JP2011027358A - Heater - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heater preventing liquid compression while enabling cooling treatment of an intermediate temperature liquid. <P>SOLUTION: The heater 100 includes a heat pump 101 and a hot water storage tank 102. The heat pump 101 has: a refrigerant circuit 117 including a compression means constituted of a first compression mechanism 108 and a second compression mechanism 113, a radiator 105, an expansion mechanism 109, a gas-liquid separator 106 and an evaporator 107; and a gas phase refrigerant flowing passage 118. An intermediate temperature water flowing passage 126 is connected to the hot water storage tank 102, and a heat exchanger 119 is provided astride the gas phase refrigerant flowing passage 118 and the intermediate temperature water flowing passage 126. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a heating device including a heat pump and a tank.

  2. Description of the Related Art Conventionally, there is known a heating apparatus that stores heated liquid generated by a heat pump in a tank and uses the heated liquid for heating. For example, Patent Literature 1 discloses a hot water supply device 1 that also serves as a heating device, as shown in FIG.

  A water heater 1 shown in FIG. 4 includes a heat pump 3 and a hot water storage tank 2. The heat pump 3 includes a compression mechanism 4, a radiator 5, an expansion valve 6, a refrigerant circuit 30 in which a main evaporator 7 and a sub-evaporator 8 are sequentially connected by piping, and a bypass path 9 that bypasses the sub-evaporator 8. A bypass valve 10 is provided in the bypass passage 9, and an electromagnetic valve 11 is provided between a position where the bypass passage 9 of the refrigerant circuit 30 branches and the sub-evaporator 8.

  The hot water storage tank 2 is connected to the radiator 5 by an extraction pipe 12 and a return pipe 13. The extraction pipe 12 is provided with a pump 18, and when this pump 18 is operated, water extracted from the lower part of the hot water storage tank 2 is sent to the radiator 5, where it is heated to become a heated liquid. It is returned to the upper part of the hot water storage tank 2. A hot water supply pipe 14 is connected to the lower part of the hot water storage tank 2, and a hot water supply pipe 15 is connected to the upper part of the hot water storage tank 2.

  A use side circuit 16 is connected to the hot water storage tank 2. The use-side circuit 16 includes a hot water passage 17 having an upstream end connected to the upper portion of the hot water storage tank 2 and a downstream end connected to the lower portion of the hot water storage tank 2, a circulating water circuit 19 including a heating radiator 25, and a hot water storage tank. 2 and an intermediate heat exchanger 20 that exchanges heat between the high-temperature water flowing into the hot water channel 17 and the water circulating in the circulating water circuit 19.

  Further, the hot water storage tank 2 is connected with a cooling path 22 via the sub-evaporator 8. The sub-evaporator 8 is a so-called plate heat exchanger, and the cooling path 22 includes an upstream pipe 22 a that connects the lower side surface of the hot water storage tank 2 and the secondary side inlet of the sub-evaporator 8, and the sub-evaporator 8. A downstream pipe 22b that connects the secondary side outlet and the lower bottom surface of the hot water storage tank 2 is provided. The downstream pipe 22b is provided with a pump 23. When this pump 23 is operated, heat exchange is performed between the water extracted from the lower part of the hot water storage tank 2 in the sub-evaporator 8 and the refrigerant circulating in the refrigerant circuit 30. Is done.

  When the heating target in the heating radiator 25 has a relatively low load, the amount of heat released in the heating radiator 25 for the circulating water is small, so that the intermediate heat exchanger 20 changes the hot water from the hot water 17 to the circulating water. Less heat is transferred. The high-temperature water that has not been sufficiently cooled flows into the lower part of the hot water storage tank 2 as intermediate temperature water with little temperature drop, and the intermediate hot water is stored in the lower part of the hot water storage tank 2. When such medium temperature water is supplied to the radiator 5, the COP of the heat pump 3 is lowered. Therefore, in the hot water supply apparatus 1, the evaporator is divided into the main evaporator 7 and the sub-evaporator 8, and the sub-evaporator 8 absorbs the heat of the intermediate-temperature water in the refrigerant so that the intermediate-temperature water is cooled. In other words, the refrigerant is evaporated using the heat of the medium temperature water.

JP 2007-10207 A

  However, like the hot water supply apparatus 1 shown in FIG. 4, the main evaporator 7 performs the first half of the refrigerant evaporation process, and the sub-evaporator 8 performs the second half of the refrigerant evaporation process using the heat of intermediate temperature water. In such a configuration, when the medium temperature water is not stored in the lower part of the hot water storage tank 2, the entire amount of the refrigerant cannot be evaporated, and the refrigerant in the gas-liquid two-phase state is sucked into the compression mechanism 4. Become. Then, since the liquid compression is performed in the compression mechanism 4, the reliability of the compression mechanism 4 and the stability of the refrigeration cycle are lowered.

  In view of such circumstances, an object of the present invention is to provide a heating device that can prevent liquid compression while allowing cooling of an intermediate temperature liquid.

  The heating device according to the present invention includes a compression unit that compresses the refrigerant, a radiator that radiates the refrigerant compressed by the compression unit, an expansion unit that expands the refrigerant radiated by the radiator, and a refrigerant expanded by the expansion unit. A gas-liquid separator that separates a gas-phase refrigerant and a liquid-phase refrigerant, and an evaporator that evaporates the liquid-phase refrigerant separated by the gas-liquid separator, and a gas phase separated by the gas-liquid separator A gas-phase refrigerant flow path for introducing a refrigerant to a portion between the evaporator and the compression means in the refrigerant circuit, and a tank returned to the upper part after the liquid extracted from the lower part is heated by the radiator A heater for dissipating the heated liquid stored in the tank; and an intermediate temperature liquid for flowing the intermediate temperature liquid in the tank caused by a temperature drop of the heated liquid, the upstream end and the downstream end of which are connected to the tank A flow passage, A heat exchanger for cooling the medium-temperature liquid by the gas-phase refrigerant flowing through the Kikisho refrigerant flow passage through the medium-temperature fluid channel, characterized in that it comprises a.

