JP5691844B2 - Heat pump steam generator - Google Patents
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- JP5691844B2 JP5691844B2 JP2011119871A JP2011119871A JP5691844B2 JP 5691844 B2 JP5691844 B2 JP 5691844B2 JP 2011119871 A JP2011119871 A JP 2011119871A JP 2011119871 A JP2011119871 A JP 2011119871A JP 5691844 B2 JP5691844 B2 JP 5691844B2
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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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
Description
本発明は、工場排水などから排熱を回収して蒸気を生成するヒートポンプ式蒸気生成装置に関する。 The present invention relates to a heat pump type steam generator that recovers exhaust heat from factory wastewater and generates steam.
蒸気生成装置の一つとして、ヒートポンプを利用したヒートポンプ式蒸気生成装置がある。ヒートポンプ式蒸気生成装置は、工場排水などから廃熱を回収して蒸気を生成するものであって、ボイラー設備等を利用して蒸気を発生させる燃焼系蒸気生成装置に比べて、ランニングコストが低く、ＣＯ２の排出量を低減できるなどのメリットがある。 As one of the steam generators, there is a heat pump steam generator using a heat pump. A heat pump steam generator recovers waste heat from factory wastewater and generates steam, and its running cost is lower than a combustion steam generator that generates steam using boiler equipment. There are merits such as reduction of CO 2 emission.
特許文献１には、圧縮機の吐出側に一端が接続された冷媒管の他端が、蒸気生成用熱交換器、温水生成用熱交換器、膨張弁、熱回収器を介して前記圧縮機の吸入側に接続された冷媒回路を備え、熱回収器において外部熱源からの熱を回収し、蒸気生成用熱交換器で蒸気を生成し、温水生成用熱交換器で温水を生成するように構成されたヒートポンプ式蒸気・温水生成装置が開示されている。そして、特許文献１のヒートポンプ式蒸気・温水生成装置では、蒸気生成用熱交換器で生成した蒸気中に含まれる水あるいは蒸気の凝縮により液化した水を給水用気液分離器で分離し、給水用気液分離器の気相部に設けられた蒸気供給管から蒸気を外部に取出している。 In Patent Document 1, the other end of the refrigerant pipe having one end connected to the discharge side of the compressor is connected to the compressor via a steam generating heat exchanger, a hot water generating heat exchanger, an expansion valve, and a heat recovery unit. The refrigerant circuit connected to the suction side of the heat recovery unit recovers heat from the external heat source in the heat recovery unit, generates steam in the heat generation heat exchanger, and generates hot water in the heat generation heat exchanger A configured heat pump steam / hot water generator is disclosed. And in the heat pump type steam / hot water generator of Patent Document 1, water contained in the steam generated by the steam generating heat exchanger or water liquefied by condensation of steam is separated by the gas-liquid separator for water supply, Steam is taken out from a steam supply pipe provided in the gas phase part of the gas-liquid separator.
特許文献２には、熱源からの熱で水を蒸発させて蒸気を生成する蒸発器と、前記蒸発器で生成された蒸気を圧縮する圧縮機とを備えたヒートポンプシステムにおいて、圧縮機に流入する蒸気量を制御する手段を設けたことを特徴とするヒートポンプシステムが開示されている。 In Patent Document 2, a heat pump system including an evaporator that evaporates water with heat from a heat source to generate steam and a compressor that compresses the steam generated by the evaporator flows into the compressor. There is disclosed a heat pump system provided with means for controlling the amount of steam.
特許文献１では、ヒートポンプ式蒸気生成装置において使用されているヒートポンプ媒体の臨界温度は、およそ１５０℃であるため、ヒートポンプ式蒸気生成装置では、約１２０〜１３０℃の蒸気を生成することが限界である。したがって、それ以上の温度の蒸気を生成することができないという問題点がある。 In patent document 1, since the critical temperature of the heat pump medium used in the heat pump steam generator is approximately 150 ° C., the heat pump steam generator is limited to generating steam of about 120 to 130 ° C. is there. Therefore, there is a problem that steam having a temperature higher than that cannot be generated.
特許文献２では、蒸発器で生成された蒸気の圧力が低いため、所望の温度（圧力）の蒸気を出力するためには、大容量の圧縮機を使用する必要があり装置が大型化すると共にコストが高くなる。また、圧縮機の動力も大きくなるため、蒸気生成効率が悪くなるという問題点がある。 In Patent Document 2, since the pressure of the steam generated in the evaporator is low, in order to output steam at a desired temperature (pressure), it is necessary to use a large-capacity compressor, and the apparatus becomes larger. Cost increases. Moreover, since the power of a compressor also becomes large, there exists a problem that steam generation efficiency worsens.
したがって、本発明の目的は、蒸気利用設備を所望温度に効率よく加温することが可能なヒートポンプ式蒸気生成装置を提供することにある。 Accordingly, an object of the present invention is to provide a heat pump type steam generator capable of efficiently heating a steam utilization facility to a desired temperature.
上記目的を達成するため、本発明の第１のヒートポンプ式蒸気生成装置は、外部熱源から熱を回収して媒体を加温する排熱回収器、前記排熱回収器を通過した媒体を圧縮する圧縮機、前記圧縮機で圧縮された媒体の熱を被加熱水に伝熱して温水及び蒸気の気液二相流を生成する媒体凝縮器、及び前記媒体凝縮器を通過した媒体を減圧して温度を下げる膨張機を有するヒートポンプ循環経路と、前記媒体凝縮器に供給水を導入する給水経路と、前記媒体凝縮器で生成した、温水及び蒸気の気液二相流を、水蒸気と水とに分離する気液分離器と、前記気液分離器の気相部の蒸気を、蒸気利用設備に送る蒸気取出し経路と、前記気液分離器の液相部と前記給水経路とを接続する水循環経路とを備えたヒートポンプ式蒸気生成装置であって、前記蒸気取出し経路に上流側から第１圧力計と蒸気圧縮機とが設けられると共に、前記蒸気圧縮機の出力を制御する制御装置が設けられており、前記制御装置は、前記蒸気利用設備における所定箇所の測定温度Ｔ１が、同箇所の設定温度Ｔｓｅｔ１に近づくように求められる出力値１と、前記第１圧力計の測定値Ｐ１が、気液分離器の設定圧力値Ｐｓｅｔ１に近づくように求められる出力値２とを比較して、低い方の出力値となるように、前記蒸気圧縮機の出力を制御することを特徴とする。 In order to achieve the above object, a first heat pump type steam generator according to the present invention recovers heat from an external heat source and heats the medium, and compresses the medium that has passed through the exhaust heat recovery apparatus. A compressor, a medium condenser that transfers heat of the medium compressed by the compressor to the water to be heated to generate a gas-liquid two-phase flow of hot water and steam, and a medium that has passed through the medium condenser is depressurized. A heat pump circulation path having an expander for lowering the temperature, a water supply path for introducing feed water to the medium condenser, and a gas-liquid two-phase flow of hot water and steam generated by the medium condenser into steam and water. A gas-liquid separator to be separated; a steam extraction path for sending vapor in a gas phase part of the gas-liquid separator to a steam utilization facility; and a water circulation path connecting the liquid phase part of the gas-liquid separator and the water supply path A heat pump steam generator comprising: A first pressure gauge and a steam compressor are provided from the upstream side in the delivery path, and a control device for controlling the output of the steam compressor is provided, and the control device is provided at a predetermined location in the steam utilization facility. The output value 1 obtained so that the measured temperature T1 approaches the set temperature T set1 at the same location and the measured value P1 of the first pressure gauge are obtained so as to approach the set pressure value P set1 of the gas-liquid separator. The output of the steam compressor is controlled so that the output value is compared with the output value 2 and becomes the lower output value.
前記出力値１は、前記蒸気利用設備における所定箇所の測定温度Ｔ１と、同箇所の設定温度Ｔｓｅｔ１とに基づいてＰＩＤ制御により求められ、前記出力値２は、前記第１圧力計の測定値Ｐ１と、前記設定圧力値Ｐｓｅｔ１とに基づいてＰＩＤ制御により求められることが好ましい。 The output value 1 is obtained by PID control based on a measurement temperature T1 at a predetermined location in the steam utilization facility and a set temperature T set1 at the same location, and the output value 2 is a measurement value of the first pressure gauge. It is preferable to be obtained by PID control based on P1 and the set pressure value Pset1 .
