CROSS REFERENCE TO RELATED APPLICATION
This application is a U.S. national stage application of PCT/JP2015/051630 filed on Jan. 22, 2015, the contents of which are incorporated herein by reference.
TECHNICAL FIELD
The present invention relates to a plate heat exchanger that performs heat exchange between refrigerant and heating target fluid, and a heat pump outdoor unit including the same.
BACKGROUND ART
A heat pump outdoor unit for performing hot-water supply or a cooling/heating operation includes a system using a plate heat exchanger as a condenser and a subcooler. Examples of the plate heat exchanger include a plate heat exchanger serving as both a condenser and a subcooler. For example, in a proposed plate heat exchanger, a boundary plate is provided in a heat transfer unit to define two heat exchange units (a condensation unit and a subcooling unit) (see, for example, Patent Literature 1).
CITATION LIST
Patent Literature
Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2005-106385
SUMMARY OF INVENTION
Technical Problem
In the plate heat exchanger proposed in Patent Literature 1, a first fluid (high-temperature, high-pressure gas refrigerant) that is a heating fluid and a second fluid (water) that is a heating target fluid, both being to exchange heat with each other, flow in the first heat exchange unit (condensation unit). A first fluid (low-temperature, high-pressure liquid refrigerant) that is a heating fluid and a third fluid (low-temperature, low-pressure two-phase refrigerant) that is a heating target fluid, both being to exchange heat with each other, flow in the second heat exchange unit (subcooling unit). In a case where the first heat exchange unit (condensation unit) and the second heat exchange unit (subcooling unit) are included in the same plate heat exchanger, the second fluid (water) and the third fluid (low-temperature, low-pressure two-phase refrigerant) exchange heat with each other through the boundary plate in a portion of the plate heat exchanger so that the temperature of the second fluid (water) decreases and, thereby, thermal efficiency decreases.
The present invention has been made to solve the problems described above, and provides a plate heat exchanger that can suppress thermal contact between the second fluid (water) and the third fluid (low-temperature, low-pressure two-phase refrigerant) and enhance thermal efficiency.
Solution to Problem
The present invention provides a plate heat exchanger including: a first heat transfer plate group that performs heat exchange between a first fluid of high-temperature, high-pressure gas refrigerant and a second fluid of a heating target fluid; and a second heat transfer plate group that performs heat exchange between a first fluid of low-temperature, high-pressure liquid refrigerant and a third fluid of low-temperature, low-pressure two-phase liquid refrigerant, wherein the first heat transfer plate group forms a plurality of refrigerant channels constituted by a stack of plates, has a configuration that a flow of the first fluid of high-temperature, high-pressure gas refrigerant and a flow of the second fluid are alternately aligned in the refrigerant channels, and causes the second fluid to flow in an outermost one of the refrigerant channels, and the second heat transfer plate group forms a plurality of refrigerant channels constituted by a stack of plates, has a configuration that a flow of the first fluid of low-temperature, high-pressure liquid refrigerant and a flow of the third fluid are alternately aligned in the refrigerant channels, and causes the first fluid of low-temperature, high-pressure liquid refrigerant to flow in one of the refrigerant channels adjacent to the first heat transfer plate group.
Advantageous Effects of Invention
According to the present invention, a flow of the first refrigerant and a flow of the second refrigerant are alternately aligned in the refrigerant channels of the first heat transfer plate group, and the second fluid flows in the outermost refrigerant channel. In the refrigerant channels of the second heat transfer plate group, a flow of the first refrigerant and a flow of the second refrigerant are also alternately aligned, and the first fluid of low-temperature, high-pressure liquid refrigerant flows in the refrigerant channel adjacent to the first heat transfer plate group. Thus, the first fluid of low-temperature, high-pressure liquid refrigerant flows between the second fluid and the third fluid. Thus, thermal contact between the second fluid and the third fluid can be suppressed, and a temperature difference between the fluids decreases so that the amount of heat transfer from the second fluid can be reduced, and thermal efficiency can be enhanced.
BRIEF DESCRIPTION OF DRAWINGS
FIG. 1 is a refrigerant circuit diagram of a heat pump hot-water supply apparatus according to Embodiment 1 of the present invention.
