦ 0 does not hold, the routine returns to S1 again and normal fan / pump rotation speed control is performed so that E n → E nmax. Do.
In S3, it is determined whether or not E n ≦ 0 is continued for a predetermined t time (predetermined time), and it is determined that the determination result is true and E n ≦ 0 is continued for t time. If it is determined that the determination result is false (No) and that E n ≦ 0 is not continued for t time, the routine returns to S1 again and a normal fan pump is set to make E n → E nmax. Rotational speed control is performed.

Ｓ４では、ファン２５及びポンプ２８の駆動を停止、即ちＲＣ回路６の機能を停止した後にＳ５に移行する。
Ｓ５では、冷却水温度センサ１１にて検出された冷却水温度Ｔｒが所定の上限温度（所定温度）Ｔｈ以上（Ｔｒ≧Ｔｈ）となるか否かを判定し、判定結果が真（Ｙｅｓ）でＴｒ≧Ｔｈが成立すると判定された場合にはＳ６に移行し、判定結果が偽（Ｎｏ）でＴｒ≧Ｔｈが成立しないと判定された場合には再びＳ４に戻ってファン２５及びポンプ２８の駆動の停止を保持する。 In S4, the driving of the fan 25 and the pump 28 is stopped, that is, the function of the RC circuit 6 is stopped, and then the process proceeds to S5.
In S5, it is determined whether or not the coolant temperature Tr detected by the coolant temperature sensor 11 is equal to or higher than a predetermined upper limit temperature (predetermined temperature) Th ( Tr ≧ Th ), and the determination result is true. If it is determined in (Yes) that T r ≧ T h is established, the process proceeds to S6. If the determination result is false (No) and it is determined that T r ≧ T h is not established, the process returns to S4 again. Thus, the driving of the fan 25 and the pump 28 is stopped.

Ｓ６では、ファン２５の駆動を開始した後にＳ７に移行する。駆動されたファン２５は本制御ルーチンとは異なる後述するファン回転数制御の制御ルーチンの実行により単独で回転数制御される。
Ｓ７では、ポンプ２８の駆動を開始、即ちＲＣ回路６の機能を復帰した後にＳ８に移行する。駆動されたポンプ２８は本制御ルーチンとは異なる後述するポンプ回転数制御の制御ルーチンの実行により単独で回転数制御される。 In S6, after driving of the fan 25 is started, the process proceeds to S7. The driven fan 25 is independently controlled in rotational speed by execution of a control routine for fan rotational speed control, which will be described later, which is different from this control routine.
In S7, the driving of the pump 28 is started, that is, after the function of the RC circuit 6 is restored, the process proceeds to S8. The driven pump 28 is independently controlled in rotational speed by executing a control routine for pump rotational speed control, which will be described later, which is different from this control routine.

Ｓ８では、正味発電量Ｅｎがゼロより大（Ｅｎ＞０）となるか否かを判定し、判定結果が真（Ｙｅｓ）でＥｎ＞０が成立すると判定された場合にはＳ９に移行し、判定結果が偽（Ｎｏ）でＥｎ＞０が成立しないと判定された場合には再びＳ６に戻ってファン２５、ポンプ２８のそれぞれの単独の回転数制御を継続する。
Ｓ９では、Ｅｎ＞０が所定のｔ1時間（第３所定時間）の間継続されるか否かを判定し、判定結果が真（Ｙｅｓ）でＥｎ＞０がｔ1時間継続されると判定された場合には再びＳ１に戻ってＥｎ→Ｅｎｍａｘとするべく通常のファン・ポンプ回転数制御に復帰し、判定結果が偽（Ｎｏ）でＥｎ＞０がｔ1時間継続されないと判定された場合には再びＳ６に戻ってファン２５、ポンプ２８のそれぞれの単独の回転数制御を継続する。 In S8, it is determined whether the net power generation amount E n is to become large (E n> 0) than zero, if the determination result is E n> 0 is determined to be satisfied in true (Yes) in S9 If the determination result is false (No) and it is determined that E n > 0 is not established, the process returns to S6 again and the individual rotation speed control of the fan 25 and the pump 28 is continued.
In S9, E n> 0, it is determined whether to continue for a predetermined t 1 hour (third predetermined time), the judgment result is continued En> 0 is t 1 hour true (Yes) If it is determined, the process returns to S1 again to return to normal fan / pump rotation speed control so that E n → E nmax, and the determination result is false (No) and E n > 0 is not continued for t 1 hours. If it is determined, the process returns to S6 again and the individual rotation speed control of each of the fan 25 and the pump 28 is continued.

