JP6361021B2 - Hot water generator - Google Patents
Hot water generator Download PDFInfo
- Publication number
- JP6361021B2 JP6361021B2 JP2014123028A JP2014123028A JP6361021B2 JP 6361021 B2 JP6361021 B2 JP 6361021B2 JP 2014123028 A JP2014123028 A JP 2014123028A JP 2014123028 A JP2014123028 A JP 2014123028A JP 6361021 B2 JP6361021 B2 JP 6361021B2
- Authority
- JP
- Japan
- Prior art keywords
- temperature
- heat exchanger
- heat medium
- outlet temperature
- target
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Steam Or Hot-Water Central Heating Systems (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Description
本発明は、冷凍サイクルを利用した温水生成装置に関するものである。 The present invention relates to a hot water generator using a refrigeration cycle.
従来、この種の温水生成装置として、圧縮機１００、冷媒１０１と熱媒１０２との間で熱交換を行う利用側熱交換器１０３、膨張弁１０４、熱源側熱交換器１０５、が冷媒配管で環状に接続され、冷媒が循環する冷媒回路１０６と、利用側熱交換器１０３、放熱器１１０、容量可変型の循環ポンプ１０９が水配管で環状に接続され、水系熱媒が循環する熱媒回路１１１とを備えたものがある（例えば、特許文献１を参照）。 Conventionally, as this type of hot water generating device, a compressor 100, a use side heat exchanger 103 that performs heat exchange between the refrigerant 101 and the heat medium 102, an expansion valve 104, and a heat source side heat exchanger 105 are refrigerant pipes. A refrigerant circuit 106 that is connected in a ring and in which the refrigerant circulates, a heat exchanger circuit 103, a radiator 110, and a variable capacity circulation pump 109 that are connected in a ring through a water pipe, and a heat medium circuit in which an aqueous heat medium circulates 111 (see, for example, Patent Document 1).
図４は、特許文献１に記載された温水生成装置の概略図である。図４に示すように、熱媒回路１１１には、利用側熱交換器１０３の入口側の水系熱媒の温度を測定する入口温度センサ１０７と、利用側熱交換器１０３の出口側の水系熱媒の温度を測定する出口温度センサ１０８と、が設けられている。また、温水生成装置の制御装置（図示せず）は、出口温度センサ１０８で検出した温度Ｔ１が目標の第１目標温度Ｔｔとなるように圧縮機１００の周波数を制御し、また、出口温度センサ１０８で検出した温度Ｔ１と入口温度センサ１０７で検出した温度Ｔ２との温度差が目標の第２目標温度差ΔＴｔとなるように循環ポンプ１０９の搬送量を制御する。これにより、利用側熱交換器１０３の負荷が減少した場合でも、水系熱媒の過度な温度変化を防止しようとするものである。 FIG. 4 is a schematic diagram of the hot water generator described in Patent Document 1. As shown in FIG. 4, the heat medium circuit 111 includes an inlet temperature sensor 107 that measures the temperature of the aqueous heat medium on the inlet side of the use side heat exchanger 103, and the aqueous heat on the outlet side of the use side heat exchanger 103. And an outlet temperature sensor 108 for measuring the temperature of the medium. A control device (not shown) of the hot water generator controls the frequency of the compressor 100 so that the temperature T1 detected by the outlet temperature sensor 108 becomes the target first target temperature Tt, and the outlet temperature sensor. The conveyance amount of the circulation pump 109 is controlled so that the temperature difference between the temperature T1 detected at 108 and the temperature T2 detected by the inlet temperature sensor 107 becomes the target second target temperature difference ΔTt. Thereby, even when the load of the use side heat exchanger 103 decreases, an excessive temperature change of the aqueous heat medium is to be prevented.
前記従来の構成では、例えば、暖房負荷が安定していた状態から一部の部屋で暖房が不要になり、必要な暖房負荷が低下したような場合には、図５に示すように、出口温度センサ１０８で検出される温度Ｔ１と、入口温度センサ１０７で検出される温度Ｔ２とがともに上昇する。この場合、制御装置は、利用側熱交換器１０３の出口の温度Ｔ１が目標温度Ｔｔとなるように圧縮機１００の周波数Ｆｑが調整する。また、制御装置は、利用側熱交換器１０３の出口と入口との温度差ｄＴ（＝Ｔ１−Ｔ２）が目標温度差ｄＴｔとなるように、循環ポンプ１０９の搬送量Ｇｗを制御する。 In the conventional configuration, for example, in the case where heating is not necessary in some rooms from the state where the heating load is stable and the required heating load is reduced, as shown in FIG. Both the temperature T1 detected by the sensor 108 and the temperature T2 detected by the inlet temperature sensor 107 rise. In this case, the control device adjusts the frequency Fq of the compressor 100 so that the temperature T1 at the outlet of the use side heat exchanger 103 becomes the target temperature Tt. Further, the control device controls the conveyance amount Gw of the circulation pump 109 so that the temperature difference dT (= T1−T2) between the outlet and the inlet of the use side heat exchanger 103 becomes the target temperature difference dTt.
