JPH03111614A - Exhaust heat recovering device for engine - Google Patents
Exhaust heat recovering device for engineInfo
- Publication number
- JPH03111614A JPH03111614A JP1251349A JP25134989A JPH03111614A JP H03111614 A JPH03111614 A JP H03111614A JP 1251349 A JP1251349 A JP 1251349A JP 25134989 A JP25134989 A JP 25134989A JP H03111614 A JPH03111614 A JP H03111614A
- Authority
- JP
- Japan
- Prior art keywords
- heat
- exhaust heat
- temperature
- heat recovery
- exhaust
- 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.)
- Granted
Links
- 239000007788 liquid Substances 0.000 claims abstract description 74
- 239000012530 fluid Substances 0.000 claims abstract description 55
- 238000011084 recovery Methods 0.000 claims description 89
- 230000005855 radiation Effects 0.000 claims description 36
- 239000002918 waste heat Substances 0.000 claims description 15
- 238000001514 detection method Methods 0.000 claims description 12
- 230000020169 heat generation Effects 0.000 claims description 7
- 230000017525 heat dissipation Effects 0.000 claims description 5
- 230000007423 decrease Effects 0.000 description 20
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 8
- 239000000498 cooling water Substances 0.000 description 7
- 230000004048 modification Effects 0.000 description 7
- 238000012986 modification Methods 0.000 description 7
- 239000007789 gas Substances 0.000 description 6
- 238000010521 absorption reaction Methods 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 4
- 238000010248 power generation Methods 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 239000011324 bead Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 239000002737 fuel gas Substances 0.000 description 1
- 235000012907 honey Nutrition 0.000 description 1
- 210000004185 liver Anatomy 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
-
- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Exhaust Gas After Treatment (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
Description
【発明の詳細な説明】 （産業上の利用分野） 本発明は、エンジンの排熱を回収する装置に関する。[Detailed description of the invention] (Industrial application field) The present invention relates to a device for recovering engine exhaust heat.
（従来の技術）
エンジンの排熱回収装置には、従来では、次のようにな
っているものがある。(Prior Art) Some conventional exhaust heat recovery devices for engines are as follows.
エンジンの排熱発生部に排熱回収用熱交換器の放熱路を
循環状に連通し、排熱回収用熱交換器の受熱路に排熱回
収液循環路を循環状に連通し、この排熱回収液循環路に
排熱回収液の循環ポンプと放熱用熱交換器の放熱路とを
直列状に介在させたものである（例えば、米国特許Ｎｏ
、 ４．２２６．２１４）。The heat radiation path of the heat exchanger for exhaust heat recovery is connected in a circular manner to the exhaust heat generation part of the engine, and the heat recovery liquid circulation path is connected in a circular manner to the heat receiving path of the heat exchanger for exhaust heat recovery. A heat recovery liquid circulation path has a circulation pump for an exhaust heat recovery liquid and a heat radiation path of a heat radiation heat exchanger interposed in series (for example, as disclosed in U.S. Patent No.
, 4.226.214).
（発明が解決しようとする課題） 上記の従来構造では次の問題がある。(Problem to be solved by the invention) The above conventional structure has the following problems.
エンジン負荷を一定にして排熱回収している状態では、
エンジンの排熱発生量と放熱用熱交換器の放熱量がバラ
ンスし、放熱用熱交換器の放熱路から受熱した受熱流体
の温度がほぼ−・定になっている。When the engine load is kept constant and exhaust heat is recovered,
The amount of exhaust heat generated by the engine and the amount of heat radiated by the heat radiating heat exchanger are balanced, and the temperature of the heat receiving fluid that receives heat from the heat radiating path of the heat radiating heat exchanger is approximately constant.
しかし、排熱回収中にエンジンの負荷が急激に低下した
場合には、エンジンの排熱発生量が低下するので、排熱
回収用熱交換器の受熱路内を流れる排熱回収液の温度が
低下して、受熱流体の温度が急激に低下する。このため
、例えば、受熱流体を暖房に利用する場合に、その急激
な温度低下で不快感が起きる。また、受熱流体を給湯に
利用する場合には、給湯温度が低く過ぎて使用できない
。However, if the engine load suddenly decreases during exhaust heat recovery, the amount of exhaust heat generated by the engine will decrease, and the temperature of the exhaust heat recovery liquid flowing in the heat receiving path of the exhaust heat recovery heat exchanger will decrease. As a result, the temperature of the heat-receiving fluid drops rapidly. For this reason, for example, when the heat-receiving fluid is used for heating, the sudden temperature drop causes discomfort. Furthermore, when the heat-receiving fluid is used for hot water supply, the hot water supply temperature is too low to be used.