以下、図６に示されるフローチャートを参照して、上記Ｓ６にてファン２５単独で実行されるファン回転数制御の制御ルーチンについて説明する。
先ず、本回転数制御がスタートされるとＳ１１に移行し、Ｓ１１では、冷却水温度センサ１１にて検出された冷却水温度Ｔｒが所定の上限温度Ｔｈ未満（Ｔｒ＜Ｔｈ）となるか否かを判定し、判定結果が真（Ｙｅｓ）でＴｒ＜Ｔｈが成立すると判定された場合にはＳ１２に移行してファン２５の回転数を減少させ、判定結果が偽（Ｎｏ）でＴｒ＜Ｔｈが成立しないと判定された場合にはＳ１３に移行してファン２５の回転数を増大させた後、Ｓ１２、Ｓ１３ともにＳ１１に再び戻ってＴｒ＜Ｔｈが成立するか否かの判定を行う。 Hereinafter, with reference to the flowchart shown in FIG. 6, the control routine of the fan rotation speed control executed by the fan 25 alone in S6 will be described.
First, proceeds to step S11 if the speed control is started, in S11, detected by the coolant temperature sensor 11 cooling water temperature T r is less than the predetermined upper limit temperature T h and (T r <T h) If the determination result is true (Yes) and it is determined that T r < Th is satisfied, the process proceeds to S12 to decrease the rotational speed of the fan 25, and the determination result is false (No ) after shifts to S13 to increase the rotational speed of the fan 25 in the case where T r <T h is determined not to be satisfied in, S12, S13 T r <T h is established back again both to S11 It is determined whether or not.

以下、図７に示されるフローチャートを参照して、上記Ｓ７にてポンプ２８単独で実行されるポンプ回転数制御の制御ルーチンについて説明する。
先ず、本回転数制御がスタートされるとＳ２１に移行し、Ｓ２１では、発電量Ｅｇからポンプ消費電力Ｅｐを減じた、ファン消費電力量Ｅｆを除いた正味発電量（第２正味発電量）Ｅ(n-p)（＝Ｅｇ−Ｅｐ）が最大値Ｅ(n-p)ｍａｘとなるようにポンプ２８の回転数を制御し（Ｅ(n-p)→Ｅ(n-p)ｍａｘ）、Ｓ２２に移行する。 Hereinafter, with reference to the flowchart shown in FIG. 7, the control routine of the pump rotation speed control executed by the pump 28 alone in S7 will be described.
First, proceeds to S21 if the speed control is started, in S21, by subtracting the pump power consumption E p from the power generation amount E g, the net power generation amount excluding the fan power consumption E f (second net power Amount) E (np) (= E g −E p ) is controlled so that the rotational speed of the pump 28 becomes the maximum value E (np) max (E (np) → E (np) max ), and the process proceeds to S22. To do.

Ｓ２２では、正味発電量Ｅ(n-p)が所定値、例えばゼロ以下（Ｅ(n-p)≦０）となるか否かを判定し、判定結果が真（Ｙｅｓ）でＥ(n-p)≦０が成立すると判定された場合にはＳ２３に移行し、判定結果が偽（Ｎｏ）でＥ(n-p)≦０が成立しないと判定された場合には再びＳ２１に戻ってＥ(n-p)→Ｅ(n-p)ｍａｘとするべくポンプ回転数制御を行う。
Ｓ２３では、Ｅ(n-p)≦０が所定のｔ2時間（第２所定時間）の間継続されるか否かを判定し、判定結果が真（Ｙｅｓ）でＥ(n-p)≦０がｔ2時間継続されると判定された場合には再びＳ２４に移行し、判定結果が偽（Ｎｏ）でＥ(n-p)≦０がｔ2時間継続されないと判定された場合には再びＳ２１に戻ってＥ(n-p)→Ｅ(n-p)ｍａｘとするべくポンプ回転数制御を行う。 In S22, it is determined whether or not the net power generation amount E (np) is a predetermined value, for example, equal to or less than zero (E (np) ≦ 0), and the determination result is true (Yes) and E (np) ≦ 0 is satisfied. If it is determined, the process proceeds to S23. If it is determined that the determination result is false (No) and E (np) ≦ 0 does not hold, the process returns to S21 and E (np) → E (np). Pump rotation speed control is performed so as to obtain max .
In S23, E (np) ≦ 0, it is determined whether to continue for a predetermined t 2 hours (second predetermined time), the determination result is E true (Yes) (np) ≦ 0 is t 2 proceeds to S24 again if it is determined that the time is continued, the determination result when E (np) ≦ 0 is determined to not continue t 2 hours at false (no), returns to S21 again E (np) → E (p) The pump speed is controlled so as to satisfy (np) max .