  According to the above configuration, the gas-liquid separator is provided on the upstream side of the evaporator, and the intermediate temperature liquid generated in the tank is cooled by the gas-phase refrigerant separated by the gas-liquid separator. Then, the liquid refrigerant can be reliably evaporated regardless of the presence or absence of the medium temperature liquid. The refrigerant evaporated in the evaporator is combined with the gas-phase refrigerant separated by the gas-liquid separator and then sucked into the compression means, so that only the gas-phase refrigerant can be sucked into the compression means. Therefore, according to the present invention, liquid compression can be prevented while enabling the cooling process of the medium temperature liquid, and the reliability of the compression means and the stability of the refrigeration cycle can be improved.

The block diagram of the heating apparatus which concerns on 1st Embodiment of this invention. (A) is a Mollier diagram of the heat pump when the intermediate temperature water cooling operation is executed, and (b) is a Mollier diagram of the heat pump when the intermediate temperature water cooling operation is not executed. The block diagram of the heating apparatus which concerns on 2nd Embodiment of this invention. Configuration diagram of conventional hot water supply equipment

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited by the following embodiment.

(First embodiment)
In FIG. 1, the heating apparatus 100 which concerns on 1st Embodiment of this invention is shown. This heating apparatus 100 heats a liquid, produces | generates a heating liquid, and heats using the heating liquid. In this embodiment, water is used as the liquid that is the heat medium. However, the liquid of the present invention is not necessarily limited to this. For example, as the liquid, it is possible to use an antifreeze liquid in which propylene glycol or the like is mixed in water, or oil. In the following description, it is assumed that the liquid is water and the heated liquid is hot water.

[Configuration of Heating Device 100]
The heating device 100 includes a heat pump 101 and a hot water storage tank 102.

  The heat pump 101 includes an expander-integrated compressor 103, a second compressor 104, a radiator 105, a gas-liquid separator 106, and an evaporator 107. The expander-integrated compressor 103 includes a first sealed container 112 that is connected to each other by a first rotating shaft 111 and that houses a first compression mechanism 108, an expansion mechanism 109, and a first motor 110. The second compressor 104 has a second sealed container 116 that houses a second compression mechanism 113 and a second motor 114 that are connected to each other by a second shaft 115.

  The first compression mechanism 108 (corresponding to the compression mechanism of the present invention), the radiator 105, the expansion mechanism 109, the gas-liquid separator 106, and the evaporator 107 are sequentially connected by piping. The second compression mechanism 113 (corresponding to the second compression mechanism of the present invention) is connected in parallel with the first compression mechanism 108 by a pipe. And these equipment and piping comprise the refrigerant circuit 117 which circulates a refrigerant | coolant. In the present embodiment, carbon dioxide is used as the refrigerant.

  The radiator 105 is for generating heat by exchanging heat between the refrigerant and the water supplied from the hot water storage tank 102, and has a refrigerant side channel 105a and a water side channel 105b. Yes. A first compression mechanism 108 and a second compression mechanism 113 are connected to one end of the refrigerant side flow path 105a via a pipe or the like, and an expansion mechanism 109 is connected to the other end of the refrigerant side flow path 105a via the pipe. Connected.

  The heat pump 101 also includes a gas-phase refrigerant flow passage 118. One end of the gas-phase refrigerant flow path 118 is connected to the gas-phase portion of the gas-liquid separator 106, and the other end is connected to a pipe connecting the evaporator 107, the first compression mechanism 108, and the second compression mechanism 113. Yes. The gas-phase refrigerant separated by the gas-liquid separator 106 is guided to a pipe connecting the evaporator 107 with the first compression mechanism 108 and the second compression mechanism 113 through the gas-phase refrigerant flow passage 118. The liquid phase refrigerant separated by the gas-liquid separator 106 is sent to the evaporator 107 along the refrigerant circuit 117.

  The hot water storage tank 102 is connected to the radiator 105 by the forward pipe 120 and the return pipe 121. A water supply pipe 122 is connected to the lower part of the hot water storage tank 102.

  Specifically, an outlet 120 a is provided on the bottom surface of the hot water storage tank 102 and a return port 121 a is provided on the upper side surface of the hot water storage tank 102. One end of the forward tube 120 is connected to the forward port 120 a, and the other end of the forward tube 120 is connected to one end of the water-side channel 105 b of the radiator 105. Further, the forward pipe 120 is provided with a first pump 124 in the vicinity of the forward opening 120a. On the other hand, one end of the return pipe 121 is connected to the return port 121a, and the other end of the return pipe 121 is connected to the other end of the water-side flow path 105b of the radiator 105. When the first pump 124 is operated, the water extracted from the lower part of the hot water storage tank 102 is sent to the radiator 105, where it is heated to be a heated liquid and then returned to the upper part of the hot water storage tank 102.

  In addition, a heating path 123 is connected to the hot water storage tank 102. The heating path 123 includes a hot water outlet 123a provided on the upper side surface of the hot water storage tank 102, a heater 123b such as a radiator, and a hot water return port 123c provided on the intermediate side surface of the hot water storage tank 102 in order by piping. Connected and configured. The heating path 123 is provided with a second pump 125. The second pump 125 is arranged on the upstream side of the heater 123b in the illustrated example, but may be arranged on the downstream side of the heater 123b.

  Here, the upper part of the hot water storage tank 102 means a portion of the upper third of the hot water storage tank 102 in the vertical direction to about one fifth, and the lower part of the hot water storage tank 102 means the lower part of the hot water storage tank 102 in the vertical direction. A side portion of about 1/3 to 1/5 is referred to, and an intermediate portion of the hot water storage tank 102 is a portion between them.