本発明は、エンジンの負荷が低下しても受熱流体の温度
低下を防止することを目的とする。An object of the present invention is to prevent the temperature of the heat-receiving fluid from decreasing even when the engine load decreases.
（課題を解決するための手段）
本発明は、上記目的を達成するために、エンジンの排熱
回収装置を次のように構成したことを特徴としている。(Means for Solving the Problems) In order to achieve the above object, the present invention is characterized in that an engine exhaust heat recovery device is configured as follows.
例えば、第１図から第３図に示すように、エンジン２の
排熱発生部９に排熱回収用熱交換器１３の放熱路１３ａ
を循環状に連通１７、排熱回収用熱交換器１３の受熱路
１３ｂに排熱回収液循環路２０を循環状に連通し、この
排熱回収液循環路２０に排熱回収液の循環ポンプ２１と
放熱用熱交換器２２の放熱路２２ａとを直列状に介在さ
せて構成した、エンジンの排熱回収装置において、
排熱回収液循環路２０に排熱回収液の循環液量調節装置
Ａを介装するとともに、放熱用熱交換器２２に受熱流体
の受熱流体量調節装置Ｂを設け、循環液量調節装置Ａと
受熱流体量調節装置Ｂとを制御装置Ｃを介して排熱回収
液温度検出手段３４に連携し、
上記の排熱回収液温度検出手段３４は、放熱用熱交換器
２２の放熱路２２８入口側における排熱回収液の温度Ｔ
を検出するものであり、上記の制御装置ｃは、排熱回収
液温度検出手段３４の温度検出信号に基づいて、循環液
量調節装置Ａ及び受熱流体量調節装置Ｂを制御作動させ
るものであって、その検出温度が標準温度領域Ｓよりも
低い場合には、排熱回収液の循環量Ｖ及び受熱流体の流
量Ｗを各標準流量ｖ＋ ｏ ” Ｗ １ （１よりも減
少させるように構成したものである。For example, as shown in FIGS. 1 to 3, the heat radiation path 13a of the heat exchanger 13 for exhaust heat recovery is connected to the exhaust heat generation section 9 of the engine 2.
17, an exhaust heat recovery liquid circulation path 20 is connected in a circulation manner to the heat receiving path 13b of the heat exchanger 13 for exhaust heat recovery, and a circulation pump for the exhaust heat recovery liquid is connected to the exhaust heat recovery liquid circulation path 20. 21 and a heat radiation path 22a of a heat radiation heat exchanger 22 are interposed in series. At the same time, the heat exchanger 22 for heat dissipation is provided with a heat-receiving fluid amount adjustment device B for the heat-receiving fluid, and the circulating fluid amount adjustment device A and the heat-receiving fluid amount adjustment device B are connected to the exhaust heat recovery liquid through the control device C. In cooperation with the temperature detection means 34, the waste heat recovery liquid temperature detection means 34 detects the temperature T of the waste heat recovery liquid at the inlet side of the heat radiation path 228 of the heat radiation heat exchanger 22.
The above-mentioned control device c controls and operates the circulating fluid amount adjusting device A and the heat-receiving fluid amount adjusting device B based on the temperature detection signal of the exhaust heat recovery liquid temperature detecting means 34. When the detected temperature is lower than the standard temperature range S, the circulation amount V of the exhaust heat recovery liquid and the flow rate W of the heat receiving fluid are adjusted to each standard flow rate v+ It is something.
（作用） 本発明は次のように作用する。(effect) The invention works as follows.
エンジン２の排熱発生量と放熱用熱交換器２２の放熱量
がバランスしている排熱回収状態で、エンジン２の負荷
が低下した場合には、エンジン２の排熱発生量が低下す
るので、排熱回収液循環路り自由のｔｌＦＩｐＩＬ量ｒ
１ワン方ぬ汎布ｈ（肝玉１丁いビーその温度が標準温度
領域Ｓよりも低下すると、その温度低下を排熱回収液温
度検出手段３４が検出し、制御装置Ｃを介して、排熱回
収液の循環ｆｉＶを減少させて排熱回収液の温度を標準
温度領域Ｓ内に保持するとともに、排熱発生量が減少し
た分だけ受熱流体の流１ｗをも減少させる。これにより
、受熱流体は、受熱温度の低下が回避され、標準温度領
域内に保たれる。In the exhaust heat recovery state where the amount of exhaust heat generated by the engine 2 and the amount of heat radiated by the heat exchanger 22 for heat radiation are balanced, if the load of the engine 2 decreases, the amount of exhaust heat generated by the engine 2 will decrease. , tlFIpIL amount r of exhaust heat recovery liquid circulation path free
1. When the temperature of the universal cloth h (liver beads 1 bee) falls below the standard temperature range S, the exhaust heat recovery liquid temperature detection means 34 detects the temperature drop, and the exhaust heat recovery liquid temperature detecting means 34 detects the temperature drop and The circulation fiV of the heat recovery liquid is reduced to maintain the temperature of the waste heat recovery liquid within the standard temperature range S, and the flow 1w of the heat receiving fluid is also reduced by the amount of reduction in the amount of waste heat generated. The fluid is kept within a standard temperature range, avoiding a drop in heat receiving temperature.