Ｓ２４では、ポンプ２８の駆動を停止、即ちＲＣ回路６の機能を停止した後に上記ファン・ポンプ回転数制御のＳ８に移行する。
このように、ファン・ポンプ回転数制御が実行されると、Ｅｎ≦０がｔ時間継続するときにはファン２５及びポンプ２８を停止し、その後Ｔｒ≧Ｔｈが成立するとファン２５の駆動を開始してファン２５単独のファン回転数制御を実行し、更にポンプ２８の駆動を開始した後にはポンプ２８単独のポンプ回転数制御を実行する。これらファン回転数制御及びポンプ回転数制御はファン・ポンプ回転数制御と並行して実行され、ファン・ポンプ回転数制御のＳ９を経由してＳ１に戻ったときにはファン回転数制御及びポンプ回転数制御はリセットされ、Ｅｎ→Ｅｎｍａｘとするべく通常のファン・ポンプ回転数制御が実行される。 In S24, the driving of the pump 28 is stopped, that is, the function of the RC circuit 6 is stopped, and then the process proceeds to S8 of the fan / pump rotation speed control.
As described above, when the fan / pump rotation speed control is executed, the fan 25 and the pump 28 are stopped when E n ≦ 0 continues for t time, and then the drive of the fan 25 is started when T r ≧ T h is satisfied. Then, the fan rotation speed control of the fan 25 alone is executed, and after the driving of the pump 28 is started, the pump rotation speed control of the pump 28 alone is executed. The fan rotation speed control and the pump rotation speed control are executed in parallel with the fan / pump rotation speed control, and when returning to S1 via S9 of the fan / pump rotation speed control, the fan rotation speed control and the pump rotation speed control are performed. Is reset, and normal fan / pump rotation speed control is executed so that E n → E nmax .

以上のように、本実施形態では、発電機３０にて発電された発電量Ｅｇからファン消費電力Ｅｆ、及びポンプ消費電力Ｅｐを減じた正味発電量Ｅｎが算出され、正味発電量Ｅｎを最大値Ｅｎｍａｘとするべくファン２５及びポンプ２８の回転数を制御する。これにより、正味発電量Ｅｎを極力増大することができ、廃熱利用装置の有効エネルギー回収量を増大することができる。 As described above, in this embodiment, the power generation is power generation amount E g from the fan power E f, and net power generation amount E n by subtracting the pump power consumption E p is calculated by the generator 30, the net power generation amount the E n for controlling the rotational speed of the fan 25 and the pump 28 so as to obtain the maximum value E nmax. Thus, it is possible to increase the net power generation amount E n utmost, it is possible to increase the effective energy recovery amount of the waste heat utilization device.

しかも、本実施形態では、ポンプ２８の回転数の加減速度を所定の加減速度制限値に制限したり、或いは、外乱要素値Ｆｄを所定数サンプリングして算出される車両の移動平均速度に基づいてポンプ２８の回転数を制御することにより、外乱要素値Ｆｄの変化に対してポンプ回転数を遅れて制御する遅延制御が行われている。
ここで、ＥＣＵは、エンジン２の廃熱量Ｑｗに合わせてエバ吸熱量Ｑｉｎを増減させるためにポンプ回転数を増減して循環路７における冷媒の循環量を増減させるが、冷媒の循環量を増減に対してエバ吸熱量Ｑｉｎ、即ちＲＣ回路６の冷却水回路４からの吸熱量の増減にはタイムラグがある。 In addition, in this embodiment, the acceleration / deceleration of the rotation speed of the pump 28 is limited to a predetermined acceleration / deceleration limit value, or based on the moving average speed of the vehicle calculated by sampling the disturbance element value Fd by a predetermined number. by controlling the rotational speed of the pump 28 Te, delay control for controlling delayed the pump speed to changes in the disturbance element value F d is performed.
Here, ECU is to increase or decrease the circulation amount of the refrigerant in the circulation path 7 by increasing or decreasing the pump speed to increase or decrease the evaporator heat absorption amount Q in in accordance with the waste heat Q w of the engine 2, the circulation amount of refrigerant There is a time lag in increasing / decreasing the heat absorption amount Q in , that is, the amount of heat absorption from the cooling water circuit 4 of the RC circuit 6.