  In this embodiment, the hot water return port 123 c is provided on the side surface of the intermediate portion of the hot water storage tank 102, but the hot water return port 123 c may be provided in the lower part of the hot water storage tank 102. Or the hot water return port 123c is provided in both the intermediate part and the lower part of the hot water storage tank 102, and it is selected according to the temperature of the warm water flowing out from the heater 123b to which direction the warm water is returned. It may be.

  Further, in the present embodiment, an intermediate temperature water flow passage 126 is connected to the hot water storage tank 102, and a heat exchanger 119 is provided across the intermediate temperature water flow passage 126 and the gas-phase refrigerant flow passage 118 described above. . The intermediate temperature water flow passage 126 is for flowing intermediate temperature water in the hot water storage tank 102 caused by the temperature drop of the hot water, and the heat exchanger 119 is driven by the gas phase refrigerant flowing in the gas phase refrigerant passage 118. It is for cooling the intermediate temperature water flowing through.

  Here, the medium temperature water is water having a temperature (for example, about 30 to 65 ° C.) that is higher than the outside air temperature but insufficient for heating as it is. For example, when R410A is used as the refrigerant, the temperature of the medium temperature water is about 30 to 40 ° C.

  The upstream end of the intermediate temperature water passage 126 is connected to a water supply port 126 a provided on the side surface of the hot water storage tank 102, and the downstream end is connected to a condensate port 126 b provided on the lower side surface of the hot water storage tank 102. ing. However, the water supply port 126 a may be provided in the lower part of the hot water storage tank 102. Alternatively, a plurality of water supply ports 126 a are provided in the vertical direction from the middle part to the lower part of the hot water storage tank 102, and the upstream end of the intermediate temperature water flow passage 126 is also branched into a plurality of branches corresponding to them. Depending on the position of the medium temperature water, it may be selected from which water outlet the medium temperature water is taken out.

  The heat exchanger 119 has a double tube structure of an inner tube and an outer tube, a first channel 119a is formed inside the inner tube, and a second channel 119b is formed between the inner tube and the outer tube. (In FIG. 1, they are drawn as parallel lines for the sake of simplicity). The first flow path 119 a constitutes a part of the gas-phase refrigerant flow path 118, and the second flow path 119 b constitutes a part of the intermediate temperature water flow path 126. That is, the gas-phase refrigerant separated by the gas-liquid separator 106 flows through the first flow path 119 a, and the medium-temperature water extracted from the intermediate portion of the hot water storage tank 102 flows through the second flow path 11. The flow of the gas-phase refrigerant in the first flow path 119a and the flow of intermediate temperature water in the second flow path 119b are counterflows.

  More specifically, the intermediate temperature water passage 126 includes an upstream pipe 126A that connects the water inlet 126a and the inlet of the second flow path 119b of the heat exchanger 119, and an outlet and a reciprocating water inlet 126b of the second flow path 119b. And a downstream pipe 126B to be connected. In the present embodiment, the third pump 127 is provided in the downstream pipe 126B, but the third pump 127 may be provided in the upstream pipe 126A.

  In the upstream pipe 126A, a first opening / closing valve 128 is provided in the vicinity of the water supply port 126a (that is, in the vicinity of the upstream end of the intermediate temperature water flow passage 126). On the other hand, in the downstream pipe 126B, a second on-off valve 129 is provided in the vicinity of the condensing port 126b (that is, in the vicinity of the downstream end of the intermediate temperature water flow passage 126 and downstream of the third pump 127). Further, a discharge passage 130 having a discharge valve 131 is connected to the downstream pipe 126B on the upstream side of the third pump 127, and the medium-temperature water in the medium-temperature water flow passage 126 is connected to the discharge port 132 through the discharge passage 130. Can be discharged. The discharge path 130 may be connected to the downstream side of the first on-off valve 128 of the upstream pipe 126A. Further, the downstream pipe 126B is provided with a flow rate adjusting temperature sensor 133 for detecting the temperature of the medium-temperature water cooled by the heat exchanger 119.

  The hot water storage tank 102 is provided with a hot water storage temperature sensor 132 for detecting the water temperature in the hot water storage tank 102 at a height position corresponding to the upstream end of the intermediate temperature liquid flow passage 126. Here, the “height position corresponding to the upstream end of the intermediate temperature water flow passage 126” may be within a range of 30 cm above and below the upstream end of the intermediate temperature water flow passage 126 as a center.

  The heating device 100 further includes a control device 134 connected to the first to third pumps 214, 125, 127, various valves 128, 129, 131, and various temperature sensors 132, 133. The control device 134 performs a hot water storage operation and a heating operation, and also performs an intermediate temperature water cooling operation. In the medium-temperature water cooling operation, the control device 134 controls the third pump, the on-off valves 128 and 129, and the discharge valve 131 based on the temperature detected by the hot water storage temperature sensor 132 and the flow rate adjusting temperature sensor 133.

[Operation of Heating Device 100]
Next, operation | movement of the heating apparatus 100 is demonstrated.

  First, the operation of the heat pump 101 will be described. The refrigerant compressed by the first compression mechanism 108 is once discharged from the first compression mechanism 108 into the first sealed container 112 and then flows out of the first sealed container 112. Similarly, the refrigerant compressed by the second compression mechanism 113 is once discharged from the second compression mechanism 113 into the second sealed container 116 and then flows out of the second sealed container 116.

  The refrigerant that has flowed out of the first sealed container 112 and the refrigerant that has flowed out of the second sealed container 116 join together and flow into the radiator 105, where they are dissipated. The refrigerant radiated by the radiator 105 is directly sucked into the expansion mechanism 109.