FIG. 2a is a left side view of the plate heat exchanger illustrated in FIG. 1.
FIG. 2b is a front view of the plate heat exchanger illustrated in FIG. 1.
FIG. 2c is a right side view of the plate heat exchanger illustrated in FIG. 1.
FIG. 2d is a rear view of the plate heat exchanger illustrated in FIG. 1.
FIG. 3 is a disassembled perspective view of the plate heat exchanger illustrated in FIG. 1.
FIG. 4 schematically illustrates a flow of fluid in the plate heat exchanger illustrated in FIG. 1.
FIG. 5 is a cross-sectional view taken along line A-A in FIG. 2b.
FIG. 6 is a partially enlarged view of a heat transfer plate group (102a, 102b) illustrated in FIG. 5.
FIG. 7a is a full view of a heat transfer plate (101a) illustrated in FIG. 6.
FIG. 7b is a full view of a heat transfer plate (101b) illustrated in FIG. 6.
FIG. 8a is a full view of a side plate (105a) illustrated in FIG. 6.
FIG. 8b is a full view of a side plate (105b) illustrated in FIG. 6.
FIG. 9a is a full view of a reinforcing plate (104a) illustrated in FIG. 6.
FIG. 9b is a full view of a reinforcing plate (104b) illustrated in FIG. 6.
FIG. 10a is a full view of an isolation plate (106a) illustrated in FIG. 6.
FIG. 10b is a full view of an isolation plate (106b) illustrated in FIG. 6.
FIG. 11 is a full view of an intermediate reinforcing plate (107b) illustrated in FIG. 6.
DESCRIPTION OF EMBODIMENTS
Embodiment 1
FIG. 1 is a refrigerant circuit diagram of a heat pump hot-water supply apparatus according to Embodiment 1 of the present invention. The heat pump hot-water supply apparatus illustrated in FIG. 1 includes a heat pump outdoor unit (heat pump unit) 2 and a water circuit 9, The heat pump outdoor unit 2 includes a compressor 3, a first heat exchanger 4, a second heat exchanger 5, electronic expansion valves 6a and 6b, and a third heat exchanger 7. Operations of these components will be described below.
(1) The compressor 3 compresses refrigerant 8 by using electric power and increases an enthalpy and a pressure of the refrigerant 8.
(2) The first heat exchanger 4 performs heat exchange between the compressed refrigerant 8 (first fluid) and a heating target fluid (second fluid).
(3) The electronic expansion valve 6a adiabatically expands a part (refrigerant 8a) of the refrigerant 8 from the first heat exchanger 4. The electronic expansion valve 6a corresponds to a first expansion valve of the present invention.
(4) The second heat exchanger 5 performs heat exchange between the refrigerant 8 (first fluid) from first heat exchanger 4 and the refrigerant 8a (third fluid) that is a part of the refrigerant 8 and subjected to pressure reduction through the electronic expansion valve 6a. The third fluid is gasified through the heat exchange and is sucked into the compressor 3.
(5) The electronic expansion valve 6b adiabatically expands the refrigerant 8 from the second heat exchanger 5. The electronic expansion valve 6b corresponds to a second expansion valve of the present invention.
(6) The third heat exchanger 7 performs heat exchange between the refrigerant 8 from the electronic expansion valve 6b and an external heat source. Although not shown, the heat pump outdoor unit 2 may include other attachments such as a receiver for storing excess refrigerant 8.
The compressor 3 to the third heat exchanger 7 described above constitute a refrigeration cycle mechanism in which the first fluid circulates. A plate heat exchanger 1 is used as the first heat exchanger 4. In this manner, heat (heat absorbed in the third heat exchanger 7) of an external heat source is transferred by the plate heat exchanger 1 so that the second fluid flowed into the plate heat exchanger 1 is heated. Examples of a medium used as the external heat source (a target of heat exchange in the third heat exchanger 7) include various media such as air and geothermal heat. The plate heat exchanger 1 can be used for any type of the heat pump outdoor unit 2 using an external heat source. In Embodiment 1, the plate heat exchanger 1 includes the second heat exchanger 5 in addition to the first heat exchanger 4, that is, includes two heat exchangers.