例えば、廃熱量Ｑｗの増減にポンプ回転数を完全に同期させるべく、車両の車速を増大した場合（アクセルを踏み込んだ場合）、それに合わせてポンプ回転を増大しても、ＲＣ回路６は冷媒を急激には蒸発させることはできないため、その分のポンプ２８の駆動に要したポンプ消費電力が無駄になる。
一方、廃熱量Ｑｗの増減にポンプ回転数を完全に同期させるべく、車両の車速を減少した場合（アクセルを開放した場合）、それに合わせてポンプ回転数を減少すると、冷媒の余熱で冷媒の蒸発が未だ充分に可能であるにも拘わらず、蒸発器１０へ流入する冷媒が不足し、膨張機２０、発電機３０を介して本来得られたはずの発電量Ｅｇを得ることができない。 For example, in order to fully synchronize the pump speed to increase or decrease the amount of waste heat Q w, if you increase the speed of the vehicle (if depresses the accelerator), even if increasing the pump rotation accordingly, RC circuit 6 refrigerant Therefore, the power consumption of the pump required for driving the pump 28 is wasted.
On the other hand, in order to fully synchronize the pump speed to increase or decrease the amount of waste heat Q w, when reducing the speed of the vehicle (when opening the accelerator) and reducing the pump speed accordingly, the refrigerant in the residual heat of the refrigerant Although the evaporation is still possible, the refrigerant flowing into the evaporator 10 is insufficient, and the power generation amount E g originally obtained through the expander 20 and the generator 30 cannot be obtained.

かかる場合において、上記遅延制御を行うことによって正味発電量Ｅｎを効果的に増大することができ、廃熱利用装置の有効エネルギー回収量をより一層増大することができる。
更に、外乱要素値Ｆｄやその変化量に応じて、所定の加減速度制限値、または、移動平均値を算出するための外乱要素値Ｆｄのサンプリング数を決定することにより、外乱要素値Ｆｄの大きさ、変動幅、変動方向に応じて精度良く遅延制御を行うことができるため、正味発電量Ｅｎを更に効果的に増大することができる。 In such a case, it can effectively increase the net power generation amount E n by performing the delay control, it is possible to further increase the effective energy recovery amount of the waste heat utilization device.
Furthermore, according to the disturbance element value F d and the change amount, a predetermined deceleration limit value, or by determining the sampling number of the disturbance element value F d for calculating the moving average value, the disturbance element values F d dimensions, fluctuation range, it is possible to accurately perform the delay control according to the variation direction, can be further effectively increase the net power generation amount E n.

更にまた、算出された正味発電量Ｅｎが所定のｔ時間に亘ってゼロ以下となるとき、ファン２５及びポンプ２８の駆動を停止する。これにより、例えばエンジン２のアイドリング時などに廃熱量Ｑｗ、即ち蒸発器１０、換言するとＲＣ回路６におけるエバ吸熱量Ｑｉｎが減少するとき、ファン２５及びポンプ２８の駆動を停止して正味発電量Ｅｎが継続的にゼロ以下になるのを防止する。ここで、正味発電量Ｅｎがゼロ以下となるのが所定のｔ時間に亘ることを条件とすることから、外乱要素値Ｆｄの変動により正味発電量Ｅｎが一時的にゼロ以下となる場合を除外することができるため、正味発電量Ｅｎを効果的に増大することができる。 Furthermore, when the net power generation amount E n calculated is equal to or smaller than zero for a predetermined time t, it stops the driving of the fan 25 and the pump 28. As a result, for example, when the engine 2 is idling, the amount of waste heat Q w , that is, when the evaporator 10, in other words, the heat absorption amount Q in the RC circuit 6, decreases, the driving of the fan 25 and the pump 28 is stopped to generate net power generation to prevent the amount E n is less continuously zero. Here, since the the net power generation amount E n is equal to or less than zero with the proviso that over a predetermined time t, the net power generation amount E n is less temporarily zero fluctuations of the disturbance element value F d it is possible to exclude the case, it is possible to increase the net power generation amount E n effectively.