また、本発明の第２のヒートポンプ式蒸気生成装置は、外部熱源から熱を回収して媒体を加温する排熱回収器、前記排熱回収器を通過した媒体を圧縮する圧縮機、前記圧縮機で圧縮された媒体の熱を被加熱水に伝熱して温水及び蒸気の気液二相流を生成する媒体凝縮器、及び前記媒体凝縮器を通過した媒体を減圧して温度を下げる膨張機を有するヒートポンプ循環経路と、前記媒体凝縮器に供給水を導入する給水経路と、前記媒体凝縮器で生成した、温水及び蒸気の気液二相流を、水蒸気と水とに分離する気液分離器と、前記気液分離器の気相部の蒸気を、蒸気利用設備に送る蒸気取出し経路と、前記気液分離器の液相部と前記給水経路とを接続する水循環経路とを備えたヒートポンプ式蒸気生成装置であって、前記蒸気取出し経路に上流側から第１圧力計と蒸気圧縮機と第２圧力計とが設けられると共に、前記蒸気圧縮機の出力を制御する制御装置が設けられており、前記制御装置は、前記蒸気利用設備における所定箇所の測定温度Ｔ１が、同箇所の設定温度Ｔｓｅｔ１に近づくように求められる出力値１を設定値とし、第２圧力計の測定値Ｐ２が、前記出力値１に近づくように求められる出力値３と、前記第１圧力計の測定値Ｐ１が、気液分離器の設定圧力値Ｐｓｅｔ１に近づくように求められる出力値２とを比較して、低い方の出力値となるように、前記蒸気圧縮機の出力を制御することを特徴とする。 The second heat pump type steam generator of the present invention includes an exhaust heat recovery unit that recovers heat from an external heat source and warms the medium, a compressor that compresses the medium that has passed through the exhaust heat recovery unit, and the compression A medium condenser that transfers the heat of the medium compressed in the machine to the water to be heated to generate a gas-liquid two-phase flow of hot water and steam, and an expander that reduces the temperature by depressurizing the medium that has passed through the medium condenser A heat pump circulation path, a water supply path for introducing feed water to the medium condenser, and a gas-liquid separation that separates a gas-liquid two-phase flow of hot water and steam generated by the medium condenser into water vapor and water , A heat pump comprising a steam extraction path for sending the vapor in the gas phase part of the gas-liquid separator to a steam utilization facility, and a water circulation path connecting the liquid phase part of the gas-liquid separator and the water supply path Type steam generator, upstream of the steam extraction path Are provided with a first pressure gauge, a steam compressor and a second pressure gauge, and a control device for controlling the output of the steam compressor is provided. An output value 1 obtained so that the measured temperature T1 approaches the set temperature Tset1 at the same location is set as a set value, and an output value 3 obtained so that the measured value P2 of the second pressure gauge approaches the output value 1 The measured value P1 of the first pressure gauge is compared with the output value 2 obtained so as to approach the set pressure value Pset1 of the gas-liquid separator, and the vapor compression is performed so that the lower output value is obtained. It is characterized by controlling the output of the machine.
前記出力値１は、前記蒸気利用設備における所定箇所の測定温度Ｔ１と、同箇所の設定温度Ｔｓｅｔ１とに基づいてＰＩＤ制御により求められ、前記出力値２は、前記第１圧力計の測定値Ｐ１と、前記設定圧力値Ｐｓｅｔ１とに基づいてＰＩＤ制御により求められ、前記出力値３は、前記第２圧力計の測定値Ｐ２と、前記出力値１とに基づいてＰＩＤ制御により求められることが好ましい。 The output value 1 is obtained by PID control based on a measurement temperature T1 at a predetermined location in the steam utilization facility and a set temperature T set1 at the same location, and the output value 2 is a measurement value of the first pressure gauge. The output value 3 is obtained by PID control based on the measured value P2 of the second pressure gauge and the output value 1 based on P1 and the set pressure value P set1. Is preferred.
また、本発明の第３のヒートポンプ式蒸気生成装置は、外部熱源から熱を回収して媒体を加温する排熱回収器、前記排熱回収器を通過した媒体を圧縮する圧縮機、前記圧縮機で圧縮された媒体の熱を被加熱水に伝熱して温水及び蒸気の気液二相流を生成する媒体凝縮器、及び前記媒体凝縮器を通過した媒体を減圧して温度を下げる膨張機を有するヒートポンプ循環経路と、前記媒体凝縮器に供給水を導入する給水経路と、前記媒体凝縮器で生成した、温水及び蒸気の気液二相流を、水蒸気と水とに分離する気液分離器と、前記気液分離器の気相部の蒸気を、蒸気利用設備に送る蒸気取出し経路と、前記気液分離器の液相部と前記給水経路とを接続する水循環経路とを備えたヒートポンプ式蒸気生成装置であって、前記蒸気取出し経路に上流側から第１圧力計と蒸気圧縮機とが設けられると共に、前記蒸気圧縮機の出力を制御する制御装置が設けられており、前記制御装置は、前記蒸気利用設備における所定箇所の測定圧力Ｐ３が、同箇所の設定圧力Ｐｓｅｔ２に近づくように求められる出力値４と、前記第１圧力計の測定値Ｐ１が、気液分離器の設定圧力値Ｐｓｅｔ１に近づくように求められる出力値２とを比較して、低い方の出力値となるように、前記蒸気圧縮機の出力を制御することを特徴とする。 The third heat pump type steam generator of the present invention includes an exhaust heat recovery unit that recovers heat from an external heat source and heats the medium, a compressor that compresses the medium that has passed through the exhaust heat recovery unit, and the compression A medium condenser that transfers the heat of the medium compressed in the machine to the water to be heated to generate a gas-liquid two-phase flow of hot water and steam, and an expander that reduces the temperature by depressurizing the medium that has passed through the medium condenser A heat pump circulation path, a water supply path for introducing feed water to the medium condenser, and a gas-liquid separation that separates a gas-liquid two-phase flow of hot water and steam generated by the medium condenser into water vapor and water , A heat pump comprising a steam extraction path for sending the vapor in the gas phase part of the gas-liquid separator to a steam utilization facility, and a water circulation path connecting the liquid phase part of the gas-liquid separator and the water supply path Type steam generator, upstream of the steam extraction path Are provided with a first pressure gauge and a steam compressor, and a control device for controlling the output of the steam compressor is provided. The control device has a measured pressure P3 at a predetermined location in the steam utilization facility, An output value 4 obtained so as to approach the set pressure P set2 at the same location, and an output value 2 obtained so that the measured value P1 of the first pressure gauge approaches the set pressure value P set1 of the gas-liquid separator. In comparison, the output of the steam compressor is controlled so that the lower output value is obtained.
前記出力値４は、前記蒸気利用設備における所定箇所の測定圧力Ｐ３と、同箇所の設定圧力Ｐｓｅｔ２に基づいてＰＩＤ制御により求められ、前記出力値２は、前記第１圧力計の測定値Ｐ１と、前記設定圧力値Ｐｓｅｔ１とに基づいてＰＩＤ制御により求められることが好ましい。 The output value 4 is obtained by PID control based on a measured pressure P3 at a predetermined location in the steam-using facility and a set pressure Pset2 at the same location, and the output value 2 is a measured value P1 of the first pressure gauge. And the set pressure value P set1 is preferably obtained by PID control.
本発明の第１のヒートポンプ式蒸気生成装置によれば、制御装置によって、蒸気利用設備における所定箇所の測定温度Ｔ１が、同箇所の設定温度Ｔｓｅｔ１に近づくように求められる出力値１と、第１圧力計の測定値Ｐ１が、気液分離器の設定圧力値Ｐｓｅｔ１に近づくように求められる出力値２とを比較して、低い方の出力値となるように、蒸気圧縮機の出力を制御するので、排熱回収器に供給される排熱量に応じて、気液分離器の気相部の蒸気圧力が所定値以下に下がらないように抑制しつつ、蒸気利用設備における所定箇所の温度Ｔ１が設定温度Ｔｓｅｔ１に近づくように、蒸気圧縮機の出力を制御して、気液分離器内の圧力を低下させすぎることなく、高温の蒸気を効率よく蒸気利用設備に供給することができ、速やかに所望温度まで昇温できる。したがって、シンプルなシステム構成で、供給される排熱を最大限に利用しつつ、高温の蒸気を安定して出力できるヒートポンプ式蒸気生成装置を提供することができる。 According to the first heat pump steam generating device of the present invention, the control device determines the measured temperature T1 at a predetermined location in the steam utilization facility so as to approach the set temperature T set1 at the same location, and the first output value 1 1 The measured value P1 of the pressure gauge is compared with the output value 2 obtained so as to approach the set pressure value Pset1 of the gas-liquid separator, and the output of the steam compressor is adjusted so as to be the lower output value. Therefore, the temperature at a predetermined location in the steam utilization facility is controlled in accordance with the amount of exhaust heat supplied to the exhaust heat recovery device, so that the vapor pressure in the gas phase portion of the gas-liquid separator does not drop below a predetermined value. The output of the steam compressor is controlled so that T1 approaches the set temperature Tset1 , and high-temperature steam can be efficiently supplied to the steam utilization facility without reducing the pressure in the gas-liquid separator too much. , Promptly the desired temperature In possible Atsushi Nobori. Therefore, it is possible to provide a heat pump type steam generating apparatus that can stably output high-temperature steam while making maximum use of supplied exhaust heat with a simple system configuration.