しかしながら、このようにすると、循環ポンプ１０９による循環量Ｇｗの増減によって、再び利用側熱交換器１０３の出口の温度Ｔ１が変化する。したがって、再び圧縮機１００の周波数Ｆｑが調整される。すなわち、循環ポンプ１０９による循環量Ｇｗの増減と、圧縮機１００の周波数の増減とが繰り返されて、熱媒回路を流れる水系熱媒の温度が収束しない場合があるという課題を有していた。 However, if it does in this way, the temperature T1 of the exit of the utilization side heat exchanger 103 will change again by the increase / decrease in the circulation amount Gw by the circulation pump 109. FIG. Therefore, the frequency Fq of the compressor 100 is adjusted again. That is, the increase / decrease in the circulation amount Gw by the circulation pump 109 and the increase / decrease in the frequency of the compressor 100 are repeated, and the temperature of the aqueous heat medium flowing through the heat medium circuit may not converge.
本発明は前記従来の課題を解決するためのもので、暖房負荷の変動によっても、熱媒回路を循環する水系熱媒の温度の変動を抑制する温水生成装置を提供することを目的とする。 This invention is for solving the said conventional subject, and it aims at providing the warm water production | generation apparatus which suppresses the fluctuation | variation of the temperature of the water-system heat medium which circulates through a heat-medium circuit also by the fluctuation | variation of a heating load.
前記従来の課題を解決するために、本発明の温水生成装置は、圧縮機、冷媒と熱媒との間で熱交換を行う利用側熱交換器、膨張手段、熱源側熱交換器、が冷媒配管で環状に接続されて構成されたヒートポンプサイクルと、前記熱媒を環状の熱媒回路の内部で循環させる循環ポンプと、前記利用側熱交換器の出口側の前記熱媒の温度を検出する出口温度検出手段と、前記利用側熱交換器の入口側の前記熱媒の温度を検出する入口温度検出手段と、制御装置と、を備え、前記制御装置は、前記出口温度検出手段で検出される出口温度と前記入口温度検出手段で検出される入口温度との平均温度が、前記平均温度の目標値よりも高いときに、前記圧縮機の周波数を低くし、前記制御装置は、前記出口温度が目標出口温度となるように、前記循環ポンプの搬送量を制御することを特徴とするものである。 In order to solve the above-described conventional problems, a hot water generator of the present invention includes a compressor, a use side heat exchanger that performs heat exchange between the refrigerant and the heat medium, an expansion unit, and a heat source side heat exchanger. A heat pump cycle configured to be annularly connected by piping, a circulation pump for circulating the heat medium inside the annular heat medium circuit, and a temperature of the heat medium on the outlet side of the use side heat exchanger are detected. An outlet temperature detection means, an inlet temperature detection means for detecting the temperature of the heat medium on the inlet side of the use side heat exchanger, and a control device, wherein the control device is detected by the outlet temperature detection means. When the average temperature of the outlet temperature detected by the inlet temperature detection means and the inlet temperature detected by the inlet temperature detection means is higher than the target value of the average temperature, the frequency of the compressor is lowered, and the control device So that the target outlet temperature becomes the target outlet temperature. It is characterized in that for controlling the conveyance amount.
これにより、循環ポンプによる循環量の増減と圧縮機の周波数の増減との干渉を抑制し、利用側熱交換器の出口の熱媒の温度の変動を抑制することができる。 Thereby, interference with the increase / decrease in the amount of circulation by the circulation pump and the increase / decrease in the frequency of a compressor can be suppressed, and the fluctuation | variation of the temperature of the heat medium of the exit of a utilization side heat exchanger can be suppressed.
本発明によれば、暖房負荷の変動によっても、水系熱媒の温度の変動を抑制することが可能な温水生成装置を提供することができる。 ADVANTAGE OF THE INVENTION According to this invention, the warm water production | generation apparatus which can suppress the fluctuation | variation of the temperature of an aqueous heating medium can be provided also by the fluctuation | variation of heating load.
第１の発明は、圧縮機、冷媒と熱媒との間で熱交換を行う利用側熱交換器、膨張手段、熱源側熱交換器、が冷媒配管で環状に接続されて構成されたヒートポンプサイクルと、前記熱媒を環状の熱媒回路の内部で循環させる循環ポンプと、前記利用側熱交換器の出口側の前記熱媒の温度を検出する出口温度検出手段と、前記利用側熱交換器の入口側の前記熱媒の温度を検出する入口温度検出手段と、制御装置と、を備え、前記制御装置は、前記出口温度検出手段で検出される出口温度と前記入口温度検出手段で検出される入口温度との平均温度が、前記平均温度の目標値よりも高いときに、前記圧縮機の周波数を低くし、前記制御装置は、前記出口温度が目標出口温度となるように、前記循環ポンプの搬送量を制御することを特徴とするものである。 1st invention is the heat pump cycle comprised by connecting the compressor, the utilization side heat exchanger which performs heat exchange between a refrigerant | coolant, and a heat medium, the expansion means, and the heat-source side heat exchanger by cyclic | annular connection with refrigerant | coolant piping. A circulation pump that circulates the heat medium inside the annular heat medium circuit, outlet temperature detection means for detecting the temperature of the heat medium on the outlet side of the use side heat exchanger, and the use side heat exchanger An inlet temperature detecting means for detecting the temperature of the heat medium on the inlet side of the inlet, and a control device, wherein the control device is detected by the outlet temperature detected by the outlet temperature detecting means and the inlet temperature detecting means. When the average temperature with respect to the inlet temperature is higher than the target value of the average temperature, the frequency of the compressor is lowered, and the control device is configured so that the outlet temperature becomes the target outlet temperature. It is characterized by controlling the transport amount of That.