（実施例） 以下、本発明の実施例を図面で説明する。(Example) Embodiments of the present invention will be described below with reference to the drawings.
第１図から第３図は、一実施例を示している。1 to 3 show one embodiment.
第１図は、熱伴給発電装置１のフローシートを示してい
る。FIG. 1 shows a flow sheet of the heat-accompanied power generation device 1.
これは、ガスエンジン２で発電機３を駆動して電力供給
端子４からミツ７を供給すると同時に、ガスエンジン２
の排熱を暖房用の温風として回収するもので、次のよう
になっている。なお、符号６は燃料ガス供給路である。This is done by driving the generator 3 with the gas engine 2 and supplying the honey 7 from the power supply terminal 4, and at the same time, the gas engine 2
The exhaust heat is recovered as hot air for heating, and the process is as follows. In addition, the code|symbol 6 is a fuel gas supply path.
また、符号７は電気制御盤で、これには、商用電源から
制御電源が入力上記の熱伴給発電装置１は、通常の排熱
回収状態では、次のように作動する。Further, reference numeral 7 denotes an electric control panel, into which control power is input from a commercial power source.The heat-accompanied power generation device 1 described above operates as follows in a normal exhaust heat recovery state.
ガスエンジン２の排熱発生部９は、エンジン冷却水の保
有熱を吸収するウォータジャケット１０と、排気ガス保
有熱を吸収する排気熱吸収用熱交換′ａ１１とを備えて
いる。ガスエンジン２の運転に伴って、ウォータジャケ
ット１０で吸熱したエンジン冷却水は、排気熱吸収用熱
交換器１１で加熱されて温度上昇した後５．そのほとん
ど大部分が排熱回収側に切換えられた可変分流弁１２を
通って（実線矢印）排熱回収用熱交換器１３の放熱路１
３ａへ供給され、ここで放熱して、エンジン冷却水循環
ポンプ１４でウォータジャケット１０の入口に戻される
。なお、排気ガスは、排気熱吸収用熱交換器１１で冷却
された後、マフラ１５から外部へ排出される。また、エ
ンジンの低温始動時には、エンジン冷却水をサーモスフ
・ノド式ノイルブ１７からバイパス路１８を経て循環ポ
ンプ１４の人口に戻すことにより、暖機時間を短縮でき
るようになっている。The exhaust heat generation section 9 of the gas engine 2 includes a water jacket 10 that absorbs heat retained in engine cooling water, and an exhaust heat absorption heat exchange 'a11 that absorbs heat retained in exhaust gas. As the gas engine 2 operates, the engine cooling water absorbs heat in the water jacket 10 and is heated in the exhaust heat absorption heat exchanger 11 to increase its temperature. Almost the majority of it passes through the variable flow dividing valve 12 switched to the exhaust heat recovery side (solid arrow), and then passes through the heat radiation path 1 of the heat exchanger 13 for exhaust heat recovery.
3a, where it radiates heat and is returned to the inlet of the water jacket 10 by the engine cooling water circulation pump 14. Note that the exhaust gas is cooled by the exhaust heat absorption heat exchanger 11 and then discharged from the muffler 15 to the outside. Furthermore, when the engine is started at a low temperature, warm-up time can be shortened by returning the engine cooling water from the thermosulfur valve 17 to the circulation pump 14 via the bypass path 18.
上記の排熱回収用熱交換器１３の受熱路１３ｂには排熱
回収液循環路２０が循環状に連通されている。この排熱
回収液循環路２０に排熱回収液の循環ポンプ２１と放熱
用熱交換器２２の放熱路２２ａとが直列状に介在される
。この放熱路２２ａに放熱ファン２３で起こした受熱風
（受熱流体）が流通される。そして、排熱回収用熱交換
器１３の受熱路１３ｂで加熱された排熱回収液循環路２
０内の循環液は、放熱用熱交換器２２の放熱路２２ａで
放熱して受熱風を加熱する。この受熱風が暖房に利用さ
れる。An exhaust heat recovery liquid circulation path 20 is cyclically connected to the heat receiving path 13b of the heat exchanger 13 for exhaust heat recovery. A circulation pump 21 for the exhaust heat recovery liquid and a heat radiation path 22a of the heat radiation heat exchanger 22 are interposed in series in the exhaust heat recovery liquid circulation path 20. Heat-receiving air (heat-receiving fluid) generated by the heat-radiating fan 23 flows through the heat-radiating path 22a. Then, the exhaust heat recovery liquid circulation path 2 heated by the heat receiving path 13b of the heat exchanger 13 for exhaust heat recovery
The circulating fluid in the air radiates heat through the heat radiation path 22a of the heat radiation heat exchanger 22 to heat the heated air. This heated air is used for heating.