The heat pump outdoor unit 2 uses, for example, water 10 as the second fluid. The water 10 circulates in the water circuit 9. The example illustrated in FIG. 1 employs an indirect heating technique. The water 10 flows into the plate heat exchanger 1, which is the first heat exchanger 4, is heated by the first fluid (refrigerant 8), and flows out of the plate heat exchanger 1. After having flowed from the plate heat exchanger 1, the water 10 flows into a heating appliance 11, such as a radiator or a floor heating, connected by pipes constituting the water circuit 9 to be used for indoor temperature control. The water circuit 9 includes a water-to-water heat exchange tank 12 for heat exchange between the water 10 and clean water 13 so that the clean water 13 heated by the water 10 can be used as water for domestic use, such as bathing or shower.
A configuration of the plate heat exchanger 1 illustrated in FIG. 1 will now be described.
FIG. 2a is a left side view of the plate heat exchanger illustrated in FIG. 1, FIG. 2b is a front view of the plate heat exchanger illustrated in FIG. 1, FIG. 2c is a right side view of the plate heat exchanger illustrated in FIG. 1, and FIG. 2d is a rear view of the plate heat exchanger illustrated in FIG. 1.
As illustrated in FIGS. 2a to 2d, the plate heat exchanger 1 includes nozzles 103a to 103g. As illustrated in FIG. 2b, the three nozzles 103a, 103d, and 103e are attached to the front face of the plate heat exchanger 1. As illustrated in FIG. 2d, the four nozzles 103b, 103c, 103fe, and 130g are attached to the rear face of the plate heat exchanger 1. The first fluid flowed through the nozzle 103a, which is a first fluid inlet, flows out from two outlets, that is, the nozzle 103b that is a first outlet and the nozzle 103c that is a second outlet. A passage in which the first refrigerant flows is a first channel. As will be described in detail later, the first fluid flows out of the nozzle 103b after having exchanged heat with the second fluid and the third fluid. The first fluid flows out of the nozzle 103c after having exchanged heat with the second fluid (not having exchanged heat with the third fluid). The second fluid flowed through the nozzle 103d that is a second fluid inlet, flows out of the nozzle 103e that is a second fluid outlet. A passage in which the second fluid flows is a second channel. The third fluid flowed through the nozzle 103f that is a third fluid inlet, flows out of the nozzle 103g that is a third fluid outlet. A passage in which the third fluid flows is a third channel. The first channel, the second channel, and the third channel constitute channels that are independent of each other.
FIG. 3 is a disassembled perspective view of the plate heat exchanger illustrated in FIG. 1. As illustrated in FIG. 3, in the plate heat exchanger 1, a reinforcing plate 104a to which the nozzles 103a, 103d, and 103e are attached, a side plate 105a, a heat transfer plate group 102a (a heat transfer plate 101a, a heat transfer plate 101b, . . . , a heat transfer plate 101a, and a heat transfer plate 101b) corresponding to the first heat exchanger 4, an isolation plate 106a, an intermediate reinforcing plate 107, an isolation plate 106b, a heat transfer plate group 102b (a heat transfer plate 101a, a heat transfer plate 101b . . . , a heat transfer plate 101a, and a heat transfer plate 101b) corresponding to the second heat exchanger 5, a side plate 105b, a reinforcing plate 104b to which the nozzles 103b, 103c, 103f, and 103g are attached, are stacked in this order.
Then, flows of the first to third fluids in the plate heat exchanger 1 will be described.
FIG. 4 schematically illustrates a flow of the fluids in the plate heat exchanger 1 illustrated in FIG. 1.