  The refrigerant expands in the expansion mechanism 109, and the expansion mechanism 109 recovers power from the expanding refrigerant. The expanded refrigerant is in a gas-liquid two-phase state. The expanded refrigerant is directly discharged from the expansion mechanism 109.

  The refrigerant discharged from the expansion mechanism 109 flows into the gas / liquid separator 106. In the gas-liquid separator 106, the refrigerant is separated into a gas phase refrigerant and a liquid phase refrigerant. The liquid phase refrigerant flows into the evaporator 107 through the piping that constitutes the refrigerant circuit 117. At this time, a part of the gas phase refrigerant may be mixed with the flow of the liquid phase refrigerant. The liquid-phase refrigerant that has flowed into the evaporator 107 absorbs heat here and evaporates. On the other hand, the gas-phase refrigerant flows into the first flow path 119a of the heat exchanger 119 through the gas-phase refrigerant flow passage 118. The gas-phase refrigerant that has flowed into the first flow path 119a of the heat exchanger 119 is heated by the intermediate temperature water in the heat exchanger 119 when the intermediate temperature water cooling operation is performed.

  The refrigerant that has flowed out of the evaporator 107 merges with the refrigerant that has flowed out of the heat exchanger 119 and is sucked into the first compression mechanism 108 and the second compression mechanism 113.

  Subsequently, hot water storage operation and heating operation will be described.

  First, water such as tap water is supplied from the water supply pipe 122 into the hot water storage tank 102. The water supplied from the water supply pipe 122 is low-temperature water at about room temperature. Then, when the first pump 124 is driven, low-temperature water flows out to the forward pipe 120 from the forward outlet 120 a provided in the lower bottom surface of the hot water storage tank 102. The low-temperature water flows through the forward pipe 120 and flows into the radiator 105 of the heat pump 101. The low-temperature water absorbs heat from the high-temperature refrigerant by the radiator 105 and becomes high-temperature hot water. The high temperature water flowing out of the radiator 105 flows through the return pipe 121 and flows into the hot water storage tank 102 from the return port 121a provided on the upper side surface of the hot water storage tank 102. Thereby, in the hot water storage tank 102, the high temperature water layer L1 is formed from the upper part of the hot water storage tank 102, and the low temperature water layer L2 of the lower part of the hot water storage tank 102 and temperature stratification are formed.

  The high temperature water stored in the upper part of the hot water storage tank 102 is supplied to the heating path 123 from a hot water outlet 123 a provided on the upper side surface of the hot water storage tank 102. The high temperature water flowing out from the warm water outlet 123a flows into the heater 123b such as a radiator and dissipates heat to the room air, and becomes medium warm water due to a decrease in the water temperature. The intermediate warm water that has flowed out of the heater 123 b flows into the hot water storage tank 102 from the hot water return port 123 c provided on the side surface of the intermediate portion of the hot water storage tank 102. As a result, in the hot water storage tank 102, an intermediate hot water layer L3 is formed between the high temperature water layer L1 above the hot water storage tank 102 and the low temperature water layer L2 below the hot water storage tank 102.

  Next, the medium temperature water cooling operation will be described. This intermediate temperature water cooling operation is performed simultaneously with the hot water storage operation.

  When the intermediate temperature water layer L3 is not generated in the hot water storage tank 102 (only when the low temperature water or only the high temperature water is formed, or when the temperature stratification is formed by the low temperature water layer L2 and the high temperature water layer L1), the intermediate temperature water circulation is performed. The third pump 127 provided in the passage 126 is stopped, and the first on-off valve 128 and the second on-off valve 129 are closed. Further, the discharge valve 131 is in an open state, and the medium temperature water flow passage 126 is drained.

  When the intermediate temperature water layer L3 is generated in the hot water storage tank 102, the discharge valve 131 is closed, and the first on-off valve 128 and the second on-off valve 129 are opened. Then, the third pump 127 is driven, and the medium temperature water in the hot water storage tank 102 flows into the medium temperature water flow passage 126.

  The control of the discharge valve 131, the on-off valves 128 and 129, and the third pump 127 is performed by the control device 134. The water temperature detected by the hot water storage temperature sensor 132 provided in the hot water storage tank 102 is output to the control device 134, and the control device 134 sets the water temperature detected by the hot water storage temperature sensor 132 to a preset temperature range. It is judged whether it exists in (for example, 45-70 degreeC). When the water temperature detected by the hot water storage temperature sensor 132 is lower or higher than the set temperature range, the control device 134 opens the discharge valve 131, opens the first on-off valve 128 and the second on-off valve 129. Is closed and the third pump 127 is stopped.

  When the water temperature detected by the hot water storage temperature sensor 132 falls within the set temperature range, the control device 134 closes the discharge valve 131, opens the first on-off valve 128 and the second on-off valve 129, and operates the third pump 127. To start. Next, the control device 134 keeps the temperature detected by the flow rate adjusting temperature sensor 133 provided in the downstream pipe 126B of the intermediate temperature water flow passage 126 within a desired temperature range (for example, about 10 to 30 ° C.). In addition, the rotational speed of the third pump 127 is controlled.

  After that, when the water temperature detected by the hot water storage temperature sensor 132 falls below or exceeds the set temperature range, the control device 134 stops the operation of the third pump 127 and switches the first on-off valve 128 and the second on-off valve 129. Close and open the drain valve 131. When the rising speed of the upper surface of the low temperature water layer L2 in the hot water storage tank 102 is higher than the lowering speed of the lower surface of the high temperature water layer L1, the water temperature detected by the hot water temperature sensor 132 is below the set temperature range. In the opposite case, the water temperature detected by the hot water storage temperature sensor 132 exceeds the set temperature range.