一方、上記の排熱回収状態において、放熱用熱交換器２
２の放熱路２２ａでの放熱量の減少等により、排熱回収
量が少なくなって、エンジン冷却水の温度が所定の温度
以上に上昇すると、可変分流弁１２が次のように切換え
られる。即ち、排気熱吸収用熱交換器１１からのエンジ
ン冷却水は、その少な（とも一部分が、放熱側に切換え
られた可変分流弁１２を通って（破線矢印）ラジェータ
２６・２７へも供給され、ここでラジェータファン２８
・２９の冷却風で冷却された後、循環ポンプ１４からウ
ォータジャケット１０へ戻されるのである。On the other hand, in the above exhaust heat recovery state, the heat radiation heat exchanger 2
When the amount of exhaust heat recovered decreases due to a decrease in the amount of heat radiated from the heat radiation path 22a of No. 2, and the temperature of the engine cooling water rises to a predetermined temperature or higher, the variable flow dividing valve 12 is switched as follows. That is, a small portion of the engine cooling water from the exhaust heat absorption heat exchanger 11 is also supplied to the radiators 26 and 27 through the variable flow dividing valve 12 (dashed line arrow) switched to the heat radiation side. Here radiator fan 28
- After being cooled by the cooling air 29, it is returned to the water jacket 10 from the circulation pump 14.
上記の構成において、排熱回収液循環路２０に、電磁弁
３１と流量調節弁３２とからなる循環液量調節装置Ａが
介装される。また、放熱用熱交換器２２に受熱風の受熱
流体量調節装置Ｂが設けられる。この受熱流体量調節装
置Ｂは、放熱ファン２３のモータ２３ａの回転数制御用
のインバータ３３で構成されている。さらに、循環液量
調節装置Ａと受熱流体量調節装置Ｂとが制御装置Ｃを介
して排熱回収液温度検出手段３４に連携される。この排
熱回収液温度検出手段３４は、放熱用熱交換器２２の放
熱路２２ａの入口側における排熱回収液の温度Ｔを検出
するものである。また、上記の制御装置Ｃは、排熱回収
液温度検出手段３４の温度検出信号に基づき、循環液量
調節装置Ａの電磁弁３１と、受熱流体量調節装置Ｂであ
るインノサータ３３とを制御作動させるようになってい
る。In the above configuration, a circulating fluid amount regulating device A consisting of a solenoid valve 31 and a flow regulating valve 32 is interposed in the exhaust heat recovery fluid circulating path 20 . Further, the heat exchanger 22 for heat radiation is provided with a heat receiving fluid amount adjusting device B for the heated air. The heat-receiving fluid amount adjusting device B includes an inverter 33 for controlling the rotation speed of the motor 23a of the heat dissipation fan 23. Further, the circulating fluid amount adjusting device A and the heat receiving fluid amount adjusting device B are linked to the exhaust heat recovery liquid temperature detecting means 34 via the control device C. This exhaust heat recovery liquid temperature detection means 34 detects the temperature T of the exhaust heat recovery liquid on the inlet side of the heat radiation path 22a of the heat radiation heat exchanger 22. Further, the above-mentioned control device C controls and operates the solenoid valve 31 of the circulating fluid amount adjusting device A and the innocerta 33 which is the heat receiving fluid amount adjusting device B based on the temperature detection signal of the exhaust heat recovery liquid temperature detecting means 34. It is designed to let you do so.
まず、排熱回収液の温度制御について説明すると、第２
図に示すように、その温度Ｔは、次のようにして標準温
度領域Ｓ内に保たれる。First, to explain the temperature control of the waste heat recovery liquid, the second
As shown in the figure, the temperature T is maintained within the standard temperature range S in the following manner.
エンジン２が全負荷で定常運転している状態では、第２
図（ｂ）に示すように、電磁弁３１が開弁されて排熱回
収液の循環量■が標準流量Ｖ＋ｏ（ここでは１２０ Ｑ
／ｗｉｎ程度）に保持され、第２図（ａ）に示すよう
に、排熱回収液の温度ＴがＴ、（ここでは８５℃程度）
に保持されるている。When engine 2 is operating steadily at full load,
As shown in FIG.