これにより、例えば、暖房負荷が急激に低下した場合には、利用側熱交換器の出口温度および入口温度の双方が上昇するので、圧縮機の周波数が調整されて低くなり、また、循環ポンプの回転数（熱媒の循環量）が調整されて減少する。よって、利用側熱交換器の出口温度が過大となることを防止することができる。 Thereby, for example, when the heating load is suddenly decreased, both the outlet temperature and the inlet temperature of the use side heat exchanger are increased, so that the frequency of the compressor is adjusted to be low, and the circulation pump The rotational speed (circulation amount of the heat medium) is adjusted and decreased. Therefore, it is possible to prevent the outlet temperature of the use side heat exchanger from becoming excessive.
また、熱媒回路における熱媒の循環量が減少することで、続いて利用側熱交換器の入口温度が上昇するが、この場合には、入口温度と出口温度との平均温度が上昇するので、まず、圧縮機の周波数が調整されて低くなる。したがって、出口温度が目標出口温度よりも高くなることを抑制する。 In addition, since the amount of circulation of the heat medium in the heat medium circuit decreases, the inlet temperature of the use side heat exchanger subsequently increases, but in this case, the average temperature of the inlet temperature and the outlet temperature increases. First, the frequency of the compressor is adjusted and lowered. Accordingly, the outlet temperature is prevented from becoming higher than the target outlet temperature.
一方、循環ポンプの回転数は、出口温度が上昇するまでは変動しない。よって、循環ポンプによる循環量の増減と圧縮機の周波数の増減との干渉を抑制し、利用側熱交換器の出口の熱媒の温度の変動を抑制することができる。 On the other hand, the rotation speed of the circulation pump does not change until the outlet temperature rises. Therefore, it is possible to suppress the interference between the increase / decrease in the amount of circulation by the circulation pump and the increase / decrease in the frequency of the compressor, and to suppress fluctuations in the temperature of the heat medium at the outlet of the use side heat exchanger.
その結果、暖房負荷の変動によっても、水系熱媒の温度の変動を抑制することが可能な温水生成装置を提供することができる。 As a result, it is possible to provide a warm water generator that can suppress the temperature variation of the aqueous heat medium even when the heating load varies .
（実施の形態１）
図１は本実施の形態における温水生成装置の概略構成図である。図１に示すように、本実施の形態の温水生成装置は、気体状態の冷媒２を吸入して圧縮し、高温高圧の冷媒２を吐出する圧縮機１と、冷媒２と熱媒３との間で熱交換を行う利用側熱交換器４と、冷媒２の流量を調整する膨張手段５と、室外空気から採熱する熱源側熱交換器６が冷媒配管で環状に接続されて構成された冷媒回路９０を有するヒートポンプサイクル８を備えている。また、温水生成装置は、熱源側熱交換器６に空気を送風する送風ファン７を備えている。ヒートポンプサイクル８と送風ファン７とはヒートポンプ装置を構成する。
(Embodiment 1)
FIG. 1 is a schematic configuration diagram of a hot water generator in the present embodiment. As shown in FIG. 1, the hot water generating apparatus of the present embodiment includes a compressor 1 that sucks and compresses a gaseous refrigerant 2 and discharges a high-temperature and high-pressure refrigerant 2, and includes a refrigerant 2 and a heat medium 3. A heat exchanger 4 that performs heat exchange between the heat exchanger 4, an expansion means 5 that adjusts the flow rate of the refrigerant 2, and a heat source heat exchanger 6 that collects heat from the outdoor air are connected in a ring shape with a refrigerant pipe. A heat pump cycle 8 having a refrigerant circuit 90 is provided. The hot water generator includes a blower fan 7 for blowing air to the heat source side heat exchanger 6. The heat pump cycle 8 and the blower fan 7 constitute a heat pump device.
また、温水生成装置は、熱媒３を環状の熱媒回路１２で循環させる循環ポンプ９と、熱媒３の利用側熱交換器４の出口温度Ｔｗｏを検出する出口温度検出手段１０と、熱媒３の利用側熱交換器４の入口温度Ｔｗｉを検出する入口温度検出手段１１と、を備えている。 The hot water generator includes a circulation pump 9 that circulates the heat medium 3 through the annular heat medium circuit 12, an outlet temperature detection means 10 that detects an outlet temperature Two of the use-side heat exchanger 4 of the heat medium 3, and heat And an inlet temperature detecting means 11 for detecting the inlet temperature Twi of the utilization side heat exchanger 4 of the medium 3.
利用側熱交換器４は、熱媒配管によって放熱器２０と接続される。これにより、循環ポンプ９、利用側熱交換器４、放熱器２０が熱媒配管で環状に接続された熱媒回路１２が構成される。ここで、放熱器２０は、放熱器２０が配置される対象空間へ、熱媒３の熱を放熱するものである。 The use side heat exchanger 4 is connected to the radiator 20 by a heat medium pipe. Thereby, the heat medium circuit 12 in which the circulation pump 9, the use side heat exchanger 4, and the radiator 20 are annularly connected by the heat medium pipe is configured. Here, the radiator 20 radiates the heat of the heat medium 3 to the target space where the radiator 20 is disposed.
さらに、温水生成装置は、圧縮機１、膨張手段５、送風ファン７、循環ポンプ９等の制御を行う制御装置３０を備えている。 Furthermore, the hot water generator includes a control device 30 that controls the compressor 1, the expansion means 5, the blower fan 7, the circulation pump 9, and the like.