The first fluid (refrigerant 8) flows from the nozzle 103a into the heat transfer plate group 102a, passes through channel holes formed in the isolation plate 106a, the intermediate reinforcing plate 107, and the isolation plate 106b, and flows into the heat transfer plate group 102b. The first fluid flowed into the heat transfer plate group 102b is divided into a first fluid that exchanges heat with the third fluid (refrigerant 8a) and flows out of the nozzle 103b and a first fluid (which is to be a third fluid subjected to an expansion process) that does not exchange heat with the third fluid (refrigerant 8a) and flows out of the nozzle 103c. The second fluid (heating target fluid) flows into the heat transfer plate group 102a from the nozzle 103d, and flows out of the nozzle 103e. The third fluid flows into the heat transfer plate group 102b from the nozzle 103f, and flows out of the nozzle 103g.
The heat transfer plate group 102a corresponds to a first heat transfer plate group of the present invention. The heat transfer plate group 102b corresponds to a second heat transfer plate group of the present invention. The refrigerant flowed from the nozzle 103a corresponds to a first fluid of high-temperature, high-pressure gas refrigerant of the present invention. The second fluid (heating target fluid) flowed from the nozzle 103d corresponds to a second fluid of a heating target fluid of the present invention. The third fluid flowed from the nozzle 103f corresponds to a low-temperature, low-pressure third fluid of the present invention. The first fluid that has exchanged heat in the heat transfer plate group 102a and flowed into the heat transfer plate group 102b corresponds to a low-temperature, high-pressure first fluid of the present invention.
Referring now to FIGS. 5 to 11, a configuration of the plate heat exchanger 1 will be specifically described.
FIG. 5 is a cross-sectional view corresponding to an A-A section in FIG. 2. Regarding to FIG. 5, the term “corresponding to” is used for the following reason. For simplicity of description in FIG. 5, a total of ten heat transfer plates 101a and 101b constituting the heat transfer plate groups 102a and 102b are used. Thus, since FIG. 5 is not identical to FIG. 2, the term “corresponding to” is used. FIG. 6 is a partially enlarged view of the heat transfer plate groups 102a and 102b illustrated in FIG. 5. The top and bottom in description with reference to FIG. 5 or FIG. 6 respectively refer to the top and bottom in the illustrated positional relationship.
As illustrated in FIGS. 5 and 6, as a main configuration of the plate heat exchanger 1 according to Embodiment 1, the heat transfer plates 101a and 101b are stacked so that the heat transfer plate groups 102a and 102b form channels for heat exchange between the first fluid and the second fluid and between the first fluid and the third fluid. The isolation plate 106a, the intermediate reinforcing plate 107, and the isolation plate 106b are disposed between the heat transfer plate groups 102a and 102b. A fundamental part 108 of the plate heat exchanger 1 (hereinafter referred to as a fundamental part 108) is constituted by disposing the side plate 105a on top of the heat transfer plate group 102a and the side plate 105b at the bottom of the heat transfer plate group 102b. The reinforcing plate 104a is disposed on top of the fundamental part 108 and the reinforcing plate 104b is disposed at the bottom of the fundamental part 108 so that the fundamental part 108 is sandwiched between the reinforcing plate 104a and the reinforcing plate 104b. The reinforcing plates 104a and 104b have nozzle attachment ports (nozzle holes). The nozzles 103a, 103d, and 103e are attached to the nozzle attachment ports of the reinforcing plate 104a. The nozzles 103b, 130c, 103f, and 103g are attached to the nozzle attachment ports of the reinforcing plate 104b. In FIG. 5, the nozzles 103c, 103d, and 103f are behind the nozzles 103b, 103e, and 103g, and thus, are not shown.
(Heat Transfer Plate 101a and Heat Transfer Plate 101b)
FIG. 7a is a full view of the heat transfer plate 101a. FIG. 7b is a full view of the heat transfer plate 101b. The heat transfer plate 101a illustrated in FIG. 7a and the heat transfer plate 101b illustrated in FIG. 7b have the same size and the same thickness. Each of the heat transfer plates 101a and 101b has channel holes 109a to 109d at four corners thereof. Corrugated shapes 110a and 110b for stirring fluid are disposed between the channel holes 109a and 109d and the channel holes 109b and 109c in the longitudinal direction of the heat transfer plate 101a (101b). The corrugated shape 110a of the heat transfer plate 101a is inverted 180 degrees (upside down) from the corrugated shape 110b of the heat transfer plate 101b. That is, the corrugated shape 110b is at a position by rotating the corrugated shape 110a 180 degrees in the direction indicated by an arrow with respect to a point P. The channel holes 109a and 109b of the heat transfer plate 101a and peripheral portions thereof in FIG. 7a are located at lower levels than the channel holes 109c and 109d and peripheral portions thereof in the vertical direction (i.e., at deeper positions in the vertical direction on the drawing sheet). Similarly, in the heat transfer plate 101b illustrated in FIG. 7b, the channel holes 109c and 109d and peripheral portions thereof are located at lower levels than the channel holes 109a and 109b and peripheral portions thereof in the vertical direction (i.e., at deeper positions in the vertical direction on the drawing sheet).