/win), and as shown in Figure 2(a), the temperature T of the waste heat recovery liquid is T, (here approximately 85°C).
is maintained.
この状態で、エンジン２の負荷が低下すると（時刻ｔＪ
、第２図（ａ）に示すように、排熱回収液の温度Ｔが低
下していく。その温度Ｔｈ（Ｔ、（ここでは８０℃程度
）にまで低下すると、電磁弁３１が閉弁され、第２図（
ｂ）に示すように、排熱回収液の循環ｍｖがＶ、、（、
：：コｔ’は４０１２ ／ｌｌ１ｉｎ程度）に低下する
。これにより、第２図（ａ）に示すように、排熱回収液
の温度Ｔが上昇していく。これを繰り返すことにより、
その温度Ｔが標準温度領域Ｓ内に保たれる。In this state, when the load on the engine 2 decreases (time tJ
, as shown in FIG. 2(a), the temperature T of the exhaust heat recovery liquid decreases. When the temperature drops to Th(T, here about 80°C), the solenoid valve 31 is closed, and as shown in FIG.
As shown in b), the circulation mv of the exhaust heat recovery liquid is V, , (,
::Cot' decreases to about 4012/ll1in). As a result, the temperature T of the exhaust heat recovery liquid increases as shown in FIG. 2(a). By repeating this,
The temperature T is maintained within the standard temperature range S.
なお、上記の電磁弁３１の開閉制御は、排熱回収液の温
度差で行うことに代えて、タイマーで制御することも可
能である。Note that the opening/closing control of the electromagnetic valve 31 described above may be controlled by a timer instead of being controlled by the temperature difference of the exhaust heat recovery liquid.
上記の排熱回収液の温度制御と同時に、インバータ３３
を介して放熱ファン２３の回転数を低くすることにより
、受熱風の流量Ｗが標準流量よりも減少される。これに
より、受熱風の温度が一定に保たれる。At the same time as controlling the temperature of the waste heat recovery liquid described above, the inverter 33
By lowering the rotational speed of the heat dissipation fan 23 via the fan 23, the flow rate W of the heated air is reduced compared to the standard flow rate. This keeps the temperature of the heated air constant.
これを第３図でさらに具体的に説明する。This will be explained in more detail with reference to FIG.
第３図（ａ）に示すように、エンジン排熱発生量Ｑ、が
標準のＱ １Ｇの状態では、排熱回収液の循環量Ｖが標
準流量■、。であり、排熱回収用熱交換器１３の出入口
における排熱回収液の温度差ΔＴ。As shown in FIG. 3(a), when the engine exhaust heat generation amount Q is the standard Q1G, the circulation amount V of the exhaust heat recovery liquid is the standard flow rate ■. and the temperature difference ΔT of the exhaust heat recovery liquid at the entrance and exit of the heat exchanger 13 for exhaust heat recovery.
がΔＴ１ｏとなっている。この状態で、エンジン排熱発
生量がＱ １０からＱ、に低下すると、排熱回収液の温
度差ΔＴ、がΔＴ、。からΔＴ４．に低下してしまう。is ΔT1o. In this state, when the amount of engine exhaust heat generation decreases from Q10 to Q, the temperature difference ΔT of the exhaust heat recovery liquid becomes ΔT. From ΔT4. It will drop to .
そこで、排熱回収液の循環量Ｖをｖｌｏからｖｌｌに低
下させることにより、排熱回収液の温度差ΔＴ、をΔＴ
、。に保つのである。Therefore, by reducing the circulation amount V of the exhaust heat recovery liquid from vlo to vll, the temperature difference ΔT of the exhaust heat recovery liquid can be reduced by ΔT
,. It is kept to
また、第３図（ｂ）に示すように、放熱用熱交換器２２
での放熱量Ｑ ｔ（” Ｑ 、）が標準のＱ、。の状態
では、受熱流体の流量Ｗが標準流量Ｗ１０で、受熱流体
の温度差ΔＴ、がΔＴ、。となっている。この状態で、
前記第３図（ａ）に示すように、エンジン排熱発生量が
Ｑ １０からＱ、に低下すると、放熱用熱交換器２２の
放熱ｆｆ１Ｑ、がＱ、。からＱ、１に低下するので、こ
のままでは受熱流体の温度差ΔＴ３がΔＴ、。からΔＴ
３１に低下してしまう。そこで、受熱流体の流ｆｉｌＷ
をＷ、。からＷｌｌに低下させることにより、受熱流体
の温度差ΔＴ、をΔＴ、。に保つのである。In addition, as shown in FIG. 3(b), a heat exchanger 22 for heat radiation
In a state where the heat radiation amount Q t ("Q,) is the standard Q,., the flow rate W of the heat receiving fluid is the standard flow rate W10, and the temperature difference ΔT, of the heat receiving fluid is ΔT,. In this state in,
As shown in FIG. 3(a), when the amount of engine exhaust heat generation decreases from Q10 to Q, the heat radiation ff1Q of the heat radiation heat exchanger 22 becomes Q. Since Q, decreases from 1 to 1, the temperature difference ΔT3 of the heat-receiving fluid becomes ΔT. from ΔT
It drops to 31. Therefore, the heat receiving fluid flow filW
W. By decreasing the temperature difference ΔT, of the heat-receiving fluid from Wll to ΔT,. It is kept to
第４図から第６図は、それぞれ変形例を示し、排熱回収
液循環路２０の部分図である。4 to 6 each show a modification and are partial views of the exhaust heat recovery liquid circulation path 20. FIG.