温水生成装置は、ヒートポンプサイクル８で加熱された冷媒２の熱を利用側熱交換器４で熱媒３に伝え、その熱を放熱器２０で対象空間に放熱することで冷暖房を行う。利用側熱交換器４には、小型かつ高効率で熱交換が可能なプレート熱交換器や二重管熱交換器を用いる。利用側熱交換器４は、冷媒２と熱媒３とが対向流となるように構成される。 The hot water generator transfers the heat of the refrigerant 2 heated in the heat pump cycle 8 to the heat medium 3 by the use side heat exchanger 4, and heats and cools the heat by radiating the heat to the target space by the radiator 20. As the use side heat exchanger 4, a plate heat exchanger or a double pipe heat exchanger capable of exchanging heat with small size and high efficiency is used. The use-side heat exchanger 4 is configured such that the refrigerant 2 and the heat medium 3 are opposed to each other.
循環ポンプ９としては、例えば、搬送量が多い渦巻きポンプを用いる。 As the circulation pump 9, for example, a spiral pump with a large conveyance amount is used.
制御装置３０は、ヒートポンプ装置の機能部品である圧縮機１、膨張手段５、送風ファン７を制御する第１制御部３０ａと、出口温度検出手段１０、入口温度検出手段１１の検出温度を取得し、循環ポンプ９の搬送量を制御する第２制御部３０ｂとを備えている。第１制御部３０ａと第２制御部３０ｂは通信線で繋がれている。第２制御部３０ｂで取得した温度等の情報は、通信線を介して第１制御部３０ａに送られる。また、第１制御部３０ａで取得したヒートポンプ装置の異常等の情報は通信線を介して第２制御部３０ｂに送られる。 The control device 30 acquires the detected temperatures of the first control unit 30a that controls the compressor 1, the expansion means 5, and the blower fan 7, which are functional parts of the heat pump device, the outlet temperature detection means 10, and the inlet temperature detection means 11. And a second control unit 30b for controlling the conveyance amount of the circulation pump 9. The first control unit 30a and the second control unit 30b are connected by a communication line. Information such as temperature acquired by the second control unit 30b is sent to the first control unit 30a via a communication line. Further, information such as abnormality of the heat pump device acquired by the first control unit 30a is sent to the second control unit 30b via the communication line.
温水生成装置は、圧縮機１、利用側熱交換器４、膨張手段５、熱源側熱交換器６、循環ポンプ９をひとつ筐体に収容して構成することができる。また、利用側熱交換器４、循環ポンプ９を、圧縮機１、利用側熱交換器４、膨張手段５と異なる筐体に収容して構成することができる。さらに、循環ポンプ９をヒートポンプ装置と異なる筐体に収容して構成することができる。 The hot water generator can be configured by housing the compressor 1, the use side heat exchanger 4, the expansion means 5, the heat source side heat exchanger 6, and the circulation pump 9 in one casing. Further, the use side heat exchanger 4 and the circulation pump 9 can be configured to be housed in a housing different from the compressor 1, the use side heat exchanger 4, and the expansion means 5. Furthermore, the circulation pump 9 can be accommodated in a housing different from the heat pump device.
放熱器２０には、床下に埋め込まれ、輻射暖房を行う床暖房パネル、室内の壁面近傍に設置され輻射暖房を行うラジエータ、送風機を用い放熱器２０の熱を強制対流させるファンコンベクタを用いることができる。 The radiator 20 may be a floor heating panel that is embedded under the floor and performs radiant heating, a radiator that is installed near the wall surface of the room and that performs radiant heating, and a fan convector that uses a blower to forcibly convection the heat of the radiator 20. it can.
以上のように構成された温水生成装置について、以下その動作、作用を説明する。図２は、本実施の形態における暖房運転時の制御動作のフローチャートである。 About the warm water production | generation apparatus comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. FIG. 2 is a flowchart of the control operation during the heating operation in the present embodiment.
図２において、ステップＳ１で制御装置３０がリモコン等のコントローラ（図示せず）から運転開始の信号を受け取ると、制御装置３０は初期運転の制御フローを開始する。初期運転において、制御装置３０は、熱媒３の利用側熱交換器４の出口温度Ｔｗｏの目標温度Ｔｗｏｔを設定する（ステップＳ２）。ここで、暖房運転の開始は、制御装置３０が、放熱器が配置された対象空間の温度や、利用側熱交換器４の入口温度の低下を認識し、自動的に開始することとしてもよい。また、初期運転は、熱源側熱交換器６の表面に付着した霜を融解させる除霜運転の終了後、続いて暖房運転を行う場合にも行われる。 In FIG. 2, when the control device 30 receives an operation start signal from a controller (not shown) such as a remote controller in step S1, the control device 30 starts an initial operation control flow. In the initial operation, the control device 30 sets a target temperature Two of the outlet temperature Two of the use side heat exchanger 4 of the heat medium 3 (step S2). Here, the start of the heating operation may be started automatically when the control device 30 recognizes the temperature of the target space in which the radiator is disposed and the decrease in the inlet temperature of the use side heat exchanger 4. . The initial operation is also performed when the heating operation is subsequently performed after the defrosting operation for melting the frost adhering to the surface of the heat source side heat exchanger 6 is completed.