(Channel Formation by Heat Transfer Plates 101a and 101b)
(Heat Transfer Plate Group 102a)
The heat transfer plates 101a and 101b are stacked so that the corrugated shape 110a and the corrugated shape 110b are in point-contact with each other. The point-contact portions are brazed to serve as “pillars” forming channels. For example, a channel for the second fluid (e.g., pure water, tap water, or water containing an antifreeze) is formed by stacking the heat transfer plate 101a and the heat transfer plate 101b in this order. A channel for the first fluid (e.g., a refrigerant, typified by R410A, for use in an air-conditioning apparatus) is formed by stacking the heat transfer plate 101b and the heat transfer plate 101a in this order. Layers of “second fluid-first fluid” are formed by stacking the heat transfer plate 101a, the heat transfer plate 101b, and the heat transfer plate 101a in this order. Subsequently, the number of stacked heat transfer plates is increased so that channels for “second fluid-first fluid-second fluid-first fluid, . . . ” are alternately formed (see FIGS. 4 and 6). The stacked heat transfer plates 101a and 101b described above constitute the heat transfer plate group 102a as illustrated in FIGS. 5 and 6. At this time, the number of heat transfer plates 101a and 101b is an even number, and the stack starts at the heat transfer plate 101a and ends at the heat transfer plate 101b. Thus, the second fluid flows in the outermost member of the heat transfer plate group 102a.
(Heat Transfer Plate Group 102b)
In a manner similar to the heat transfer plate group 102a, the heat transfer plates 101a and 101b are stacked to constitute the heat transfer plate group 102b. A channel for the first fluid is formed by stacking the heat transfer plate 101b and the heat transfer plate 101a in this order. A channel for the third fluid is formed by stacking the heat transfer plate 101a and the heat transfer plate 101b in this order. Layers of “first fluid-third fluid-first fluid” are formed by stacking the heat transfer plate 101a, the heat transfer plate 101b, and the heat transfer plate 101a. Subsequently, channels for “first fluid-third fluid-first fluid . . . ” are alternately formed by increasing the number of stacked heat transfer plates (see FIGS. 4 and 6). The stacked heat transfer plates 101a and 101b described above constitute the heat transfer plate group 102b as illustrated in FIGS. 5 and 6. At this time, the number of heat transfer plates 101a and 101b is an even number, and the stack starts at the heat transfer plate 101b and ends at the heat transfer plate 101a. Thus, the first fluid flows in the outermost member (i.e., the channel closest to the heat transfer plate group 102a) of the heat transfer plate group 102b.
(Side Plates 105a and 105b)
FIG. 8a is a full view of the side plate 105a illustrated in FIG. 6. FIG. 8b is a full view of the side plate 105b illustrated in FIG. 6. The side plate 105a and the side plate 105b are flat plates that have sizes and thicknesses similar to those of the heat transfer plates 101a and 101b, each have channel holes 109a to 109d at the four corners thereof, and do not have corrugated shape 110a, 110a. As illustrated in FIG. 5, the side plate 105a is disposed on top of the heat transfer plate group 102a, and the side plate 105b is disposed at the bottom of the heat transfer plate group 102b, thereby constituting the fundamental part 108. As illustrated in FIGS. 8a and 8b, each of the channel holes 109a and 109b of the side plate 105a has a narrowing portion 111a, and each of the channel holes 109c and 109d of the side plate 105b has a narrowing portion 111b.