また、本発明の第２のヒートポンプ式蒸気生成装置によれば、制御装置によって、前記蒸気利用設備における所定箇所の測定温度Ｔ１が、同箇所の設定温度Ｔｓｅｔ１に近づくように求められる出力値１を設定値とし、第２圧力計の測定値Ｐ２が、出力値１に近づくように求められる出力値３と、第１圧力計の測定値Ｐ１が、気液分離器の設定圧力値Ｐｓｅｔ１に近づくように求められる出力値２とを比較して、低い方の出力値となるように、蒸気圧縮機の出力を制御するので、いわゆるカスケード制御によって、蒸気利用設備における所定箇所の温度をより迅速に設定温度Ｔｓｅｔ１に近づけることができる。 Moreover, according to the 2nd heat pump type | formula steam generator of this invention, the output value 1 calculated | required so that the measurement temperature T1 of the predetermined location in the said steam utilization equipment may approach the set temperature Tset1 of the same location by the control apparatus. Is the set value, and the output value 3 obtained so that the measured value P2 of the second pressure gauge approaches the output value 1 and the measured value P1 of the first pressure gauge become the set pressure value Pset1 of the gas-liquid separator. Since the output of the steam compressor is controlled so as to become the lower output value by comparing with the output value 2 that is required to approach, the temperature at a predetermined location in the steam utilization facility is more quickly obtained by so-called cascade control. To the set temperature T set1 .
また、本発明の第３のヒートポンプ式蒸気生成装置によれば、制御装置によって、蒸気利用設備における所定箇所の測定圧力Ｐ３が、同箇所の設定圧力Ｐｓｅｔ２に近づくように求められる出力値４と、第１圧力計の測定値Ｐ１が、気液分離器の設定圧力値Ｐｓｅｔ１に近づくように求められる出力値２とを比較して、低い方の出力値となるように、蒸気圧縮機の出力を制御するので、気液分離器内の圧力を低下させすぎることなく、高温の蒸気を効率よく蒸気利用設備に供給することができる。 Further, according to the third heat pump type steam generator of the present invention, the output value 4 is calculated by the control device so that the measured pressure P3 at a predetermined location in the steam utilization facility approaches the set pressure P set2 at the same location. The measured value P1 of the first pressure gauge is compared with the output value 2 obtained so as to approach the set pressure value Pset1 of the gas-liquid separator, so that the lower output value is obtained. Since the output is controlled, high-temperature steam can be efficiently supplied to the steam utilization equipment without excessively reducing the pressure in the gas-liquid separator.
［第１の実施形態］
図１に示すように、このヒートポンプ式蒸気生成装置は、排熱回収器１の出口側から伸びた配管Ｌ１が、圧縮機２、媒体凝縮器３、膨張機５の順に経由して、排熱回収器１の入り口側に接続したヒートポンプ循環経路２０を備える。
[First Embodiment]
As shown in FIG. 1, this heat pump type steam generator is configured such that a pipe L <b> 1 extending from the outlet side of the exhaust heat recovery device 1 passes through a compressor 2, a medium condenser 3, and an expander 5 in this order, A heat pump circulation path 20 connected to the inlet side of the collector 1 is provided.
ヒートポンプ循環経路２０では、ヒートポンプ媒体が循環流通しており、ヒートポンプ媒体を介して外部熱源から送られてくる熱媒体（この実施形態では、熱媒体として排温水を使用している）の熱を回収するとともに、給水源から送られてくる供給水にヒートポンプ媒体の熱を伝熱して蒸気を生成するように構成されている。 In the heat pump circulation path 20, the heat pump medium circulates and collects the heat of the heat medium (in this embodiment, waste water is used as the heat medium) sent from the external heat source via the heat pump medium. At the same time, the heat of the heat pump medium is transferred to the supply water sent from the water supply source to generate steam.
ヒートポンプ媒体としては、臨界温度が高く、地球温暖化係数が低く、オゾン破壊係数の低いものが好ましく用いられる。このような媒体としては、１，１，１，３，３−ペンタフルオロプロパン（構造式：ＣＨＦ２ＣＨ２ＣＦ３、Ｒ２４５ｆａ）、ｎ−ペンタン（構造式：Ｃ５Ｈ１２）、１，１，１，２，２，３，３−ヘプタフルオロ−３−メトキシプロパン（構造式：Ｃ３Ｆ７ＯＣＨ３、３Ｍ社製品名：「ＨＦＥ−７０００」）等が挙げられる。これらは、いずれも臨界温度が１５０℃以上であり、地球温暖化係数が低く、オゾン破壊係数が低い。 As the heat pump medium, a medium having a high critical temperature, a low global warming potential, and a low ozone depletion potential is preferably used. As such a medium, 1,1,1,3,3-pentafluoropropane (structural formula: CHF 2 CH 2 CF 3 , R245fa), n-pentane (structural formula: C 5 H 12 ), 1,1 , 1,2,2,3,3-heptafluoro-3-methoxypropane (Structural formula: C 3 F 7 OCH 3 , 3M product name: “HFE-7000”) and the like. All of these have a critical temperature of 150 ° C. or higher, a low global warming potential, and a low ozone depletion potential.
外部熱源から伸びた、排温水が流通する配管Ｌ２は、排熱回収器１を経由して系外に接続している。 A pipe L <b> 2 extending from an external heat source and through which the exhaust hot water flows is connected to the outside of the system via the exhaust heat recovery device 1.
給水源から伸びた、供給水が流通する配管Ｌ３は、給水ポンプＰ１、媒体凝縮器３の順に経由して、気液分離器７の気相部に接続している。 A pipe L3 extending from the water supply source and through which the supply water flows is connected to the gas phase portion of the gas-liquid separator 7 through the water supply pump P1 and the medium condenser 3 in this order.
気液分離器７の気相部には、蒸気利用設備４０に接続する蒸気取出し用の配管Ｌ４が設けられている。この配管Ｌ４には、上流から、第１圧力計３１、蒸気圧縮機３５の順に配置されている。蒸気圧縮機３５は、第１圧力計３１の測定値Ｐ１と、蒸気利用設備４０に設けられた温度計３３の測定値Ｔ１に基づき、制御装置５０によって駆動が制御されている。また、気液分離器７の液相部には、系外の排水系へと伸びる配管Ｌ５と、媒体凝縮器３に接続する配管Ｌ６が設けられている。 In the gas phase portion of the gas-liquid separator 7, a steam extraction pipe L <b> 4 connected to the steam utilization facility 40 is provided. In the pipe L4, the first pressure gauge 31 and the steam compressor 35 are arranged in this order from the upstream. The driving of the steam compressor 35 is controlled by the control device 50 based on the measured value P1 of the first pressure gauge 31 and the measured value T1 of the thermometer 33 provided in the steam utilization facility 40. In addition, a pipe L5 extending to a drainage system outside the system and a pipe L6 connected to the medium condenser 3 are provided in the liquid phase part of the gas-liquid separator 7.
次に、本発明のヒートポンプ式蒸気生成装置の動作について、熱の流れに沿って説明する。 Next, operation | movement of the heat pump type steam generation apparatus of this invention is demonstrated along the flow of heat.
（排温水について）
工場排水系等の外部熱源から送られる排温水は、配管Ｌ２を流通し、排熱回収器１を通過して排水として系外へと送られる。
排熱回収器１では、排温水の熱を、配管Ｌ１を流通するヒートポンプ媒体に伝熱してヒートポンプ媒体を加温する。
(About waste water)
Waste heat water sent from an external heat source such as a factory waste water system flows through the pipe L2, passes through the waste heat recovery device 1, and is sent out of the system as waste water.