また、冷却水温度センサ１１にて検出された冷却水温度Ｔｒが所定の上限温度Ｔｈ以上となるとき、駆動を停止されたファン２５を再駆動し、冷却水温度Ｔｒを所定の上限温度Ｔｈ未満に保持するべくファン２５の回転数を制御する。これにより、エンジン２の作動中にＲＣ回路６の機能を停止しても、ラジエータ１２への外気送風により冷却水回路４の冷却水を冷却することができるため、エンジン２の過熱を防止することができる。 Further, when the cooling water temperature Tr detected by the cooling water temperature sensor 11 is equal to or higher than the predetermined upper limit temperature Th, the fan 25 that is stopped from driving is re-driven, and the cooling water temperature Tr is set to the predetermined upper limit temperature Th. controlling the rotational speed of the fan 25 so as to kept below the temperature T h. Thereby, even if the function of the RC circuit 6 is stopped while the engine 2 is in operation, the cooling water of the cooling water circuit 4 can be cooled by the outside air blowing to the radiator 12, thereby preventing overheating of the engine 2. Can do.

更に、ファン２５が再駆動された後には、駆動を停止されたポンプ２８を再駆動し、発電量Ｅｇからポンプ消費電力Ｅｐを減じた正味発電量Ｅ(n-p)を算出し、正味発電量Ｅ(n-p)を最大値Ｅ(n-p)ｍａｘとするべくポンプ回転数を制御する。これにより、エンジン２の過熱を防止するためにファン２５を駆動し、ポンプ２８を再駆動してＲＣ回路６を再作動した場合であって、ＲＣ回路６の作動に関係ないファン消費電力Ｅｆを除いた正味発電量Ｅ(n-p)を極力増大することができ、廃熱利用装置の有効エネルギー回収量を増大することができる。 Further, after the fan 25 is re-driven, the pump 28 stops the driving driven again and calculates the power generation amount E g pump consumed from the power E p a reduced net power generation amount E (np), the net power generation The pump speed is controlled so that the amount E (np) is the maximum value E (np) max . Thereby, in order to prevent the engine 2 from overheating, the fan 25 is driven, the pump 28 is driven again, and the RC circuit 6 is restarted. The fan power consumption E f that is not related to the operation of the RC circuit 6 is obtained. The net power generation amount E (np) excluding can be increased as much as possible, and the effective energy recovery amount of the waste heat utilization device can be increased.

更にまた、算出された正味発電量Ｅ(n-p)が所定のｔ２時間に亘ってゼロ以下となるとき、ポンプ２８の駆動を停止する。これにより、例えばエンジン２のアイドリング時などにエンジン２の廃熱量Ｑｗ、即ち蒸発器１０、換言するとＲＣ回路６におけるエバ吸熱量Ｑｉｎが減少するとき、ポンプ２８の駆動を停止して正味発電量Ｅ(n-p)が継続的にゼロ以下になるのを防止することができる。ここで、正味発電量Ｅ(n-p)がゼロ以下となるのが所定のｔ２時間に亘ることを条件とすることから、外乱要素値Ｆｄの変動により正味発電量Ｅ(n-p)が一時的にゼロ以下となる場合を除外することができるため、正味発電量Ｅ(n-p)を効果的に増大することができる。 Furthermore, when the calculated net power generation amount E (np) becomes equal to or less than zero for a predetermined t 2 hours, the driving of the pump 28 is stopped. Thus, for example, when the amount of waste heat Q w of the engine 2 in such idling of the engine 2, i.e. the evaporator 10, the evaporator heat absorption amount Q in the RC circuit 6 in other words is reduced, the net power generation stops driving the pump 28 It is possible to prevent the amount E (np) from continuously decreasing below zero. Here, since the the net power generation amount E (np) is equal to or less than zero with the proviso that over a predetermined t 2 hours, specifically net power generation amount E (np) temporary fluctuations of the disturbance element value F d Therefore, the net power generation amount E (np) can be effectively increased.

また、算出された正味発電量Ｅｎが所定のｔ１時間に亘ってゼロより大となるとき、正味発電量Ｅｎを最大値Ｅｎｍａｘとするべくファン２５及びポンプ２８の回転数を制御する。これにより、ラジエータ１２への外気送風によりエンジン２の過熱を防止しつつ正味発電量Ｅ(n-p)を最大値Ｅ(n-p)ｍａｘとするためのポンプ回転数のみの制御から、正味発電量Ｅｎを最大値Ｅｎｍａｘとするためのファン２５及びポンプ２８の回転数の制御に迅速に復帰させることができるため、正味発電量Ｅｎを効果的に増大することができ、ひいては廃熱利用装置の有効エネルギー回収量を大幅に増大することができる。 Further, when the net power generation amount E n calculated is larger than zero for a predetermined t 1 hour, to control the rotational speed of the fan 25 and the pump 28 to the net power generation amount E n and the maximum value E nmax . Thus, the control of only pump speed to a maximum value E (np) max while preventing overheating of the engine 2 the net power generation amount E a (np) by the outside air blown to the radiator 12, the net power generation amount E n since it is possible to rapidly return to the rotation speed control of the fan 25 and the pump 28 to the maximum value E nmax, it is possible to increase the net power generation amount E n effectively, thus the waste heat utilization device The effective energy recovery amount can be greatly increased.