<Effects of First Embodiment>
In the heating apparatus 100 according to the present embodiment, a gas-liquid separator 106 is provided on the upstream side of the evaporator 107, and the medium-temperature water generated in the hot water storage tank 102 is cooled by the gas-phase refrigerant separated by the gas-liquid separator 106. Thus, the evaporator 107 can reliably evaporate the liquid refrigerant regardless of the presence or absence of the medium temperature water. The refrigerant evaporated in the evaporator 107 joins with the gas-phase refrigerant separated in the gas-liquid separator 106 and is then sucked into the first compression mechanism 108 and the second compression mechanism 113, so that the first compression mechanism 108 and Only the refrigerant in the gas phase state can be sucked into the second compression mechanism 113. Therefore, according to this embodiment, liquid compression can be prevented while allowing the cooling process of the medium-temperature water to be performed, and the reliability of the first compression mechanism 108 and the second compression mechanism 113 and the stability of the refrigeration cycle are improved. be able to.

  Further, the refrigerant discharged from the expansion mechanism 109 is separated into a gas-phase refrigerant and a liquid-phase refrigerant in the gas-liquid separator 106, and only the liquid-phase refrigerant flows into the evaporator 107, thereby reducing the pressure loss in the evaporator 107. Can be reduced. As a result, a decrease in suction portion pressure between the first compression mechanism 108 of the expander-integrated compressor 103 and the second compression mechanism 113 of the second compressor 104 can be reduced, and the efficiency of the heat pump 101 can be increased. Become.

  The gas-phase refrigerant separated by the gas-liquid separator 106 flows into the first flow path 119a of the heat exchanger 119 through the gas-phase refrigerant flow path 118. Then, the medium-temperature water generated in the hot water storage tank 102 and flowing into the medium-temperature water flow passage 126 flows into the second flow path 119b of the heat exchanger 119, and in the heat exchanger 119, the vapor phase of the first flow path 119a. Heat exchange is performed between the refrigerant and the medium temperature water of the second flow path 119b. That is, the gas-phase refrigerant in the first channel 119a is heated by the medium temperature water in the second channel 119b.

  The gas-phase refrigerant separated in the gas-liquid separator 106 has a saturation temperature. On the other hand, the liquid-phase refrigerant separated in the gas-liquid separator 106 is heated to the saturation temperature or higher in the evaporator 107. Therefore, if the gas-phase refrigerant is not heated in the gas-phase refrigerant flow passage 118, the expander-integrated compression is used. When the refrigerant that has passed through the evaporator 107 joins the refrigerant that has passed through the gas-phase refrigerant flow passage 118 at the suction portion of the first compression mechanism 108 of the machine 103 and the second compression mechanism 113 of the second compressor 104, The degree of superheat will decrease. However, in the heating apparatus 100 of the present embodiment, the gas-phase refrigerant separated in the gas-liquid separator 106 is heated by the medium-temperature water flowing through the medium-temperature water flow passage 126 in the heat exchanger 119 and raised to the saturation temperature or higher. Therefore, it is possible to suppress a decrease in the degree of superheat when the refrigerant after passing through the evaporator 107 and the refrigerant after passing through the gas-phase refrigerant flow passage 118 merge. This prevents a decrease in suction temperature of the first compression mechanism 108 of the expander-integrated compressor 103 and the second compression mechanism 113 of the second compressor 104, and discharge of the first compression mechanism 108 and the second compression mechanism 113. It is possible to provide a heating apparatus 100 that maintains a high temperature and has a high heating capacity.

  FIG. 2A is a Mollier diagram of the heat pump when the intermediate temperature water cooling operation is executed, and FIG. 2B is a Mollier diagram of the heat pump when the intermediate temperature water cooling operation is not executed.

  As operating conditions of the heat pump 101, the high pressure is set to 10.0 MPa, the low pressure is set to 3.0 MPa, and the degree of heating at the outlet of the evaporator 107 is set to 5 ° C. When the medium temperature water cooling operation is not executed, the refrigerant temperature at the outlet of the radiator 105 is defined as medium temperature water returning from the heating path 123 and becomes 45 ° C.

  As shown in FIG. 2 (b), when the intermediate temperature water cooling operation is not performed, the compression means suction portion (the suction portion of the first compression mechanism 108 and the second compression mechanism 113 in FIG. 1; hereinafter, the first compression mechanism). 108 and the second compression mechanism 113 are also collectively referred to as “compression means”), the liquid phase refrigerant separated by the gas-liquid separator 106 provided downstream of the expansion mechanism 109 is: Upon receiving atmospheric heat in the evaporator 107, the temperature becomes about −0.55 ° C. (3.0 MPa saturation temperature + superheat degree 5 ° C.) and flows out of the evaporator 107 (point a in the figure), to the suction means of the compression means And so on. On the other hand, since the gas-phase refrigerant separated by the gas-liquid separator 106 does not receive heat by the heat exchanger 119, it is at about −5.55 ° C. (3.0 MPa saturation temperature) (point b in the figure). To the compression means suction part.

  For this reason, when the refrigerant that has passed through the evaporator 107 and the refrigerant that has flowed through the gas-phase refrigerant flow passage 118 join before being sucked into the compression means, the temperature becomes approximately −3.41 ° C., and the compression means The refrigerant temperature to be sucked is lowered (about −0.55 ° C. → about −3.41 ° C.). This lowers the discharge temperature of the compression means. For example, if the suction temperature of the compression means is about −0.55 ° C., the suction temperature of the compression means becomes about −3.41 ° C., so that the discharge temperature of the compression means that was about 93.8 ° C. is about 90 ° C. .It drops to 2 ° C.