In the exhaust heat recovery device 1, the heat of the exhaust hot water is transferred to the heat pump medium flowing through the pipe L1 to heat the heat pump medium.
（ヒートポンプ媒体について）
排熱回収器１にて、排温水との熱交換により加温されたヒートポンプ媒体は、圧縮機２に送られる。
(About heat pump media)
The heat pump medium heated in the exhaust heat recovery device 1 by heat exchange with the exhaust hot water is sent to the compressor 2.
圧縮機２では、ヒートポンプ媒体を所定の圧力まで圧縮して高温高圧にする。この高温高圧になったヒートポンプ媒体は、媒体凝縮器３を通過して、配管Ｌ３を流通する供給水との熱交換に利用される。 In the compressor 2, the heat pump medium is compressed to a predetermined pressure to be a high temperature and a high pressure. The heat pump medium that has become high temperature and pressure passes through the medium condenser 3 and is used for heat exchange with the supply water flowing through the pipe L3.
媒体凝縮器３では、高温高圧になったヒートポンプ媒体の熱を、配管Ｌ３を流通する被加熱水に伝熱して温水及び蒸気の気液二相流を生成する。 In the medium condenser 3, the heat of the heat pump medium that has become high temperature and pressure is transferred to the heated water flowing through the pipe L3 to generate a gas-liquid two-phase flow of hot water and steam.
媒体凝縮器３を通過したヒートポンプ媒体は、膨張機５に送られ、所定圧力まで減圧したのち、排熱回収器１に再び導入して、配管Ｌ２を流通する排温水の熱回収に用いられる。 The heat pump medium that has passed through the medium condenser 3 is sent to the expander 5 and decompressed to a predetermined pressure. Then, the heat pump medium is reintroduced into the exhaust heat recovery unit 1 and used for heat recovery of the exhaust warm water flowing through the pipe L2.
（供給水について）
給水源から給水ポンプＰ１で供給される供給水は、供給水の質量流量Ｑ１が、配管Ｌ４から取出される蒸気の質量流量Ｑ２及び配管Ｌ５からの排水流量Ｑ３との合計量（Ｑ２＋Ｑ３）となるように制御される。
(About supply water)
In the supply water supplied from the water supply source by the water supply pump P1, the mass flow rate Q1 of the supply water is the total amount (Q2 + Q3) of the mass flow rate Q2 of the steam taken out from the pipe L4 and the drainage flow rate Q3 from the pipe L5. To be controlled.
次に、供給水は、配管Ｌ６から送られてくる、気液分離器７内の温水（循環水）と合流して、循環水と供給水との混合水が形成され、媒体凝縮器３に送液される。媒体凝縮器３に導入された混合水は、前述したように高温高圧になったヒートポンプ媒体の熱を回収し、温水及び蒸気の気液二相流を生成して、気液分離器７に送られる。 Next, the supply water is combined with warm water (circulation water) in the gas-liquid separator 7 sent from the pipe L6 to form a mixed water of the circulation water and the supply water. The liquid is sent. The mixed water introduced into the medium condenser 3 recovers the heat of the heat pump medium that has become high temperature and high pressure as described above, generates a gas-liquid two-phase flow of hot water and steam, and sends it to the gas-liquid separator 7. It is done.
気液分離器７では、温水及び蒸気の気液二相流を蒸気と温水とに分離する。そして、気液分離器７の気相部に貯留された蒸気は、蒸気圧縮機３５で所定の温度及び圧力まで圧縮し、蒸気利用設備４０に供給される。また、気液分離器７の液相部に貯留された温水は、配管Ｌ６を通して配管Ｌ３内を流通する供給水と混合して循環利用される。 In the gas-liquid separator 7, the gas-liquid two-phase flow of hot water and steam is separated into steam and hot water. The steam stored in the gas phase portion of the gas-liquid separator 7 is compressed to a predetermined temperature and pressure by the steam compressor 35 and supplied to the steam utilization facility 40. Moreover, the warm water stored in the liquid phase part of the gas-liquid separator 7 is circulated and used by mixing with the supply water flowing through the pipe L3 through the pipe L6.
気液分離器７の液相部に接続された配管Ｌ５からは、循環水系統の塩分の濃縮防止を目的としてブローダウンするために、定期的又は一時的に系外に排水する。 The pipe L5 connected to the liquid phase part of the gas-liquid separator 7 is drained out of the system periodically or temporarily in order to blow down for the purpose of preventing the concentration of salt in the circulating water system.
（制御装置５０での制御について）
次に、制御装置５０で行われる制御について、図２の制御ブロック図を用いて説明する。
(About control by the control apparatus 50)
Next, the control performed by the control device 50 will be described using the control block diagram of FIG.
ＰＩＤ制御器６１に、蒸気利用設備４０の蒸気需要先に設けられた温度計３３の測定値Ｔ１が入力される。ＰＩＤ制御器６１では、測定値Ｔ１が予め設定した設定温度Ｔｓｅｔ１に近づくようにＰＩＤ制御して出力値１を得て、出力値１をローレベルセレクター６５に入力する。 The measured value T1 of the thermometer 33 provided at the steam demand destination of the steam utilization facility 40 is input to the PID controller 61. In the PID controller 61, the output value 1 is obtained by performing PID control so that the measured value T1 approaches the preset temperature Tset1 , and the output value 1 is input to the low level selector 65.
また、ＰＩＤ制御器６２に、第１圧力計３１の測定値Ｐ１が入力される。ＰＩＤ制御器６２では、測定値Ｐ１が予め設定した気液分離器の設定圧力値Ｐｓｅｔ１に近づくように制御して出力値２を得て、出力値２をローレベルセレクター６５に入力する。ここで、出力値２は設定圧力値Ｐｓｅｔ１において出力できる最大値を示すことになる。 In addition, the measured value P1 of the first pressure gauge 31 is input to the PID controller 62. The PID controller 62 controls the measured value P1 so as to approach a preset gas-liquid separator set pressure value Pset1 to obtain an output value 2, and inputs the output value 2 to the low level selector 65. Here, the output value 2 indicates the maximum value that can be output at the set pressure value P set1 .
ローレベルセレクター６５では、入力された出力値１と、出力値２とを比較して、小さい方の出力値を選択してインバータ６７に入力する。 The low level selector 65 compares the input output value 1 with the output value 2 and selects the smaller output value and inputs it to the inverter 67.
インバータ６７では、入力された出力値を、蒸気圧縮機３５の回転数指令値に変換し、得られた回転数指令値を蒸気圧縮機３５に入力して蒸気圧縮機３５の駆動を制御する。 In the inverter 67, the input output value is converted into a rotation speed command value of the steam compressor 35, and the obtained rotation speed command value is input to the steam compressor 35 to control the driving of the steam compressor 35.
蒸気圧縮機３５の回転数を上げて駆動力を高めることで、蒸気利用設備４０に供給する蒸気温度を高めることができる。このため、温度計３３の測定値Ｔ１が予め設定した設定温度Ｔｓｅｔ１に近づくように蒸気圧縮機３５の駆動を制御することで、目的温度の蒸気を蒸気利用設備４０に供給することができる。しかしながら、蒸気圧縮機３５の駆動力を高めるに伴い、蒸気圧縮機３５の入り口圧力、すなわち、気液分離器７の気相部の圧力が低下する傾向にある。気液分離器７の気相部の圧力が低下すると、蒸気の取出しが困難になったり、液相部の水面が安定しなくなったり、気液分離器７から媒体凝縮器３に循環水を供給する際に、送液ポンプがキャビテーションを起こす等の問題が生じる。 The steam temperature supplied to the steam utilization equipment 40 can be increased by increasing the rotational speed of the steam compressor 35 and increasing the driving force. For this reason, the steam of the target temperature can be supplied to the steam utilization equipment 40 by controlling the driving of the steam compressor 35 so that the measured value T1 of the thermometer 33 approaches the preset temperature Tset1 set in advance. However, as the driving force of the steam compressor 35 is increased, the inlet pressure of the steam compressor 35, that is, the pressure in the gas phase portion of the gas-liquid separator 7 tends to decrease. When the pressure in the gas phase part of the gas-liquid separator 7 decreases, it becomes difficult to extract steam, the water surface of the liquid phase part becomes unstable, or the circulating water is supplied from the gas-liquid separator 7 to the medium condenser 3. In doing so, problems such as cavitation of the liquid feed pump occur.