第４図は第１変形例を示している。FIG. 4 shows a first modification.
これは、排熱回収液の循環量調節装置Ａを電動弁３７で
構成したものである。これにより、排熱回収液の循環量
の調節幅が広くとれるので、排熱回収液の温度変化が少
なくてすむ。In this example, the exhaust heat recovery liquid circulation amount adjusting device A is configured with an electric valve 37. As a result, the circulating amount of the exhaust heat recovery liquid can be adjusted over a wide range, so that the temperature change of the exhaust heat recovery liquid can be reduced.
第５図は第２変形例を示している。FIG. 5 shows a second modification.
これは、排熱回収液の循環ポンプ２１のモータにインバ
ータ３９を付設し、このインバータ３９で排熱回収液の
循環量調節装置Ａを構成したちのである。これにより、
排熱回収液の循環量の調節幅が広（とれるので、排熱回
収液の温度変化が少なくてすむ。This is because an inverter 39 is attached to the motor of the exhaust heat recovery liquid circulation pump 21, and this inverter 39 constitutes the exhaust heat recovery liquid circulation amount adjusting device A. This results in
The circulation amount of the waste heat recovery liquid can be adjusted over a wide range, so there are fewer temperature changes in the waste heat recovery liquid.
第６図は第３変形例を示している。FIG. 6 shows a third modification.
これは、第４図の変形例をさらに次のように変形したも
のである。放熱用熱交換器２２が液−液用熱交換器に構
成され、その受熱路２２ｂに受熱ｉ＆（受熱流体）の循
環路４１が連通される。この受熱液循環路４１に循環ポ
ンプ４２と電動弁４３とが直列状に介装される。この電
動弁４３で受熱流体量調節装置Ｂが構成される。そして
、制御装置Ｃは、排熱回収液温度検出手段３４の温度検
出信号に基づき、排熱回収液循環路２０の電動弁３７と
、受熱液循環路４１の電動弁４３とを制御作動させるよ
うになっている。This is a further modification of the modification shown in FIG. 4 as follows. The heat exchanger 22 for heat radiation is configured as a liquid-liquid heat exchanger, and a circulation path 41 for heat receiving i& (heat receiving fluid) is communicated with the heat receiving path 22b. A circulation pump 42 and an electric valve 43 are installed in series in this heat-receiving liquid circulation path 41 . This electric valve 43 constitutes a heat-receiving fluid amount adjusting device B. Then, the control device C controls and operates the electric valve 37 of the exhaust heat recovery liquid circulation path 20 and the electric valve 43 of the heat receiving liquid circulation path 41 based on the temperature detection signal of the exhaust heat recovery liquid temperature detection means 34. It has become.
なお、上記実施例では、熱伴給発電装置１にラジェータ
２６・２７等の放熱回路を設けたが、エンジン２の排熱
発生量と排熱回収用熱交換器１３の放熱量とを制御装置
Ｃによる放熱用熱交換器２２の放熱制御でバランスさせ
てエンジン冷却水の温度上昇を防止することにより、ラ
ジェータ２６・２７等の放熱回路を省略することも可能
である。In the above embodiment, the heat-accompanied power generation device 1 is provided with heat radiation circuits such as the radiators 26 and 27, but the amount of waste heat generated by the engine 2 and the amount of heat released by the heat exchanger 13 for waste heat recovery are controlled by the control device. It is also possible to omit heat radiation circuits such as the radiators 26 and 27 by balancing the heat radiation control of the heat radiation heat exchanger 22 by C and preventing the temperature of the engine cooling water from rising.
（発明の効果）
本発明は、上記のように構成され作用することから次の
効果を奏する。(Effects of the Invention) The present invention has the following effects because it is configured and operates as described above.