  On the other hand, when the medium temperature water cooling operation is performed under the same operating conditions of the heat pump 101 (high pressure is 10.0 MPa, low pressure is 3.0 MPa, and the degree of heating at the outlet of the evaporator 107 is 5 ° C.), the heating path 123 is used. The intermediate temperature water returning from the refrigerant is cooled by the gas phase refrigerant flowing in the gas phase refrigerant flow path 118 by flowing the medium temperature water through the medium temperature water flow path 126, and the outlet temperature of the radiator 105 is set to 40 ° C.

  As shown in FIG. 2A, when the intermediate temperature water cooling operation is executed, the refrigerant temperature at the suction portion of the compression means is separated by the gas-liquid separator 106 provided on the downstream side of the expansion mechanism 109. The liquid refrigerant thus received is subjected to atmospheric heat in the evaporator 107, becomes approximately −0.55 ° C. (3.0 MPa saturation temperature + superheat degree 5 ° C.), and flows out of the evaporator 107 (point a in the figure). ) To the compression means suction part. On the other hand, the gas-phase refrigerant separated by the gas-liquid separator 106 receives heat from 45 ° C. medium-temperature water flowing through the intermediate-temperature water flow passage 126 by the heat exchanger 119 and becomes about 22.4 ° C. (point b in the figure). ) To the compression means suction part. At this time, the medium temperature water becomes 40 ° C. at the outlet of the heat exchanger 119. Further, the flow rate of the intermediate warm water flowing through the intermediate warm water flow passage 126 is equal to the amount of water returning from the heating path 123 to the hot water storage tank 102, and the increase of the intermediate warm water layer L3 in the hot water storage tank 102 is suppressed.

  When the refrigerant that has passed through the evaporator 107 and the refrigerant that has flowed through the gas-phase refrigerant flow passage 118 join before being sucked into the compression means, the temperature becomes approximately 8.86 ° C. As a result, the discharge temperature of the compression unit becomes approximately 105.4 ° C., and the discharge temperature of the compression unit can be increased.

  Further, in the heating device 100 of the present embodiment, when the liquid phase refrigerant is mixed in the gas phase refrigerant flow passage 118 into which the gas phase refrigerant separated in the gas-liquid separator 106 flows, the heat exchanger 119 heats with medium temperature water. As a result, the liquid refrigerant evaporates, preventing the first compression mechanism 108 of the expander-integrated compressor 103 and the second compression mechanism 113 of the second compressor 104 from sucking the liquid refrigerant and causing liquid compression. be able to. Accordingly, the reliability of the first compression mechanism 108 of the expander-integrated compressor 103 and the second compression mechanism 113 of the second compressor 104 can be improved, and the heating apparatus 100 having high reliability can be provided. .

  Further, according to the heating device 100 of the present embodiment, the medium-temperature water generated in the hot water storage tank 102 by operating the heating device 100 is guided to the medium-temperature water flow passage 126, and the gas-liquid separator 106 in the heat exchanger 119. The medium temperature water layer L3 in the hot water storage tank 102 can be eliminated by cooling with the gas-phase refrigerant separated in (3) and returning the cooled low temperature water into the hot water storage tank 102. As a result, the water flowing out from the outlet 120a of the hot water storage tank 102 and flowing into the radiator 105 of the heat pump 101 through the outgoing pipe 120 can be prevented from becoming medium temperature water, and can always be low temperature water. And the temperature difference of the refrigerant | coolant between the inlet_port | entrance of the heat radiator 105 of the heat pump 101 and an exit can be enlarged, the fall of the heating capability of the heat pump 101 can be prevented, and a high heating capability can be maintained.

  As shown in FIG. 2A and FIG. 2B, the intermediate temperature water is cooled from 45 ° C. to 40 ° C. by the gas-phase refrigerant separated in the gas-liquid separator 106, so that The enthalpy difference is increasing. As a result, the amount of heat dissipated in the radiator 105 increases, so that the heating capacity of the heat pump 101 increases.

  Moreover, in the heating apparatus 100 of this embodiment, when the intermediate temperature water layer L3 is not generated in the hot water storage tank 102, the third pump 127 provided in the intermediate temperature water flow passage 126 is stopped, and the first The on-off valve 128 and the second on-off valve 129 are in a closed state. Further, the discharge valve 131 is opened, and the medium temperature water flow passage 126 is drained. As a result, when intermediate temperature does not flow into the intermediate temperature water flow passage 126 and the ambient temperature of the intermediate temperature water flow passage 126 reaches or falls below the freezing temperature of the water, the water is frozen in the intermediate temperature water flow passage 126 and the piping. Etc. can be prevented from being damaged. In addition, in the state where the ambient temperature of the intermediate temperature water passage 126 is equal to or lower than the freezing temperature of water, the intermediate temperature water generated in the hot water storage tank 102 when the temperature value measured by the hot water temperature sensor 132 enters the set temperature range. Can immediately flow into the warm water flow passage 126.

<Modification>
In the above-described embodiment, the certain time during which the discharge valve 131 is opened is the total time during which the water temperature detected by the hot water storage temperature sensor 132 is below or above the set temperature range. The fixed time for which the discharge valve 131 is opened may be shorter than the total time of the period. For example, the discharge valve 131 may be opened for a time during which water in the intermediate temperature water passage 126 can be discharged.

  Further, in the heating apparatus 100 of the present embodiment, the flow rate adjustment temperature sensor 133 is provided in the downstream pipe 126B of the intermediate temperature water flow passage 126, so that the freezing is performed based on the temperature detected by the flow rate adjustment temperature sensor 133. It can also be prevented. For example, when the temperature detected by the flow rate adjusting temperature sensor 133 approaches the freezing temperature of water, the number of rotations of the third pump 127 is increased, and the flow rate of the intermediate temperature water flowing through the intermediate temperature water flow passage 126 is increased. Also good. As a result, when the gas-phase refrigerant flowing through the first flow path 119a of the heat exchanger 119 is close to the freezing temperature of water, the flow of intermediate temperature water in the second flow path 119b of the heat exchanger 119 is intensified. Even when the temperature approaches the freezing temperature of water, the medium-temperature water flowing through the second flow path 119b of the heat exchanger 119 can be made difficult to freeze near the outlet of the second flow path 119b of the heat exchanger 119.