この実施形態によれば、温度計３３の測定値Ｔ１が予め設定した設定温度Ｔｓｅｔ１に近づくようにＰＩＤ制御して出力値１を得ると共に、第１圧力計３１の測定値Ｐ１が予め設定した設定圧力値Ｐｓｅｔ１に近づくようにＰＩＤ制御して出力値２を得て、出力値１及び出力値２のいずれか小さい方の値に基づき、蒸気圧縮機３５の駆動を制御しているので、気液分離器７の気相部の圧力低下を生じさせることなく、高温の蒸気を蒸気利用設備４０に供給して、蒸気利用設備４０を速やかに所望温度まで加温できる。 According to this embodiment, the output value 1 is obtained by performing PID control so that the measured value T1 of the thermometer 33 approaches the preset set temperature Tset1, and the measured value P1 of the first pressure gauge 31 is preset. Since the output value 2 is obtained by performing PID control so as to approach the set pressure value P set1 , and the driving of the steam compressor 35 is controlled based on the smaller one of the output value 1 and the output value 2, Without causing a pressure drop in the gas phase portion of the gas-liquid separator 7, high-temperature steam can be supplied to the steam utilization facility 40, and the steam utilization facility 40 can be quickly heated to a desired temperature.
［第２の実施形態］
次に、図３を用いて、本発明を適用するヒートポンプ式蒸気生成装置の第２の実施形態について説明する。なお、第１の実施形態のヒートポンプ式蒸気生成装置と同一箇所は同一符号を付して、その説明を省略する。
[Second Embodiment]
Next, a second embodiment of a heat pump steam generator to which the present invention is applied will be described with reference to FIG. In addition, the same location as the heat pump type steam generation apparatus of 1st Embodiment attaches | subjects the same code | symbol, and abbreviate | omits the description.
この実施形態では、気取出し用の配管Ｌ４に、上流側から順に、第１圧力計３１、蒸気圧縮機３５、第２圧力計３２が配置されている。そして、蒸気圧縮機３５が、第１圧力計３１の測定値Ｐ１と、第２圧力計３２の測定値Ｐ２と、蒸気利用設備４０に設けられた温度計３３の測定値Ｔ１に基づき、制御装置５１によって駆動が制御されるように構成されている。 In this embodiment, a first pressure gauge 31, a steam compressor 35, and a second pressure gauge 32 are arranged in this order from the upstream side in the air extraction pipe L4. Then, the steam compressor 35 is controlled based on the measured value P1 of the first pressure gauge 31, the measured value P2 of the second pressure gauge 32, and the measured value T1 of the thermometer 33 provided in the steam utilization facility 40. The drive is controlled by 51.
制御装置５１で行われる制御について、図４の制御ブロック図を用いて説明する。 The control performed by the control device 51 will be described with reference to the control block diagram of FIG.
ＰＩＤ制御器６１に、蒸気利用設備４０の蒸気需要先に設けられた温度計３３の測定値Ｔ１が入力される。ＰＩＤ制御器６１では、測定値Ｔ１が予め設定した設定温度Ｔｓｅｔ１に近づくようにＰＩＤ制御して出力値１を得て、出力値１をＰＩＤ制御器６３に入力する。そして、ＰＩＤ制御器６３では、ＰＩＤ制御器６１から出力された出力値１を設定値とし、第２圧力計３２の測定値Ｐ２が、出力値１に近づくようにＰＩＤ制御して出力値３を得て、出力値３をローレベルセレクター６６に入力する。 The measured value T1 of the thermometer 33 provided at the steam demand destination of the steam utilization facility 40 is input to the PID controller 61. The PID controller 61 obtains an output value 1 by performing PID control so that the measured value T1 approaches the preset temperature T set1 set in advance, and inputs the output value 1 to the PID controller 63. The PID controller 63 sets the output value 1 output from the PID controller 61 as a set value, performs PID control so that the measured value P2 of the second pressure gauge 32 approaches the output value 1, and sets the output value 3 to The output value 3 is input to the low level selector 66.
また、ＰＩＤ制御器６２に、第１圧力計３１の測定値Ｐ１が入力される。ＰＩＤ制御器６２では、測定値Ｐ１が予め設定した気液分離器の設定圧力値Ｐｓｅｔ１に近づくように制御して出力値２を得て、出力値２をローレベルセレクター６５に入力する。ここで、出力値２は設定圧力値Ｐｓｅｔ１において出力できる最大値を示すことになる。 In addition, the measured value P1 of the first pressure gauge 31 is input to the PID controller 62. The PID controller 62 controls the measured value P1 so as to approach a preset gas-liquid separator set pressure value Pset1 to obtain an output value 2, and inputs the output value 2 to the low level selector 65. Here, the output value 2 indicates the maximum value that can be output at the set pressure value P set1 .
ローレベルセレクター６６では、入力された出力値２と、出力値３とを比較して、小さい方の出力値を選択してインバータ６７に入力する。 The low level selector 66 compares the input output value 2 with the output value 3 to select the smaller output value and input it to the inverter 67.
インバータ６７では、入力された出力値を、蒸気圧縮機３５の回転数指令値に変換し、得られた回転数指令値を蒸気圧縮機３５に入力して蒸気圧縮機３５の駆動を制御する。 In the inverter 67, the input output value is converted into a rotation speed command value of the steam compressor 35, and the obtained rotation speed command value is input to the steam compressor 35 to control the driving of the steam compressor 35.
この実施形態によれば、温度計３３の測定値Ｔ１が予め設定した設定温度Ｔｓｅｔ１に近づくようにＰＩＤ制御して出力値１を得て、この出力値１を設定値として、第２圧力計３２の測定値Ｐ２が、出力値１に近づくようにＰＩＤ制御して出力値３を得ている。この出力値３は、カスケード制御方式によって得られた出力値であるので、出力値３をローレベルセレクターで選択し、出力値３に基づき蒸気圧縮機３５の駆動を制御した場合、速やかに目的温度の蒸気を蒸気利用設備４０に供給することができる。蒸気利用設備４０の熱容量が大きく、応答が悪い場合に特に有効である。 According to this embodiment, the output value 1 is obtained by performing PID control so that the measured value T1 of the thermometer 33 approaches the preset set temperature Tset1 , and the second pressure gauge is set with the output value 1 as a set value. The output value 3 is obtained by performing PID control so that the measured value P2 of 32 approaches the output value 1. Since this output value 3 is an output value obtained by the cascade control method, when the output value 3 is selected by the low level selector and the driving of the steam compressor 35 is controlled based on the output value 3, the target temperature is quickly obtained. The steam can be supplied to the steam utilization facility 40. This is particularly effective when the steam utilization facility 40 has a large heat capacity and poor response.
また、この実施形態においても、出力値３と、第１圧力計３１の測定値Ｐ１が予め設定した設定圧力値Ｐｓｅｔ１に近づくようにＰＩＤ制御して得た出力値２のいずれか小さい方の値に基づき、蒸気圧縮機３５の駆動を制御しているので、気液分離器７の気相部の圧力低下を生じさせることなく、高温の蒸気を蒸気利用設備４０に供給して、蒸気利用設備４０を速やかに所望温度まで加温できる。 Also in this embodiment, the smaller one of the output value 3 and the output value 2 obtained by PID control so that the measured value P1 of the first pressure gauge 31 approaches the preset pressure value Pset1 set in advance. Since the driving of the steam compressor 35 is controlled based on the value, high-temperature steam is supplied to the steam utilization facility 40 without causing a pressure drop in the gas phase portion of the gas-liquid separator 7 to use the steam. The facility 40 can be quickly heated to a desired temperature.
第２の実施形態の構成によれば、第２の実施形態の構成に比べて、加熱対象物の温度上昇のオーバーシュートを抑制できる利点がある。 According to the structure of 2nd Embodiment, there exists an advantage which can suppress the overshoot of the temperature rise of a heating target object compared with the structure of 2nd Embodiment.
［第３の実施形態］
図５を用いて、本発明を適用するヒートポンプ式蒸気生成装置の第３の実施形態について説明する。なお、第１の実施形態のヒートポンプ式蒸気生成装置と同一箇所は同一符号を付して、その説明を省略する。
[Third Embodiment]
A third embodiment of a heat pump steam generator to which the present invention is applied will be described with reference to FIG. In addition, the same location as the heat pump type steam generation apparatus of 1st Embodiment attaches | subjects the same code | symbol, and abbreviate | omits the description.