エンジンの負荷が低下した場合には、エンジンの排熱発
生量が低下するので、排熱回収液循環路内の排熱回収液
の温度が低下してい（が、制御装置を介して循環液量調
節装置で排熱回収液の温度を標準温度領域内に保持する
とともに受熱流体ｍ調節装置で受熱流体を標準温度領域
内に保持する。When the engine load decreases, the amount of exhaust heat generated by the engine decreases, so the temperature of the exhaust heat recovery fluid in the exhaust heat recovery fluid circulation path decreases (but the amount of circulating fluid is controlled via the control device). The temperature of the waste heat recovery liquid is maintained within the standard temperature range by the regulating device, and the heat receiving fluid is maintained within the standard temperature range by the heat receiving fluid m regulating device.
このため、例えば受熱流体を暖房に利用する場合に、エ
ンジンの負荷低下による受熱流体の温度低下で不快感を
覚えることを回避できる。また、受熱流体を給湯に利用
する場合に、エンジンの負荷低下による給湯温度の異常
低下を防止できる。Therefore, when the heat-receiving fluid is used for heating, for example, it is possible to avoid feeling uncomfortable due to a decrease in the temperature of the heat-receiving fluid due to a decrease in engine load. Furthermore, when the heat-receiving fluid is used for hot water supply, it is possible to prevent an abnormal drop in the hot water supply temperature due to a decrease in engine load.
第１図から第６図は本発明の実施例を示している。
第１図から第３図は一実施例を示し、第１図はエンジン
の排熱回収装置である熱伴給発電装置のフローシート、
第２図は排熱回収液の循環量を調節する装置の作動説明
図、第３図は制御装置の作動説明図である。
第４図から第６図は、それぞれ、変形例を示し、フロー
シートの部分図である。
２・・・エンジン、９・・・排熱発生部、１３・・・排
熱回収用熱交換器、１３ａ・・・放熱路、１３ｂ・・・
受熱路、２０・・・排熱回収液循環路、２１・・・循環
ポンプ、２２・・・放熱用熱交換器、２２ａ・・・放熱
路、３４・・・排熱回収液温度検出手段、
Ａ・・・排熱回収液の循環液量調節装置、Ｂ・・・受熱
流体の受熱流体量調節装置、Ｃ・・・制御装置、Ｓ・・
・標準温度領域、Ｔ・・・排熱回収液の温度、■・・・
排熱回収液の循環量、ｖｌｏ・・・標準流量、Ｗ・・・
受熱流体の流量、Ｗｌ。・・・標準流量。
Ｗ＋＋
Ｗ＋０
金色績
−ワタ九−！１1 to 6 show embodiments of the invention. FIGS. 1 to 3 show an example, and FIG. 1 is a flow sheet of a heat-accompanied power generation device that is an exhaust heat recovery device for an engine;
FIG. 2 is an explanatory diagram of the operation of the device for adjusting the circulation amount of the exhaust heat recovery liquid, and FIG. 3 is an explanatory diagram of the operation of the control device. FIGS. 4 to 6 each show a modification and are partial views of a flow sheet. 2... Engine, 9... Exhaust heat generating section, 13... Heat exchanger for exhaust heat recovery, 13a... Heat radiation path, 13b...
Heat receiving path, 20... Exhaust heat recovery liquid circulation path, 21... Circulation pump, 22... Heat radiation heat exchanger, 22a... Heat radiation path, 34... Exhaust heat recovery liquid temperature detection means, A... Circulating fluid amount adjustment device for exhaust heat recovery liquid, B... Heat receiving fluid amount adjustment device for heat receiving fluid, C... Control device, S...
・Standard temperature range, T...Temperature of waste heat recovery liquid, ■...
Circulation amount of exhaust heat recovery liquid, vlo... standard flow rate, W...