次に、制御装置３０の第２制御部３０ｂは、ステップＳ３で、循環ポンプ９を所定の搬送量Ｇｗ１（初期搬送量）で運転する。また、第２制御部３０ｂは、熱媒３の利用側熱交換器４入口温度Ｔｗｉを検出する（ステップＳ４）。次に、制御装置３０の第１制御部３０ａは、ステップＳ５で、第２制御部３０ｂで取得した熱媒３の利用側熱交換器４の入口温度Ｔｗｉ、出口温度Ｔｗｏ、目標温度Ｔｗｏｔに基づき、圧縮機１の周波数Ｆｑ０（初期周波数）を決定する。第１制御部３０ａは、設定された初期周波数Ｆｑ０と目標温度Ｔｗｏｔとに基づいて、圧縮機１、膨張手段５、送風ファン７を制御する。 Next, the 2nd control part 30b of the control apparatus 30 operates the circulation pump 9 by predetermined | prescribed conveyance amount Gw1 (initial conveyance amount) by step S3. Moreover, the 2nd control part 30b detects the utilization side heat exchanger 4 inlet_port | entrance temperature Twi of the heat medium 3 (step S4). Next, the 1st control part 30a of the control apparatus 30 is based on the inlet temperature Twi of the utilization side heat exchanger 4 of the heat medium 3 acquired by the 2nd control part 30b, the exit temperature Two, and target temperature Two by step S5. The frequency Fq0 (initial frequency) of the compressor 1 is determined. The 1st control part 30a controls the compressor 1, the expansion means 5, and the ventilation fan 7 based on the set initial frequency Fq0 and target temperature Twot.
制御装置３０は、圧縮機１の初期周波数での運転を所定時間継続する（ステップ６）。制御装置３０は、所定時間が経過した後に、定常運転へと移行する。なお、本実施の形態では、定常運転の前に初期運転を行う期間を設けたが、初期運転の方法は本実施の形態の方法に特に限定されない。また、初期運転の方法によらず、定常運転を行えば、暖房負荷の変動に対応するという本発明の効果を発揮することができる。 The control device 30 continues the operation of the compressor 1 at the initial frequency for a predetermined time (step 6). The control device 30 shifts to a steady operation after a predetermined time has elapsed. In this embodiment, the period for performing the initial operation is provided before the steady operation, but the method of the initial operation is not particularly limited to the method of the present embodiment. Moreover, if the steady operation is performed regardless of the method of the initial operation, the effect of the present invention corresponding to the variation of the heating load can be exhibited.
制御装置３０は、ステップＳ７において、熱媒３の利用側熱交換器４の出口温度Ｔｗｏと目標温度Ｔｗｏｔとを比較する。 In step S7, the control device 30 compares the outlet temperature Two of the use side heat exchanger 4 of the heat medium 3 with the target temperature Twot.
ここで、熱媒３の利用側熱交換器４の出口温度Ｔｗｏが目標温度Ｔｗｏｔである場合には、ステップＳ８に進み、循環ポンプ９の搬送量Ｇｗを維持する。 Here, when the outlet temperature Two of the use side heat exchanger 4 of the heat medium 3 is the target temperature Twot, the process proceeds to step S8, and the conveyance amount Gw of the circulation pump 9 is maintained.
また、熱媒３の利用側熱交換器４の出口温度Ｔｗｏが目標温度Ｔｗｏｔより小さい場合は、ステップＳ９に進み、循環ポンプ９の搬送量Ｇｗを減少させる。また、熱媒３の利用側熱交換器４の出口温度Ｔｗｏが目標温度Ｔｗｏｔより大きい場合は、ステップＳ１０に進み、循環ポンプ９の搬送量Ｇｗを増加させる。これにより、熱媒３の利用側熱交換器４出口温度Ｔｗｏを目標温度Ｔｗｏｔに近づける。 On the other hand, when the outlet temperature Two of the use side heat exchanger 4 of the heat medium 3 is lower than the target temperature Twot, the process proceeds to step S9 and the transport amount Gw of the circulation pump 9 is decreased. On the other hand, when the outlet temperature Two of the use side heat exchanger 4 of the heat medium 3 is higher than the target temperature Twot, the process proceeds to step S10 and the conveyance amount Gw of the circulation pump 9 is increased. Thereby, the use side heat exchanger 4 outlet temperature Two of the heat medium 3 is brought close to the target temperature Two.
なお、ここで、ステップＳ７において、出口温度Ｔｗｏが目標温度Ｔｗｏｔと同一である場合にステップＳ８に進むこととしたが、所定値α（例えば、３Ｋ）を設けて、目標温度Ｔｗｏｔと出口温度Ｔｗｏとの温度差（絶対値）が所定値αの範囲内である場合には、ステップＳ８に進むこととしてもよい。このとき、（Ｔｗｏｔ−Ｔｗｏ）＜−αである場合にはステップＳ９に進み、（Ｔｗｏｔ−Ｔｗｏ）＞αである場合には、ステップＳ１０に進む。 Here, in step S7, when the outlet temperature Two is the same as the target temperature Two, the process proceeds to step S8. However, the predetermined value α (for example, 3K) is provided, and the target temperature Two and the outlet temperature Two are set. When the temperature difference (absolute value) is within the range of the predetermined value α, the process may proceed to step S8. At this time, if (Twot-Two) <-α, the process proceeds to step S9, and if (Twot-Two)> α, the process proceeds to step S10.
次に、制御装置３０は、ステップＳ１１で熱媒３の利用側熱交換器４の出口温度Ｔｗｏ及び入口温度Ｔｗｉの平均温度Ｔｗａと、目標平均温度Ｔｗａｔとを比較する。ここで。目標平均温度Ｔｗａｔは、目標温度Ｔｗｏｔと、目標温度Ｔｗｏｔよりも所定温度（例えば５Ｋ〜１５Ｋ）低い温度に設定される目標入水温度Ｔｗｉｔとの平均値である。 Next, the control device 30 compares the average temperature Twa of the outlet temperature Two and the inlet temperature Twi of the use side heat exchanger 4 of the heat medium 3 with the target average temperature Twat in step S11. here. The target average temperature Twat is an average value of the target temperature Twot and the target incoming water temperature Twit set to a temperature lower than the target temperature Two by a predetermined temperature (for example, 5K to 15K).