この実施形態では、蒸気利用設備が、ボイラー４５から供給される蒸気と、気液分離器７から取出されるヒートポンプからの蒸気とを集合及び分配させる配管を備えた蒸気共通ヘッダ４１であり、蒸気共通ヘッダ４１内に、内部の雰囲気圧力を計測する第３圧力計３４が配置されている。そして、蒸気圧縮機３５が、第１圧力計３１の測定値Ｐ１と、蒸気共通ヘッダ４１に設けられた第３圧力計３４の測定値Ｐ３に基づき、制御装置５２によって駆動が制御されるように構成されている。 In this embodiment, the steam utilization facility is a steam common header 41 having a pipe for collecting and distributing the steam supplied from the boiler 45 and the steam from the heat pump taken out from the gas-liquid separator 7. In the common header 41, the 3rd pressure gauge 34 which measures an internal atmospheric pressure is arrange | positioned. The driving of the steam compressor 35 is controlled by the control device 52 based on the measured value P1 of the first pressure gauge 31 and the measured value P3 of the third pressure gauge 34 provided in the steam common header 41. It is configured.
制御装置５２で行われる制御について、図６の制御ブロック図を用いて説明する。 The control performed by the control device 52 will be described with reference to the control block diagram of FIG.
ＰＩＤ制御器６４に、蒸気共通ヘッダ４１に設けられた第３圧力計３４の測定値Ｐ３が入力される。ＰＩＤ制御器６４では、測定値Ｐ３が予め設定した蒸気共通ヘッダ４１の設定圧力Ｐｓｅｔ２に近づくようにＰＩＤ制御して出力値４を得て、出力値４をローレベルセレクター６５に入力する。 The measured value P3 of the third pressure gauge 34 provided in the steam common header 41 is input to the PID controller 64. The PID controller 64 performs PID control so that the measured value P3 approaches the preset pressure P set2 of the steam common header 41, obtains an output value 4, and inputs the output value 4 to the low level selector 65.
また、ＰＩＤ制御器６２に、第１圧力計３１の測定値Ｐ１が入力される。ＰＩＤ制御器６２では、測定値Ｐ１が予め設定した気液分離器の設定圧力値Ｐｓｅｔ１に近づくように制御して出力値２を得て、出力値２をローレベルセレクター６５に入力する。ここで、出力値２は設定圧力値Ｐｓｅｔ１において出力できる最大値を示すことになる。 In addition, the measured value P1 of the first pressure gauge 31 is input to the PID controller 62. The PID controller 62 controls the measured value P1 so as to approach a preset gas-liquid separator set pressure value Pset1 to obtain an output value 2, and inputs the output value 2 to the low level selector 65. Here, the output value 2 indicates the maximum value that can be output at the set pressure value P set1 .
ローレベルセレクター６５では、入力された出力値４と、出力値２とを比較して、小さい方の出力値を選択してインバータ６７に入力する。 In the low level selector 65, the input output value 4 and the output value 2 are compared, and the smaller output value is selected and input to the inverter 67.
インバータ６７では、入力された出力値を、蒸気圧縮機３５の回転数指令値に変換し、得られた回転数指令値を蒸気圧縮機３５に入力して蒸気圧縮機３５の駆動を制御する。 In the inverter 67, the input output value is converted into a rotation speed command value of the steam compressor 35, and the obtained rotation speed command value is input to the steam compressor 35 to control the driving of the steam compressor 35.
この実施形態によれば、第３圧力計３４の測定値Ｐ３が、予め設定した蒸気共通ヘッダ４１の設定圧力Ｐｓｅｔ２に近づくようにＰＩＤ制御して出力値４を得ると共に、第１圧力計３１の測定値Ｐ１が予め設定した設定圧力値Ｐｓｅｔ１に近づくようにＰＩＤ制御して出力値２を得て、出力値４及び出力値２のいずれか小さい方の値に基づき、蒸気圧縮機３５の駆動を制御しているので、気液分離器７の気相部の圧力低下を生じさせることなく、高温の蒸気を蒸気共通ヘッダ４１に安定供給できる。 According to this embodiment, the measured value P3 of the third pressure gauge 34 is PID controlled so as to approach the preset pressure P set2 of the steam common header 41 to obtain the output value 4, and the first pressure gauge 31 PID control is performed so that the measured value P1 approaches the preset pressure value Pset1 set in advance to obtain the output value 2, and based on the smaller one of the output value 4 and the output value 2, the steam compressor 35 Since driving is controlled, high-temperature steam can be stably supplied to the steam common header 41 without causing a pressure drop in the gas phase portion of the gas-liquid separator 7.
（実施例１）
図１に示すヒートポンプ式蒸気生成装置を使い、第１圧力計３１の圧力が０．１０ＭＰａ・Ｇ（１２０℃飽和蒸気）になるようにヒートポンプ循環経路２０の圧縮機２、膨張機５を運転した。第１圧力計３１の設定圧力値Ｐｓｅｔ１は、０．０４ＭＰａ・Ｇ（１１０℃飽和蒸気）に設定した。この状態で、ＰＩＤ制御器６２の出力は１００％であった。
蒸気利用設備４０加熱対象物を入れ、温度計３３にて温度を測定した。温度計３３の測定値Ｔ１は３０℃であった。設定温度Ｔｓｅｔ１を１３０℃とした場合、この状態でＰＩＤ制御器６１の出力は１００％であった。
加熱対象物の乾燥を開始するために蒸気圧縮機３５を起動した。設定温度Ｔｓｅｔ１を１３０℃とし、蒸気圧縮機３５をインバータ６７のスロースタート機能を使って起動し、すぐに１００％運転となったが、第１圧力計３１の測定圧力Ｐ１が０．０４ＭＰａ・ＧになるとＰＩＤ制御器６２の出力が低下して４０％運転となった。
５時間経過後、温度計３３の測定値Ｔ１は１２８℃となり、ＰＩＤ制御器６１の出力値１が低下し２０％となり、蒸気圧縮機３５は２０％運転となった。
第１圧力計３１の測定値Ｐ１は０．０４ＭＰａ・Ｇから上昇を始め、０．１０ＭＰａ・Ｇとなり安定した。
蒸気圧縮機３５は、運転回転数がしだいに低下し、温度計３３の測定値Ｔ１が１３２℃となると、ＰＩＤ制御器６１の出力値１は０％となり蒸気圧縮機３５は停止した。
Example 1
The compressor 2 and the expander 5 of the heat pump circulation path 20 were operated so that the pressure of the first pressure gauge 31 became 0.10 MPa · G (120 ° C. saturated steam) using the heat pump steam generator shown in FIG. . The set pressure value P set1 of the first pressure gauge 31 was set to 0.04 MPa · G (110 ° C. saturated steam). In this state, the output of the PID controller 62 was 100%.
The steam utilization equipment 40 heating object was put and the temperature was measured with the thermometer 33. The measured value T1 of the thermometer 33 was 30 ° C. When the set temperature T set1 was 130 ° C., the output of the PID controller 61 was 100% in this state.
In order to start drying of the heating object, the vapor compressor 35 was started. The set temperature T set1 was set to 130 ° C., the steam compressor 35 was started using the slow start function of the inverter 67, and immediately started to operate at 100%, but the measured pressure P1 of the first pressure gauge 31 was 0.04 MPa · When it became G, the output of the PID controller 62 decreased and the operation became 40%.
After 5 hours, the measured value T1 of the thermometer 33 became 128 ° C., the output value 1 of the PID controller 61 decreased to 20%, and the steam compressor 35 was operated at 20%.
The measured value P1 of the first pressure gauge 31 started to increase from 0.04 MPa · G and became 0.10 MPa · G and stabilized.
The operation speed of the steam compressor 35 gradually decreased, and when the measured value T1 of the thermometer 33 reached 132 ° C., the output value 1 of the PID controller 61 became 0% and the steam compressor 35 stopped.