Heat-receiving fluid flow rate, Wl. ...Standard flow rate. W++ W+0 Golden result - Wata 9 -! 1
Claims (1)
交換器（１３）の放熱路（１３ａ）を循環状に連通し、 排熱回収用熱交換器（１３）の受熱路（１３ｂ）に排熱
回収液循環路（２０）を循環状に連通し、この排熱回収
液循環路（２０）に排熱回収液の循環ポンプ（２１）と
放熱用熱交換器（２２）の放熱路（２２ａ）とを直列状
に介在させて構成した、エンジンの排熱回収装置におい
て、 排熱回収液循環路（２０）に排熱回収液の循環液量調節
装置（Ａ）を介装するとともに、放熱用熱交換器（２２
）に受熱流体の受熱流体量調節装置（Ｂ）を設け、循環
液量調節装置（Ａ）と受熱流体量調節装置（Ｂ）とを制
御装置（Ｃ）を介して排熱回収液温度検出手段（３４）
に連携し、 上記の排熱回収液温度検出手段（３４）は、放熱用熱交
換器（２２）の放熱路（２２ａ）入口側における排熱回
収液の温度（Ｔ）を検出するものであり、 上記の制御装置（Ｃ）は、排熱回収液温度検出手段（３
４）の温度検出信号に基づいて、循環液量調節装置（Ａ
）及び受熱流体量調節装置（Ｂ）を制御作動させるもの
であって、その検出温度が標準温度領域（Ｓ）よりも低
い場合には、排熱回収液の循環量（Ｖ）及び受熱流体の
流量（Ｗ）を各標準流量（Ｖ＿１＿０）（Ｗ＿１＿０）
よりも減少させるように構成した、ことを特徴とするエ
ンジンの排熱回収装置。[Claims] 1. A heat radiation path (13a) of a heat exchanger for exhaust heat recovery (13) is connected in a circular manner to the exhaust heat generation part (9) of the engine (2), and heat exchange for exhaust heat recovery is performed. An exhaust heat recovery liquid circulation path (20) is connected in a circular manner to the heat receiving path (13b) of the vessel (13), and a circulation pump (21) for the exhaust heat recovery liquid and a heat radiation are connected to the exhaust heat recovery liquid circulation path (20). In an engine exhaust heat recovery device configured by interposing a heat dissipation path (22a) of a heat exchanger (22) in series, A heat exchanger for heat dissipation (22
) is provided with a heat receiving fluid amount adjusting device (B) for the heat receiving fluid, and the circulating fluid amount adjusting device (A) and the heat receiving fluid amount adjusting device (B) are connected to the exhaust heat recovery liquid temperature detecting means via the control device (C). (34)
The waste heat recovery liquid temperature detection means (34) detects the temperature (T) of the waste heat recovery liquid on the inlet side of the heat radiation path (22a) of the heat radiation heat exchanger (22). , The above control device (C) includes an exhaust heat recovery liquid temperature detection means (3
Based on the temperature detection signal of 4), the circulating fluid amount adjustment device (A
) and the heat-receiving fluid amount adjusting device (B), and when the detected temperature is lower than the standard temperature range (S), the circulation amount (V) of the exhaust heat recovery liquid and the heat-receiving fluid volume control device (B) are controlled. Flow rate (W) for each standard flow rate (V_1_0) (W_1_0)
An exhaust heat recovery device for an engine, characterized in that the exhaust heat recovery device is configured to reduce the heat by more than
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1251349A JP2582301B2 (en) | 1989-09-26 | 1989-09-26 | Engine exhaust heat recovery device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1251349A JP2582301B2 (en) | 1989-09-26 | 1989-09-26 | Engine exhaust heat recovery device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03111614A true JPH03111614A (en) | 1991-05-13 |
| JP2582301B2 JP2582301B2 (en) | 1997-02-19 |
Family
ID=17221507
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1251349A Expired - Lifetime JP2582301B2 (en) | 1989-09-26 | 1989-09-26 | Engine exhaust heat recovery device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2582301B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008290569A (en) * | 2007-05-24 | 2008-12-04 | West Japan Railway Co | Light emission type fascia for railway |
| CN114673582A (en) * | 2022-04-29 | 2022-06-28 | 中国科学技术大学 | Waste heat recovery system for double-split flow type vehicle |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6155116U (en) * | 1984-09-14 | 1986-04-14 | ||
| JPS61118913U (en) * | 1985-01-14 | 1986-07-26 | ||
| JPS62206260A (en) * | 1986-03-06 | 1987-09-10 | Meidensha Electric Mfg Co Ltd | Dual-purpose electricity and steam generation device |
| JPS643020U (en) * | 1987-06-23 | 1989-01-10 | ||
| JPS6460760A (en) * | 1987-08-28 | 1989-03-07 | Kubota Ltd | Waste heat recovering device for water cooled engine |
-
1989
- 1989-09-26 JP JP1251349A patent/JP2582301B2/en not_active Expired - Lifetime
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6155116U (en) * | 1984-09-14 | 1986-04-14 | ||
| JPS61118913U (en) * | 1985-01-14 | 1986-07-26 | ||
| JPS62206260A (en) * | 1986-03-06 | 1987-09-10 | Meidensha Electric Mfg Co Ltd | Dual-purpose electricity and steam generation device |
| JPS643020U (en) * | 1987-06-23 | 1989-01-10 | ||
| JPS6460760A (en) * | 1987-08-28 | 1989-03-07 | Kubota Ltd | Waste heat recovering device for water cooled engine |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008290569A (en) * | 2007-05-24 | 2008-12-04 | West Japan Railway Co | Light emission type fascia for railway |
| CN114673582A (en) * | 2022-04-29 | 2022-06-28 | 中国科学技术大学 | Waste heat recovery system for double-split flow type vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2582301B2 (en) | 1997-02-19 |
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