制御装置３０は、平均温度Ｔｗａが目標平均温度Ｔｗａｔと等しい場合は、放熱器２０が配置される対象空間での暖房負荷と、利用側熱交換器４における加熱量とが釣り合っていると判断し、ステップＳ１２に進む。制御装置３０は、ステップ１２において圧縮機１の周波数Ｆｑをそのまま維持する。 When the average temperature Twa is equal to the target average temperature Twat, the control device 30 determines that the heating load in the target space where the radiator 20 is disposed and the heating amount in the use side heat exchanger 4 are balanced. The process proceeds to step S12. In step 12, the control device 30 maintains the frequency Fq of the compressor 1 as it is.
一方、平均温度Ｔｗａが目標平均温度Ｔｗａｔより低い場合は、放熱器２０が配置された対象空間への暖房負荷が不足している判断して、ステップＳ１３に進む。制御装置３０は、ステップＳ１３において、圧縮機１の周波数Ｆｑが初期周波数Ｆｑ０もしくは初期周波数以上である場合には、周波数を維持する。一方、制御装置３０は、圧縮機１の周波数が初期周波数Ｆｑ０よりも小さい場合には、周波数を増加させる。 On the other hand, when average temperature Twa is lower than target average temperature Twat, it judges that the heating load to the object space where radiator 20 is arranged is insufficient, and progresses to Step S13. In step S13, the control device 30 maintains the frequency when the frequency Fq of the compressor 1 is equal to or higher than the initial frequency Fq0. On the other hand, when the frequency of the compressor 1 is smaller than the initial frequency Fq0, the control device 30 increases the frequency.
また、制御装置３０は、平均温度Ｔｗａが目標平均温度Ｔｗａｔより高い場合は、放熱器２０が放熱する対象空間への暖房負荷が過剰であると判断して、ステップＳ１４に進む。制御装置３０は、ステップ１４において、圧縮機１の周波数Ｆｑを低下させる。 In addition, when the average temperature Twa is higher than the target average temperature Twat, the control device 30 determines that the heating load on the target space to which the radiator 20 radiates heat is excessive, and proceeds to step S14. In step 14, the control device 30 decreases the frequency Fq of the compressor 1.
なお、ここで、ステップ１１において、平均温度Ｔｗａが目標平均温度Ｔｗａｔと同一である場合にステップ１２に進むこととしたが、所定値β（例えば、３Ｋ）を設けて、平気温度Ｔｗａと平均目標温度Ｔｗａｔとの温度差（絶対値）が所定値βの範囲内である場合には、ステップＳ１２に進むこととしてもよい。このとき、（Ｔｗａｔ−Ｔｗａ）＜−βである場合には、ステップ１３に進み、（Ｔｗａｔ−Ｔｗａ）＞βである場合には、ステップ１４に進む。定常運転の制御動作は、暖房運転の停止がリモコン等から指示された場合や、熱媒回路１２を循環する熱媒３が所定温度以上となった場合等に停止される。 Here, in step 11, when the average temperature Twa is the same as the target average temperature Twat, the process proceeds to step 12. However, the predetermined value β (for example, 3K) is provided, and the flat air temperature Twa and the average target are set. When the temperature difference (absolute value) from the temperature Twat is within the range of the predetermined value β, the process may proceed to step S12. At this time, if (Twat−Twa) <− β, the process proceeds to step 13, and if (Twat−Twa)> β, the process proceeds to step 14. The control operation of the steady operation is stopped when the stop of the heating operation is instructed from a remote controller or the like, or when the heat medium 3 circulating in the heat medium circuit 12 reaches a predetermined temperature or higher.
このような制御動作を行うと、利用側熱交換器４の出口温度Ｔｗｏが変化した場合に循環ポンプ９の搬送量Ｇｗによって出口温度Ｔｗｏを調整しても、必要な暖房負荷が変動しない場合は放熱量も変動しない。したがって、出口温度Ｔｗｏと入口温度Ｔｗｉとの平均温度Ｔｗａは変化せず、圧縮機１の周波数Ｆｑは変化しない。 When such a control operation is performed, when the outlet temperature Two of the use-side heat exchanger 4 changes, even if the outlet temperature Two is adjusted by the transport amount Gw of the circulation pump 9, the required heating load does not fluctuate. The amount of heat dissipation does not change. Therefore, the average temperature Twa between the outlet temperature Two and the inlet temperature Twi does not change, and the frequency Fq of the compressor 1 does not change.
そのため、例えば、対象空間で暖房が不要となり、暖房負荷が低下して、平均温度Ｔｗａが高くなった場合には、図３に示すように、暖房負荷に合った平均温度Ｔｗａとなるように圧縮機１の周波数Ｆｑを低下させる。また、圧縮機１の周波数Ｆｑが調整されたことにより、出口温度Ｔｗｏが変動しても、平均温度Ｔｗａによって制御される圧縮機１の周波数Ｆｑに干渉することなく循環ポンプ９の搬送量Ｇｗを減少させる。これによって、熱媒３の出口温度Ｔｗｏを目標温度Ｔｗｏｔに戻す。 Therefore, for example, when heating is not required in the target space, the heating load is reduced, and the average temperature Twa is high, compression is performed so that the average temperature Twa matches the heating load as shown in FIG. The frequency Fq of the machine 1 is reduced. Further, by adjusting the frequency Fq of the compressor 1, even if the outlet temperature Two varies, the conveyance amount Gw of the circulation pump 9 can be reduced without interfering with the frequency Fq of the compressor 1 controlled by the average temperature Twa. Decrease. Thereby, the outlet temperature Two of the heat medium 3 is returned to the target temperature Twot.