（実施例２）
図３に示すヒートポンプ式蒸気生成装置を使い、第１圧力計３１の圧力が０．１０ＭＰａ・Ｇ（１２０℃飽和蒸気）になるようにヒートポンプ循環経路２０の圧縮機２、膨張機５を運転した。第１圧力計３１の設定圧力値Ｐｓｅｔ１は、０．０４ＭＰａ・Ｇ（１１０℃飽和蒸気）に設定した。この状態で、ＰＩＤ制御器６２の出力は１００％であった。
蒸気利用設備４０加熱対象物を入れ、温度計３３にて温度を測定した。温度計３３の測定値Ｔ１は３０℃であった。また、圧力計３２にて、蒸気利用設備４０内に供給される雰囲気の圧力を測定した。蒸気圧縮機３５の起動前の圧力計３２の測定値Ｐ２は０ＭＰａ・Ｇであった。設定温度Ｔｓｅｔ１を１３０℃とした場合、この状態でＰＩＤ制御器６１の出力は１００％であった。ＰＩＤ制御器６３の設定値は、ＰＩＤ制御器６１の出力値１の０−１００％に対し、０〜０．２６ＭＰａ・Ｇ（１４０℃飽和蒸気）に割り付けた。
加熱対象物の乾燥を開始するために蒸気圧縮機３５を起動した。設定温度Ｔｓｅｔ１を１３０℃とし、蒸気圧縮機３５をインバータ６７のスロースタート機能を使って起動し、すぐに３８％運転となった。この時、圧力計３２の測定値Ｐ２は０．２６ＭＰａ・Ｇであり、ＰＩＤ制御器６３の出力値３は３８％であった。また、第１圧力計３１の測定圧力Ｐ１は０．０６ＭＰａ・Ｇであり、ＰＩＤ制御器６２の出力値２は１００％であった。
５時間経過後、温度計３３の測定値Ｔ１は１２８℃となり、ＰＩＤ制御器６１の出力値１が７３％に低下し、ＰＩＤ制御器６３の出力値３が２０％となり蒸気圧縮機３５は２０％運転となった。
第１圧力計３１の測定値Ｐ１は０．０６ＭＰａ・Ｇから上昇を始め、０．１０ＭＰａ・Ｇとなり安定した。
温度計３３の測定値Ｔ１が１３０℃となると、ＰＩＤ制御器６３の出力値３は０％となり蒸気圧縮機３５は停止した。
(Example 2)
The compressor 2 and the expander 5 of the heat pump circulation path 20 were operated so that the pressure of the first pressure gauge 31 became 0.10 MPa · G (120 ° C. saturated steam) using the heat pump steam generation device shown in FIG. . The set pressure value P set1 of the first pressure gauge 31 was set to 0.04 MPa · G (110 ° C. saturated steam). In this state, the output of the PID controller 62 was 100%.
The steam utilization equipment 40 heating object was put and the temperature was measured with the thermometer 33. The measured value T1 of the thermometer 33 was 30 ° C. Further, the pressure of the atmosphere supplied into the steam utilization facility 40 was measured with the pressure gauge 32. The measured value P2 of the pressure gauge 32 before starting the vapor compressor 35 was 0 MPa · G. When the set temperature T set1 was 130 ° C., the output of the PID controller 61 was 100% in this state. The set value of the PID controller 63 was assigned to 0 to 0.26 MPa · G (140 ° C. saturated steam) with respect to 0 to 100% of the output value 1 of the PID controller 61.
In order to start drying of the heating object, the vapor compressor 35 was started. The set temperature T set1 was set to 130 ° C., the steam compressor 35 was started using the slow start function of the inverter 67, and 38% operation was immediately started. At this time, the measured value P2 of the pressure gauge 32 was 0.26 MPa · G, and the output value 3 of the PID controller 63 was 38%. The measured pressure P1 of the first pressure gauge 31 was 0.06 MPa · G, and the output value 2 of the PID controller 62 was 100%.
After 5 hours, the measured value T1 of the thermometer 33 is 128 ° C., the output value 1 of the PID controller 61 is reduced to 73%, the output value 3 of the PID controller 63 is 20%, and the steam compressor 35 is 20%. % Driving.
The measured value P1 of the first pressure gauge 31 started to rise from 0.06 MPa · G and stabilized at 0.10 MPa · G.
When the measured value T1 of the thermometer 33 reached 130 ° C., the output value 3 of the PID controller 63 became 0%, and the steam compressor 35 was stopped.
（実施例３）
図５に示すヒートポンプ式蒸気生成装置を使い、第１圧力計３１の圧力が０．１０ＭＰａ・Ｇ（１２０℃飽和蒸気）になるようにヒートポンプ循環経路２０の圧縮機２、膨張機５を運転した。第１圧力計３１の設定圧力値Ｐｓｅｔ１は、０．０４ＭＰａ・Ｇ（１１０℃飽和蒸気）に設定した。この状態で、ＰＩＤ制御器６２の出力は１００％であった。
共通蒸気ヘッダー４１は、ボイラーからの蒸気とヒートポンプからの蒸気を集合・分配させる配管を備えており、圧力計３４の測定値Ｐ３は０．３７ＭＰａ・Ｇ（１５０℃飽和蒸気）であり、設定圧力値Ｐｓｅｔ２は０．４０ＭＰａ・Ｇとした。この状態でＰＩＤ制御器６４の出力は１００％であった。
蒸気圧縮機３５をインバータ６７のスロースタート機能を使って起動し、すぐに１００％運転となったが、第１圧力計３１の測定圧力Ｐ１が０．０４ＭＰａ・ＧになるとＰＩＤ制御器６２の出力が低下し、蒸気圧縮機３５は３０％で連続運転となった。
(Example 3)
The compressor 2 and the expander 5 of the heat pump circulation path 20 were operated so that the pressure of the first pressure gauge 31 became 0.10 MPa · G (120 ° C. saturated steam) using the heat pump steam generator shown in FIG. . The set pressure value P set1 of the first pressure gauge 31 was set to 0.04 MPa · G (110 ° C. saturated steam). In this state, the output of the PID controller 62 was 100%.
The common steam header 41 includes a pipe for collecting and distributing steam from the boiler and steam from the heat pump, and the measured value P3 of the pressure gauge 34 is 0.37 MPa · G (150 ° C. saturated steam). The value P set2 was 0.40 MPa · G. In this state, the output of the PID controller 64 was 100%.
The steam compressor 35 was started using the slow start function of the inverter 67 and immediately started to operate at 100%, but when the measured pressure P1 of the first pressure gauge 31 reached 0.04 MPa · G, the output of the PID controller 62 The steam compressor 35 was continuously operated at 30%.
１：排熱回収器
２：圧縮機
３：媒体凝縮器
５：膨張機
７：気液分離器
２０：ヒートポンプ循環経路
３１：第１圧力計
３２：第２圧力計
３３：温度計
３４：第３圧力計
３５：蒸気圧縮機
４０：蒸気利用設備
４１：共通蒸気ヘッダー
５０，５１，５２：制御装置
６１，６２，６３，６４：ＰＩＤ制御器
６５，６６：ローレベルセレクター
６７：インバータ
Ｌ１〜Ｌ６：配管
Ｐ１：供給ポンプ
1: exhaust heat recovery device 2: compressor 3: medium condenser 5: expander 7: gas-liquid separator 20: heat pump circulation path 31: first pressure gauge 32: second pressure gauge 33: thermometer 34: third Pressure gauge 35: Steam compressor 40: Steam utilization equipment 41: Common steam headers 50, 51, 52: Control devices 61, 62, 63, 64: PID controllers 65, 66: Low level selector 67: Inverters L1-L6: Piping P1: Supply pump
Claims (6)
前記媒体凝縮器に供給水を導入する給水経路と、
前記媒体凝縮器で生成した、温水及び蒸気の気液二相流を、水蒸気と水とに分離する気液分離器と、
前記気液分離器の気相部の蒸気を、蒸気利用設備に送る蒸気取出し経路と、
前記気液分離器の液相部と前記給水経路とを接続する水循環経路とを備えたヒートポンプ式蒸気生成装置であって、
前記蒸気取出し経路に上流側から第１圧力計と蒸気圧縮機とが設けられると共に、前記蒸気圧縮機の出力を制御する制御装置が設けられており、
前記制御装置は、前記蒸気利用設備における所定箇所の測定温度Ｔ１が、同箇所の設定温度Ｔｓｅｔ１に近づくように求められる出力値１と、前記第１圧力計の測定値Ｐ１が、気液分離器の設定圧力値Ｐｓｅｔ１に近づくように求められる出力値２とを比較して、低い方の出力値となるように、前記蒸気圧縮機の出力を制御することを特徴とするヒートポンプ式蒸気生成装置。 An exhaust heat recovery unit that recovers heat from an external heat source to heat the medium, a compressor that compresses the medium that has passed through the exhaust heat recovery unit, and transfers the heat of the medium compressed by the compressor to the water to be heated. A heat pump circulation path having a medium condenser that generates a gas-liquid two-phase flow of hot water and steam, and an expander that depressurizes the medium that has passed through the medium condenser to lower the temperature;
A water supply path for introducing supply water to the medium condenser;
A gas-liquid separator that separates the gas-liquid two-phase flow of hot water and steam generated by the medium condenser into water vapor and water;
A vapor extraction path for sending the vapor in the gas phase portion of the gas-liquid separator to a steam utilization facility;
A heat pump type steam generator comprising a water circulation path connecting the liquid phase part of the gas-liquid separator and the water supply path,
A first pressure gauge and a steam compressor are provided from the upstream side in the steam extraction path, and a control device for controlling the output of the steam compressor is provided,
The control device is configured such that an output value 1 obtained so that a measured temperature T1 at a predetermined location in the steam utilization facility approaches a set temperature Tset1 at the same location and a measured value P1 of the first pressure gauge are separated from each other. Heat pump steam generation, characterized in that the output of the steam compressor is controlled so as to be a lower output value by comparing with an output value 2 obtained so as to approach the set pressure value P set1 of the compressor apparatus.