以上で本発明の一実施形態についての説明を終えるが、本発明は上記実施形態に限定されるものではなく、本発明の趣旨を逸脱しない範囲で種々の変更ができるものである。
例えば、上記実施形態では、ポンプ回転数の遅延制御にポンプ回転数の加減速度制限値を設けたり、ポンプ回転数を車両の移動平均速度で制御したりしているが、これに限らずポンプ回転数を車両のエンジン２の作動状態を含む外乱要素値Ｆｄに基づいて遅延できれば良い。 The description of one embodiment of the present invention is finished above, but the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention.
For example, in the above embodiment, the pump rotation speed acceleration / deceleration limit value is provided for the pump rotation speed delay control, or the pump rotation speed is controlled by the moving average speed of the vehicle. It is sufficient that the number can be delayed based on the disturbance element value F d including the operating state of the engine 2 of the vehicle.

また、外乱要素値Ｆｄは、車速以外に外気温度やエンジン２の廃熱量Ｑｗ、エンジン２に燃料を供給するためのスロットル開度など様々なパラメータを含むことは勿論である。
更に、上記実施形態では、ＥＣＵにおいて、発電量Ｅｇからファン消費電力Ｅｆ、及びポンプ消費電力Ｅｐを減じることにより正味発電量Ｅｎを算出し、また、発電量Ｅｇからポンプ消費電力Ｅｐを減じた、ファン消費電力量Ｅｆを除く正味発電量Ｅ(n-p)を算出しているが、正味発電量Ｅｎ，Ｅ(n-p)を実測しても良く、この場合にはＥＣＵにおける上記各制御の制御性が向上して好ましい。 In addition to the vehicle speed, the disturbance element value F d naturally includes various parameters such as the outside air temperature, the waste heat amount Q w of the engine 2, and the throttle opening for supplying fuel to the engine 2.
Further, in the above embodiment, in the ECU, the power generation amount E g from the fan power E f, and calculates the net power generation amount E n by subtracting the pump power consumption E p, The pump power from the power generation amount E g minus E p, but calculates the net power generation amount E (np) except the fan power consumption E f, the net power generation amount E n, be actually measured E (np) may, in this case ECU The controllability of each control described above is preferable.

更にまた、上記実施形態では、ＥＣＵにおける各制御により、正味発電量Ｅｎ，Ｅ(n-p)を値がゼロとなることを基準にファン２５及びポンプ２８の起動または停止しているが、これに限らず、例えばファン２５及びポンプ２８の起動または停止に係るエネルギー損失を考慮して、この基準値を正の微少量ｅとして設定しても良く、この場合には廃熱利用装置の有効エネルギー回収量を更に増大することができて好ましい。 Furthermore, in the above embodiment, the fan 25 and the pump 28 are started or stopped on the basis that the net power generation amounts E n and E (np) are zero by each control in the ECU. The reference value may be set as a positive minute amount e in consideration of, for example, energy loss related to the start or stop of the fan 25 and the pump 28. In this case, the effective energy recovery of the waste heat utilization device is possible. The amount can be further increased, which is preferable.