以上のように、本実施の形態では、出口温度Ｔｗｏと、入口温度Ｔｗｉとの平均温度Ｔｗａが低い時よりも高いときに、圧縮機１の周波数Ｆｑを低くする。また、出口温度Ｔｗｏが目標出口温度Ｔｗｏｔとなるように、循環ポンプ９の搬送量Ｇｗを調整する。これにより、出口温度Ｔｗｏが変化すると循環ポンプ９の搬送量Ｇｗにより調整するが、暖房負荷が変動しない場合には放熱量も変動しないので、平均温度Ｔｗａは変化せず、圧縮機１の周波数Ｆｑは変化しない。 As described above, in the present embodiment, when the average temperature Twa of the outlet temperature Two and the inlet temperature Twi is higher than when it is low, the frequency Fq of the compressor 1 is lowered. Further, the conveyance amount Gw of the circulation pump 9 is adjusted so that the outlet temperature Two becomes the target outlet temperature Twot. As a result, when the outlet temperature Two changes, the adjustment is made based on the conveyance amount Gw of the circulation pump 9. However, when the heating load does not change, the heat radiation amount does not change, so the average temperature Twa does not change, and the frequency Fq of the compressor 1 Does not change.
したがって、暖房負荷の変動によって平均温度Ｔｗａが高くなった場合でも、暖房負荷に合った圧縮機１の周波数Ｆｑに調整される。また、圧縮機１の周波数Ｆｑが調整されたことに起因する出口温度Ｔｗｏの変動を、圧縮機１の周波数Ｆｑに干渉することなく循環ポンプ９の搬送量Ｇｗによって調整する。 Therefore, even when the average temperature Twa is increased due to fluctuations in the heating load, the frequency Fq of the compressor 1 that matches the heating load is adjusted. Moreover, the fluctuation | variation of the exit temperature Two resulting from adjusting the frequency Fq of the compressor 1 is adjusted with the conveyance amount Gw of the circulation pump 9 without interfering with the frequency Fq of the compressor 1. FIG.
よって、熱源の能力が暖房負荷に合った所定の範囲に調整される。さらに、暖房負荷の変動に対応して熱源の能力が変化しても、出口温度Ｔｗｏを目標出口温度Ｔｗｏｔに安定させることができる。 Therefore, the capacity of the heat source is adjusted to a predetermined range that matches the heating load. Furthermore, even if the capacity of the heat source changes in response to a change in the heating load, the outlet temperature Two can be stabilized at the target outlet temperature Twot.
なお、初期運転において、出口温度Ｔｗｏが目標出口温度Ｔｗｏｔとなるまでの間、入口温度Ｔｗｉが低い時よりも高い時、すなわち、平均温度Ｔｗａが低い時よりも高い時に、圧縮機１の周波数Ｆｑを高くしてもよい。これにより、入口温度Ｔｗｉが高くなって、利用側熱交換器４における冷媒２のエンタルピー差が小さくなって場合でも、加熱能力の低下を抑制して、目標出口温度Ｔｗｏｔの湯水をより早く生成でき、またそれを維持することができる。 In the initial operation, until the outlet temperature Two reaches the target outlet temperature Two, when the inlet temperature Twi is higher than when it is low, that is, when the average temperature Twa is higher than when it is low, the frequency Fq of the compressor 1 May be raised. Thereby, even when the inlet temperature Twi becomes high and the enthalpy difference of the refrigerant 2 in the use side heat exchanger 4 becomes small, it is possible to generate hot water with the target outlet temperature Twot more quickly by suppressing a decrease in heating capacity. Can also maintain it.
その結果、除霜運転からの復帰等で出口温度Ｔｗｏが下がり切った場合でも、出口温度Ｔｗｏが目標出口温度Ｔｗｏｔに到達するまでの時間（復帰時間）を短縮し、使用者の快適性を向上させることができる。 As a result, even when the outlet temperature Two has fallen due to the return from the defrosting operation, etc., the time until the outlet temperature Two reaches the target outlet temperature Two (return time) is shortened, and the user's comfort is improved. Can be made.
以上のように、本発明にかかる温水生成装置は、暖房負荷の変動があった場合でも圧縮機と循環ポンプの制御が干渉せず、制御の安定性を向上することができるもので、ヒートポンプ式温水暖房機や温水循環加熱装置、チラー等の用途に適用できる。 As described above, the hot water generating device according to the present invention can improve the stability of the control without interfering with the control of the compressor and the circulation pump even when the heating load fluctuates. It can be applied to applications such as hot water heaters, hot water circulation heating devices, and chillers.