前記出力値２は、前記第１圧力計の測定値Ｐ１と、前記設定圧力値Ｐｓｅｔ１とに基づいてＰＩＤ制御により求められる請求項１記載のヒートポンプ式蒸気生成装置。 The output value 1 is obtained by PID control based on a measured temperature T1 at a predetermined location in the steam utilization facility and a set temperature T set1 at the same location,
The heat pump steam generator according to claim 1, wherein the output value 2 is obtained by PID control based on a measured value P1 of the first pressure gauge and the set pressure value Pset1 .
前記媒体凝縮器に供給水を導入する給水経路と、
前記媒体凝縮器で生成した、温水及び蒸気の気液二相流を、水蒸気と水とに分離する気液分離器と、
前記気液分離器の気相部の蒸気を、蒸気利用設備に送る蒸気取出し経路と、
前記気液分離器の液相部と前記給水経路とを接続する水循環経路とを備えたヒートポンプ式蒸気生成装置であって、
前記蒸気取出し経路に上流側から第１圧力計と蒸気圧縮機と第２圧力計とが設けられると共に、前記蒸気圧縮機の出力を制御する制御装置が設けられており、
前記制御装置は、前記蒸気利用設備における所定箇所の測定温度Ｔ１が、同箇所の設定温度Ｔｓｅｔ１に近づくように求められる出力値１を設定値とし、第２圧力計の測定値Ｐ２が、前記出力値１に近づくように求められる出力値３と、
前記第１圧力計の測定値Ｐ１が、気液分離器の設定圧力値Ｐｓｅｔ１に近づくように求められる出力値２とを比較して、低い方の出力値となるように、前記蒸気圧縮機の出力を制御することを特徴とするヒートポンプ式蒸気生成装置。 An exhaust heat recovery unit that recovers heat from an external heat source to heat the medium, a compressor that compresses the medium that has passed through the exhaust heat recovery unit, and transfers the heat of the medium compressed by the compressor to the water to be heated. A heat pump circulation path having a medium condenser that generates a gas-liquid two-phase flow of hot water and steam, and an expander that depressurizes the medium that has passed through the medium condenser to lower the temperature;
A water supply path for introducing supply water to the medium condenser;
A gas-liquid separator that separates the gas-liquid two-phase flow of hot water and steam generated by the medium condenser into water vapor and water;
A vapor extraction path for sending the vapor in the gas phase portion of the gas-liquid separator to a steam utilization facility;
A heat pump type steam generator comprising a water circulation path connecting the liquid phase part of the gas-liquid separator and the water supply path,
A first pressure gauge, a steam compressor, and a second pressure gauge are provided from the upstream side in the steam extraction path, and a control device that controls the output of the steam compressor is provided,
The control device uses the output value 1 required so that the measured temperature T1 at a predetermined location in the steam utilization facility approaches the set temperature Tset1 at the same location, and the measured value P2 of the second pressure gauge is An output value 3 required to approach the output value 1, and
The steam compressor is configured such that the measured value P1 of the first pressure gauge becomes a lower output value by comparing with the output value 2 obtained so as to approach the set pressure value Pset1 of the gas-liquid separator. The heat pump type steam generator characterized by controlling the output.
前記出力値２は、前記第１圧力計の測定値Ｐ１と、前記設定圧力値Ｐｓｅｔ１とに基づいてＰＩＤ制御により求められ、
前記出力値３は、前記第２圧力計の測定値Ｐ２と、前記出力値１とに基づいてＰＩＤ制御により求められる請求項３記載のヒートポンプ式蒸気生成装置。 The output value 1 is obtained by PID control based on a measured temperature T1 at a predetermined location in the steam utilization facility and a set temperature T set1 at the same location,
The output value 2 is obtained by PID control based on the measured value P1 of the first pressure gauge and the set pressure value Pset1 .
The heat output steam generator according to claim 3, wherein the output value 3 is obtained by PID control based on the measured value P2 of the second pressure gauge and the output value 1.
前記媒体凝縮器に供給水を導入する給水経路と、
前記媒体凝縮器で生成した、温水及び蒸気の気液二相流を、水蒸気と水とに分離する気液分離器と、
前記気液分離器の気相部の蒸気を、蒸気利用設備に送る蒸気取出し経路と、
前記気液分離器の液相部と前記給水経路とを接続する水循環経路とを備えたヒートポンプ式蒸気生成装置であって、
前記蒸気取出し経路に上流側から第１圧力計と蒸気圧縮機とが設けられると共に、前記蒸気圧縮機の出力を制御する制御装置が設けられており、
前記制御装置は、前記蒸気利用設備における所定箇所の測定圧力Ｐ３が、同箇所の設定圧力Ｐｓｅｔ２に近づくように求められる出力値４と、前記第１圧力計の測定値Ｐ１が、気液分離器の設定圧力値Ｐｓｅｔ１に近づくように求められる出力値２とを比較して、低い方の出力値となるように、前記蒸気圧縮機の出力を制御することを特徴とするヒートポンプ式蒸気生成装置。 An exhaust heat recovery unit that recovers heat from an external heat source to heat the medium, a compressor that compresses the medium that has passed through the exhaust heat recovery unit, and transfers the heat of the medium compressed by the compressor to the water to be heated. A heat pump circulation path having a medium condenser that generates a gas-liquid two-phase flow of hot water and steam, and an expander that depressurizes the medium that has passed through the medium condenser to lower the temperature;
A water supply path for introducing supply water to the medium condenser;
A gas-liquid separator that separates the gas-liquid two-phase flow of hot water and steam generated by the medium condenser into water vapor and water;
A vapor extraction path for sending the vapor in the gas phase portion of the gas-liquid separator to a steam utilization facility;
A heat pump type steam generator comprising a water circulation path connecting the liquid phase part of the gas-liquid separator and the water supply path,
A first pressure gauge and a steam compressor are provided from the upstream side in the steam extraction path, and a control device for controlling the output of the steam compressor is provided,
In the control device, the measured pressure P3 at a predetermined location in the steam-using facility is determined so that the output value 4 required to approach the set pressure Pset2 at the same location and the measured value P1 of the first pressure gauge are gas-liquid separated. Heat pump steam generation, characterized in that the output of the steam compressor is controlled so as to be a lower output value by comparing with an output value 2 obtained so as to approach the set pressure value P set1 of the compressor apparatus.
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| WO2015068531A1 (en) * | 2013-11-08 | 2015-05-14 | 富士電機株式会社 | Steam-generating heat pump and method for controlling operation of steam-generating heat pump |
| KR101643844B1 (en) * | 2014-03-21 | 2016-07-28 | 주식회사 엘지화학 | Heat recovery apparatus |
| WO2016002878A1 (en) * | 2014-07-02 | 2016-01-07 | 富士電機株式会社 | Heat-pump-type steam-generating device |
| JP6528467B2 (en) * | 2015-03-04 | 2019-06-12 | 富士電機株式会社 | Heat pump type steam generating device and operating method of heat pump type steam generating device |
| JP6394472B2 (en) * | 2015-04-08 | 2018-09-26 | 富士電機株式会社 | Heat pump type steam generator and operation method of heat pump type steam generator |
| KR101839781B1 (en) | 2015-06-18 | 2018-03-20 | 주식회사 엘지화학 | Heat recovery apparatus |
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