本発明の一実施形態に係る内燃機関の廃熱利用装置を概略的に示した模式図である。1 is a schematic view schematically showing a waste heat utilization device for an internal combustion engine according to an embodiment of the present invention. コンデンサへの外気送風の風量Ｆに応じた、ファン消費電力Ｅｆ、ポンプ消費電力Ｅｐ、発電量Ｅｇ、正味発電量Ｅｎ、エバ吸熱量Ｑｉｎを示した図である。According to the air flow F of the outside air blown to the capacitor is a diagram showing the fan power E f, the pump power consumption E p, the power generation amount E g, the net power generation amount E n, the evaporator heat absorption amount Q in. ポンプ回転数の加減速度を加減速度制限値に制限したときの車速の変化に対するポンプ回転数の変化を時系列的に示した図である。It is the figure which showed the change of the pump rotation speed with respect to the change of the vehicle speed when the acceleration / deceleration speed of the pump rotation speed is limited to the acceleration / deceleration limit value. ポンプ回転数を車速の移動平均値に基づいて制御したときの車速の変化に対するポンプ回転数の変化を時系列的に示した図である。It is the figure which showed the change of the pump rotation speed with respect to the change of the vehicle speed when controlling the pump rotation speed based on the moving average value of the vehicle speed in time series. 図１の廃熱利用装置のＥＣＵが行うファン・ポンプ回転数制御の制御ルーチンを示したフローチャートである。3 is a flowchart showing a control routine of fan / pump rotation speed control performed by the ECU of the waste heat utilization apparatus of FIG. 1. 図５のファン・ポンプ回転数制御にてファン及びポンプを停止し、ファンを再駆動した場合にファン単独で実行するファン回転数制御の制御ルーチンを示したフローチャートである。6 is a flowchart showing a control routine of fan rotation speed control executed by the fan alone when the fan and pump are stopped by the fan / pump rotation speed control of FIG. 5 and the fan is driven again. 図５のファン・ポンプ回転数制御にてファン及びポンプを停止し、ファンの後にポンプを再駆動した場合にポンプ単独で実行するポンプ回転数制御の制御ルーチンを示したフローチャートである。6 is a flowchart showing a control routine of pump rotation speed control executed by the pump alone when the fan and pump are stopped by the fan / pump rotation speed control of FIG. 5 and the pump is driven again after the fan.

符号の説明Explanation of symbols

２ エンジン（内燃機関）
４ 冷却水回路
６ ランキンサイクル
７ 循環路
１０ 蒸発器
１１ 冷却水温度センサ（冷却水温度検出手段）
１２ ラジエータ
２０ 膨張機
２４ コンデンサ
２５ ファン
２８ 冷媒ポンプ（ポンプ）
３０ 発電機 2 Engine (Internal combustion engine)
4 Cooling water circuit 6 Rankine cycle 7 Circulating path 10 Evaporator 11 Cooling water temperature sensor (cooling water temperature detecting means)
12 Radiator 20 Expander 24 Condenser 25 Fan 28 Refrigerant Pump (Pump)
30 Generator

Claims (10)