  Alternatively, even when the intermediate temperature water layer L3 is generated in the hot water storage tank 102, when the temperature detected by the flow rate adjustment temperature sensor 133 is very close to the freezing temperature of water (or below the freezing temperature of water), The operation of the third pump 127 may be stopped by the control device 134, the first on-off valve 128 and the second on-off valve 129 may be closed, and the discharge valve 131 may be opened. In this way, since the water in the intermediate temperature water flow passage 126 is discharged, it is possible to prevent the piping and the like from being damaged by freezing of water in the intermediate temperature water flow passage 126. Further, when the ambient temperature of the intermediate temperature water flow passage 126 is equal to or lower than the freezing temperature of water, the ambient temperature of the intermediate temperature water flow passage 126 is equal to or higher than the freezing temperature of water. The medium temperature water can immediately flow into the warm water heat exchange circuit 126.

(Second Embodiment)
In FIG. 3, the heating apparatus 300 which concerns on 2nd Embodiment of this invention is shown. In the present embodiment, the same components as those in the first embodiment described above are denoted by the same reference numerals, and detailed description thereof is omitted.

[Configuration of Heating Device 300]
In the heating apparatus 300 of the present embodiment, the discharge path 130 (see FIG. 1) is not connected to the medium-temperature water flow path 126, and a bypass path 301 having a bypass valve 302 is provided instead. The bypass passage 301 extends from a position downstream of the first opening / closing valve 128 of the upstream pipe 126A in the intermediate temperature water flow passage 126 to a position between the third pump 127 and the second opening / closing valve 129 in the downstream pipe 126B.

[Operation of Heating Device 300]
Subsequently, the operation of the bypass path 301 will be described.

  When the intermediate temperature water layer L3 is not generated in the hot water storage tank 102 (only when the temperature stratification is formed by the low temperature water layer L2 and the high temperature water layer L1), the first opening / closing is performed. The valve 128 and the second on-off valve 129 are closed, and the bypass valve 302 provided in the bypass passage 301 is opened. Then, the third pump 127 is driven, and the water stored in the intermediate temperature water flow passage 126 is circulated.

  When the intermediate temperature water layer L3 is generated in the hot water storage tank 102, the first on-off valve 128 and the second on-off valve 129 are opened, and the bypass valve 302 is closed. Then, the third pump 127 continues to be driven, and the medium temperature water in the hot water storage tank 102 flows into the medium temperature water flow passage 126. Thus, in the present embodiment, the third pump 127 is always operating.

  Such control of the bypass valve 302 and the on-off valves 128 and 129 is performed by the control device 134. The water temperature detected by the hot water storage temperature sensor 132 provided in the hot water storage tank 102 is output to the control device 134, and the control device 134 sets the water temperature detected by the hot water storage temperature sensor 132 to a preset temperature range. It is judged whether it exists in (for example, 45-70 degreeC). When the water temperature detected by the hot water storage temperature sensor 132 is lower or higher than the set temperature range, the control device 134 closes the first on-off valve 128 and the second on-off valve 129, and bypass valve 302 is opened.

  When the water temperature detected by the hot water storage temperature sensor 132 falls within the set temperature range, the control device 134 opens the first on-off valve 128 and the second on-off valve 129 and closes the bypass valve 302. Next, the control device 134 keeps the temperature detected by the flow rate adjusting temperature sensor 133 provided in the downstream pipe 126B of the intermediate temperature water flow passage 126 within a desired temperature range (for example, about 10 to 30 ° C.). In addition, the rotational speed of the third pump 127 is controlled.

  Thereafter, when the water temperature detected by the hot water storage temperature sensor 132 falls below or exceeds the set temperature range, the control device 134 closes the first on-off valve 128 and the second on-off valve 129 and opens the bypass valve 302.

<Effects of Second Embodiment>
In the heating device 300 of the present embodiment, when the water temperature detected by the hot water storage temperature sensor 132 is outside the set temperature range, a closed loop is formed by the intermediate temperature water flow passage 126 and the bypass passage 301, The water stored in the hot water flow passage 126 is circulated. As a result, even when the medium temperature water does not flow into the medium temperature water flow passage 126 and the ambient temperature of the medium temperature water flow passage 126 reaches the water freezing temperature or less, the water flow in the medium temperature water flow passage 126 is made intense. Further, it is possible to prevent the piping and the like from being damaged due to freezing of water in the intermediate temperature water flow passage 126. Further, when the temperature value measured by the hot water storage temperature sensor 132 enters the set temperature range from the state where the ambient temperature of the intermediate temperature water flow passage 126 is equal to or lower than the freezing temperature of water, the intermediate temperature water generated in the hot water storage tank 102 is generated. Can immediately flow into the hot water heat exchange circuit 126.

  Further, in the heating device 300 of the present embodiment, when the intermediate temperature water flow passage 126 is stopped, water is circulated in the intermediate temperature water flow passage 126 and the bypass passage 301, so that the water system circuit (the hot water storage tank 102, the middle The water stored in the warm water flow passage 126 and the heating passage 123) can be maintained without being reduced by drainage or the like.

<Modification>
In the above-described embodiment, the fixed time during which the bypass valve 302 is opened and the third pump 127 is operated is a period in which the water temperature detected by the hot water storage temperature sensor 132 is below or above the set temperature range. Although it is the total time, the fixed time during which the bypass pump 302 is opened and the third pump 127 is operated may be shorter than the total time of the period. For example, the third pump 127 may be operated while the bypass valve 302 is intermittently opened during the period.