１ 圧縮機
４ 利用側熱交換器
５ 膨張手段
６ 熱源側熱交換器
８ ヒートポンプサイクル
９ 循環ポンプ
１０ 出口温度検出手段
１１ 入口温度検出手段
１２ 熱媒回路
３０ 制御装置
DESCRIPTION OF SYMBOLS 1 Compressor 4 Use side heat exchanger 5 Expansion means 6 Heat source side heat exchanger 8 Heat pump cycle 9 Circulation pump 10 Outlet temperature detection means 11 Inlet temperature detection means 12 Heat medium circuit 30 Controller
Claims (1)
前記熱媒を環状の熱媒回路の内部で循環させる循環ポンプと、
前記利用側熱交換器の出口側の前記熱媒の温度を検出する出口温度検出手段と、
前記利用側熱交換器の入口側の前記熱媒の温度を検出する入口温度検出手段と、
制御装置と、を備え、
前記制御装置は、前記出口温度検出手段で検出される出口温度と前記入口温度検出手段で検出される入口温度との平均温度が、前記平均温度の目標値よりも高いときに、前記圧縮機の周波数を低くし、
前記制御装置は、前記出口温度が目標出口温度となるように、前記循環ポンプの搬送量を制御することを特徴とする温水生成装置。 A heat pump cycle configured by connecting a compressor, a use side heat exchanger for exchanging heat between the refrigerant and the heat medium, an expansion means, a heat source side heat exchanger, and an annular connection with a refrigerant pipe;
A circulation pump for circulating the heat medium inside an annular heat medium circuit;
Outlet temperature detection means for detecting the temperature of the heat medium on the outlet side of the use side heat exchanger;
Inlet temperature detection means for detecting the temperature of the heat medium on the inlet side of the use side heat exchanger;
A control device,
When the average temperature of the outlet temperature detected by the outlet temperature detecting means and the inlet temperature detected by the inlet temperature detecting means is higher than the target value of the average temperature, the control device Lower the frequency,
The said control apparatus controls the conveyance amount of the said circulation pump so that the said outlet temperature may turn into target outlet temperature, The hot water production | generation apparatus characterized by the above-mentioned.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014123028A JP6361021B2 (en) | 2014-06-16 | 2014-06-16 | Hot water generator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014123028A JP6361021B2 (en) | 2014-06-16 | 2014-06-16 | Hot water generator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2016003789A JP2016003789A (en) | 2016-01-12 |
| JP6361021B2 true JP6361021B2 (en) | 2018-07-25 |
Family
ID=55223190
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2014123028A Expired - Fee Related JP6361021B2 (en) | 2014-06-16 | 2014-06-16 | Hot water generator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP6361021B2 (en) |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007093100A (en) * | 2005-09-28 | 2007-04-12 | Mitsubishi Electric Corp | Control method of heat pump water heater, and heat pump water heater |
| JP2010196946A (en) * | 2009-02-24 | 2010-09-09 | Daikin Ind Ltd | Heat pump system |
| JP5058324B2 (en) * | 2010-10-14 | 2012-10-24 | 三菱電機株式会社 | Refrigeration cycle equipment |
| JP2012233605A (en) * | 2011-04-28 | 2012-11-29 | Mitsubishi Electric Corp | Liquid circulation heating system |
| EP2789933B1 (en) * | 2011-12-06 | 2016-11-23 | Mitsubishi Electric Corporation | Heat pump type heating/hot-water supply system |
| JP2014005961A (en) * | 2012-06-22 | 2014-01-16 | Panasonic Corp | Refrigeration cycle device and hot water generator including the same |
-
2014
- 2014-06-16 JP JP2014123028A patent/JP6361021B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP2016003789A (en) | 2016-01-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US10641516B2 (en) | Method and apparatus for reheat dehumidification with variable air volume | |
| US10753664B2 (en) | Method and apparatus for reheat dehumidification with variable speed outdoor fan | |
| JP5524571B2 (en) | Heat pump equipment | |
| JP5838363B2 (en) | Heat medium circulation heat pump heater | |
| JP5452581B2 (en) | HEAT PUMP SYSTEM AND HEAT PUMP DEVICE CONTROL METHOD | |
| JP2013108720A (en) | Refrigeration cycle device and hot water producing device with the same | |
| EP2508806B1 (en) | Heat pump system and heat pump unit controlling method | |
| EP2857761B1 (en) | Water heater | |
| JP2016053452A (en) | Air conditioner | |
| JP2012233605A (en) | Liquid circulation heating system | |
| JP5973076B2 (en) | Hot water heater | |
| JP6570766B2 (en) | Heating control system and heat pump hot water supply heating system | |
| JP6912349B2 (en) | Temperature control system | |
| JPWO2015194038A1 (en) | Heat pump heating system | |
| JP6685418B2 (en) | Air conditioning system, air conditioning controller, air conditioning method and program | |
| JP2017067321A (en) | Heat pump control device, hot water supply unit of heat pump-type heating system, heat pump-type heating system, and method executed by heat pump control device | |
| JP6361021B2 (en) | Hot water generator | |
| JPWO2018042515A1 (en) | Air conditioner | |
| JPWO2017138133A1 (en) | Hot / cold water air conditioning system | |
| JP6890727B1 (en) | Air conditioning system and control method | |
| JP6423651B2 (en) | Water heater | |
| JP2011237111A (en) | Heat pump hot water heating apparatus | |
| JP5818601B2 (en) | Heat pump heat source machine | |
| JP2019132464A (en) | Heating system | |
| JP2022155001A (en) | air conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| RD01 | Notification of change of attorney |
Free format text: JAPANESE INTERMEDIATE CODE: A7421 Effective date: 20160520 |
|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20170206 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20171122 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20171219 |
|
| A521 | Request for written amendment filed |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20171220 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20180515 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20180528 |
|
| R151 | Written notification of patent or utility model registration |
Ref document number: 6361021 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R151 |
|
| LAPS | Cancellation because of no payment of annual fees |