作動流体の循環路に、内燃機関の廃熱により作動流体を加熱する蒸発器、該蒸発器から流出された作動流体を膨張させて駆動力を発生する膨張機、該膨張機から流出された作動流体をファンによる外気送風により凝縮させるコンデンサ、該コンデンサから流出された作動流体を前記蒸発器に送出して前記循環路に作動流体を循環させるポンプが介挿されたランキンサイクルと、
前記膨張機に連結され、該膨張機にて発生した駆動力を電力に変換して発電する発電機と、
前記内燃機関の作動状態を含む前記ランキンサイクルの外乱要素値に応じて前記ファン及び前記ポンプの回転数を制御する制御手段とを備え、
前記制御手段は、前記発電機にて発電された発電量から前記ファン及び前記ポンプの消費電力を減じた正味発電量を増大させるように前記ファン及び前記ポンプの回転数を制御することを特徴とする内燃機関の廃熱利用装置。 An evaporator that heats the working fluid by the waste heat of the internal combustion engine in the working fluid circulation path, an expander that expands the working fluid that flows out of the evaporator to generate a driving force, and an operation that flows out of the expander A condenser for condensing the fluid by blowing air from the fan, a Rankine cycle in which a pump for sending the working fluid flowing out of the condenser to the evaporator and circulating the working fluid in the circulation path is inserted;
A generator connected to the expander for converting the driving force generated by the expander into electric power to generate power;
Control means for controlling the rotational speed of the fan and the pump in accordance with a disturbance element value of the Rankine cycle including the operating state of the internal combustion engine,
The control means controls the rotation speed of the fan and the pump so as to increase a net power generation amount obtained by subtracting power consumption of the fan and the pump from a power generation amount generated by the generator. A waste heat utilization device for an internal combustion engine. 前記制御手段は、前記外乱要素値の変化に対して前記ポンプの回転数を遅れて制御する遅延制御を行うことを特徴とする請求項１に記載の内燃機関の廃熱利用装置。   2. The waste heat utilization apparatus for an internal combustion engine according to claim 1, wherein the control unit performs delay control for controlling the rotation speed of the pump with a delay with respect to a change in the disturbance element value. 前記制御手段は、前記ポンプの回転数の加減速度を所定の加減速度制限値に制限することにより遅延制御を行うことを特徴とする請求項２に記載の内燃機関の廃熱利用装置。   The waste heat utilization apparatus for an internal combustion engine according to claim 2, wherein the control means performs delay control by limiting the acceleration / deceleration of the rotational speed of the pump to a predetermined acceleration / deceleration limit value. 前記制御手段は、時系列的に検出される所定数の前記外乱要素値から算出される前記外乱要素値の移動平均値に基づいて前記ポンプの回転数を制御することにより遅延制御を行うことを特徴とする請求項２に記載の内燃機関の廃熱利用装置。   The control means performs delay control by controlling the rotational speed of the pump based on a moving average value of the disturbance element values calculated from a predetermined number of the disturbance element values detected in time series. The waste heat utilization apparatus for an internal combustion engine according to claim 2, wherein the apparatus is a waste heat utilization apparatus. 前記制御手段は、前記外乱要素値やその変化量に応じて、前記所定の加減速度制限値、または、前記移動平均値を算出するための前記外乱要素値の所定数を決定することを特徴とする請求項３または４に記載の内燃機関の廃熱利用装置。   The control means determines the predetermined acceleration / deceleration limit value or the predetermined number of the disturbance element values for calculating the moving average value according to the disturbance element value and the amount of change thereof. The waste heat utilization apparatus for an internal combustion engine according to claim 3 or 4. 前記制御手段は、前記正味発電量が所定時間に亘って所定値以下となるとき、前記ファン及び前記ポンプの駆動を停止することを特徴とする請求項１乃至５の何れかに記載の内燃機関の廃熱利用装置。   6. The internal combustion engine according to claim 1, wherein the control unit stops driving the fan and the pump when the net power generation amount becomes a predetermined value or less over a predetermined time. Waste heat utilization equipment. 前記内燃機関の廃熱によって加熱された冷却水を前記蒸発器に流入させるとともに、該蒸発器から流出された冷却水を前記ファンによる外気送風により冷却させるラジエータを有する冷却水回路と、該内燃機関を経由した冷却水の温度を検出する冷却水温度検出手段とを備え、
前記制御手段は、前記冷却水温度検出手段にて検出された冷却水温度が所定温度以上となるとき、駆動を停止された前記ファンを再駆動し、冷却水温度を前記所定温度未満に保持するべく前記ファンの回転数を制御することを特徴とする請求項６に記載の内燃機関の廃熱利用装置。 A cooling water circuit having a radiator for allowing cooling water heated by waste heat of the internal combustion engine to flow into the evaporator and cooling the cooling water flowing out of the evaporator by blowing outside air from the fan; and the internal combustion engine Cooling water temperature detecting means for detecting the temperature of the cooling water passing through,
When the cooling water temperature detected by the cooling water temperature detection means is equal to or higher than a predetermined temperature, the control means re-drives the fan that has been stopped to hold the cooling water temperature below the predetermined temperature. The waste heat utilization apparatus for an internal combustion engine according to claim 6, wherein the rotational speed of the fan is controlled accordingly. 前記制御手段は、前記ファンが再駆動された後には、駆動を停止された前記ポンプを再駆動し、前記発電量から前記ポンプ消費電力を減じた第２正味発電量を増大させるように前記ポンプの回転数を制御することを特徴とする請求項７に記載の内燃機関の廃熱利用装置。   The control means, after the fan is re-driven, re-drives the pump that has been stopped to increase the second net power generation amount by subtracting the pump power consumption from the power generation amount. The waste heat utilization apparatus for an internal combustion engine according to claim 7, wherein the rotational speed of the internal combustion engine is controlled. 前記制御手段は、前記第２正味発電量が第２所定時間に亘って所定値以下となるとき、前記ポンプの駆動を停止することを特徴とする請求項８に記載の内燃機関の廃熱利用装置。   The waste heat utilization of the internal combustion engine according to claim 8, wherein the control means stops the driving of the pump when the second net power generation amount becomes equal to or less than a predetermined value for a second predetermined time. apparatus. 前記制御手段は、前記正味発電量が第３所定時間に亘って所定値より大となるとき、前記正味発電量を増大させるように前記ファン及び前記ポンプの回転数を制御することを特徴とする請求項９に記載の内燃機関の廃熱利用装置。   The control means controls the rotational speeds of the fan and the pump so as to increase the net power generation amount when the net power generation amount becomes larger than a predetermined value over a third predetermined time. The waste heat utilization apparatus for an internal combustion engine according to claim 9.
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