(Other embodiments)
In the first and second embodiments, the expander-integrated compressor 103 and the second compressor 104 are used. However, the present invention is also applicable to a heating apparatus using only the expander-integrated compressor 103. Is possible. That is, the compression means of the present invention may be composed of the first compression mechanism 108 and the second compression mechanism 113 or may be composed of only the first compression mechanism 108.

  In the present invention, the expander-integrated compressor 103 is not necessarily used. Even if the first compression mechanism 108 and the expansion mechanism 109 are accommodated in separate containers and the expansion mechanism 109 is connected to the generator. Good.

  Furthermore, in addition to the expansion mechanism 109, for example, an expansion valve can be employed as the expansion means of the present invention.

  The heating device of the present invention is particularly useful as a heating device that can suppress the production of medium-temperature water and increase the efficiency of the heat pump.

DESCRIPTION OF SYMBOLS 100,300 Refrigeration cycle apparatus 101 Heat pump 102 Hot water storage tank 103 Expander-integrated compressor 104 Second compressor 105 Radiator 106 Gas-liquid separator 107 Evaporator 118 Gas-phase refrigerant flow path 119 Heat exchanger 126 Medium temperature water flow path 127 Third pump 128 First on-off valve 129 Second on-off valve 130 Discharge passage 131 Discharge valve 132 Hot water storage temperature sensor 133 Flow rate adjusting temperature sensor 134 Controller 301 Bypass passage 302 Bypass valve L1 High temperature water layer L2 Low temperature water layer L3 Medium temperature water layer

Claims (14)

Compression means for compressing the refrigerant, a radiator for dissipating the refrigerant compressed by the compression means, an expansion means for expanding the refrigerant dissipated by the radiator, and a refrigerant expanded by the expansion means as a gas phase refrigerant and a liquid phase refrigerant A refrigerant circuit comprising: a gas-liquid separator to be separated; and an evaporator for evaporating the liquid-phase refrigerant separated by the gas-liquid separator;
A gas-phase refrigerant flow passage for guiding the gas-phase refrigerant separated by the gas-liquid separator to a portion of the refrigerant circuit between the evaporator and the compression means;
A tank withdrawn from the lower part is heated by the radiator and then returned to the upper part;
A heater for dissipating heat from the heated liquid stored in the tank;
An intermediate temperature liquid flow passage for flowing an intermediate temperature liquid in the tank caused by a temperature drop of the heated liquid, the upstream end and the downstream end being connected to the tank;
A heat exchanger that cools the intermediate temperature liquid flowing through the intermediate temperature liquid flow passage by the gas phase refrigerant flowing through the gas phase refrigerant flow passage;
A heating device comprising:   The heating according to claim 1, wherein an upstream end of the intermediate temperature liquid flow passage is connected to an intermediate portion or a lower portion of the tank, and a downstream end of the intermediate temperature liquid flow passage is connected to a lower portion of the tank. apparatus. A temperature sensor provided at a height position corresponding to the upstream end of the intermediate temperature liquid flow path in the tank, for detecting the liquid temperature in the tank;
The intermediate temperature liquid flow passage is provided with a pump,
The heating apparatus according to claim 2, wherein the pump starts operating when a liquid temperature detected by the temperature sensor falls within a set temperature range.   The heating device according to claim 3, wherein when the liquid temperature detected by the temperature sensor falls below the set temperature range or exceeds the set temperature range, the pump stops operating. The intermediate temperature liquid flow passage is provided with a first on-off valve in the vicinity of the upstream end, and a second on-off valve in the vicinity of the downstream end,
The heating device according to claim 3 or 4, wherein the pump is disposed between the heat exchanger and the second on-off valve.   When the liquid temperature detected by the temperature sensor falls within the set temperature range, the first on-off valve and the second on-off valve are opened, and the liquid temperature detected by the temperature sensor falls below the set temperature range, or The heating device according to claim 5, wherein when the temperature exceeds a set temperature range, the first on-off valve and the second on-off valve are closed. A discharge path having a discharge valve is connected to a portion between the first on-off valve and the pump in the intermediate temperature liquid flow path,
7. The discharge valve according to claim 6, wherein the discharge valve is opened for a certain period of time during a period in which the liquid temperature detected by the temperature sensor is below the set temperature range or above the set temperature range. Heating device. A bypass path having a bypass valve from the position between the first on-off valve and the heat exchanger to the position between the pump and the second on-off valve in the intermediate temperature liquid flow path;
The liquid temperature detected by the temperature sensor is lower than the set temperature range or is higher than the set temperature range for a certain period of time, the bypass valve is opened and the pump operates. The heating device according to claim 6. The intermediate temperature liquid flow passage is provided with a flow rate adjusting temperature sensor for detecting the temperature of the intermediate temperature liquid cooled by the heat exchanger,
The heating device according to any one of claims 3 to 8, further comprising a control device that controls a rotation speed of the pump based on a temperature detected by the temperature sensor for flow rate adjustment.   The heat exchanger has a double tube structure of an inner tube and an outer tube, a first flow path through which the gas-phase refrigerant flows is formed inside the inner tube, and the space between the inner tube and the outer tube The heating device according to any one of claims 1 to 9, wherein a second flow path through which the medium-temperature liquid flows is formed.   The heating device according to claim 10, wherein the flow of the gas-phase refrigerant in the first flow path and the flow of the medium-temperature liquid in the second flow path are counterflows.   The heating device according to any one of claims 1 to 11, wherein the expansion means is an expansion mechanism that recovers power from the expanding refrigerant.   The heating device according to claim 12, wherein the compression means includes a compression mechanism connected to the expansion mechanism by a rotation shaft.   The heating device according to claim 13, wherein the compression means further includes a second compression mechanism connected in parallel with the compression mechanism.

Images