(Narrowing Portions 111a to 111d)
As illustrated in FIGS. 5, 8a, and 8b, the side plate 105a has recessed narrowing portions 111a formed by a narrowing process around the channel holes 109a and 109b, and the side plate 105b has projected narrowing portions 111b formed by a narrowing process around the channel holes 109c and 109d. The narrowing portions 111a and 111b are brazed to portions around the channel holes 109a and 109b of the heat transfer plates 101a and 101b so that pillars are formed around the channel holes of the heat transfer plate 101a and the side plates 105a and 105b, thereby increasing the strength thereof.
As illustrated in FIG. 5, the narrowing portions 111a of the side plate 105a form a heat nontransfer space 112a formed by the side plate 105a and the heat transfer plate 101a and prevent the first fluid from flowing therein. The heat nontransfer space 112a is a space formed by a plane and the corrugated shape (110b), and has poor heat conduction. Thus, it is possible to prevent the first fluid from flowing into the heat nontransfer space 112a so that excessive heat transfer and a decrease in flow rate of refrigerant can be prevented. Similarly, the narrowing portions 111b of the side plate 105b form a heat nontransfer space 112b formed by the side plate 105b and the heat transfer plate 101a and prevent the third fluid flow flowing therein.
Reinforcing Plate (Pressure-resistant Plate) 104a and 104b)
FIG. 9a is a full view of the reinforcing plate 104a illustrated in FIG. 6. FIG. 9b is a full view of the reinforcing plate 104b illustrated in FIG. 6. As illustrated in FIG. 5, the reinforcing plate 104a is attached to the top of the fundamental part 108, and the reinforcing plate 104b is attached to the bottom of the fundamental part 108. Each of the reinforcing plates 104a and 104b has a thickness about five times as large as those of the heat transfer plates 101a and 101b and the side plate 105, for example. In the plate heat exchanger 1, each of the reinforcing plates 104a and 104b has three channel holes 109a, 109c, and 109d as illustrated in FIG. 9.
In the reinforcing plate 104a, the nozzles 103a, 103d, and 103e are brazed to the channel holes 109a, 109c, and 109d, respectively, at the side opposite to the heat transfer plate group 102a. In the reinforcing plate 104b, the nozzles 103b, 130c, 103f, and 103g are brazed to the channel holes 109a, 109c, and 109d, respectively, at the side opposite to the heat transfer plate group 102b. The reinforcing plates 104a and 104b enable the plate heat exchanger 1 to withstand fatigue due to a variation of a pressure caused by a fluid flowing in the fundamental part 108 and a force occurring due to a difference between the pressure of the plate heat exchanger 1 and an atmospheric pressure.
(Isolation Plates 106a and 106b)
FIG. 10a is a full view of the isolation plate 106a illustrated in FIG. 6. FIG. 10b is a full view of the isolation plate 106b. As illustrated in FIG. 5, the isolation plate 106a is disposed at the bottom of the heat transfer plate group 102a, and the isolation plate 106b is disposed on top of the heat transfer plate group 102b. The isolation plate 106a is a flat plate that has a size and a thickness similar to those of the heat transfer plate 101a (101b), has a channel hole 109b, and does not have the corrugated shape 110a. The isolation plate 106a has a narrowing portion 111c at the side facing the heat transfer plate group 102a, and as illustrated in FIG. 5, is brazed to peripheral portions of the channel holes 109a and 109b of the heat transfer plate 101b lastly stacked in the heat transfer plate group 102a to prevent the first fluid from flowing into a heat nontransfer space 112c. Similarly, the isolation plate 106b is also a flat plate that has a size and a thickness similar to those of the heat transfer plate 101b (101a), has a channel hole 109b, and does not have the corrugated shape 110b. The isolation plate 106b has a narrowing portion 111d at the side facing the heat transfer plate group 102b, and as illustrated in FIG. 5, is brazed to peripheral portions of the channel holes 109c and 109d of the heat transfer plate 101b to prevent the third fluid from flowing into the heat nontransfer space 112d.
(Intermediate Reinforcing Plate 107)
FIG. 11 is a full view of the intermediate reinforcing plate 107 illustrated in FIG. 6. As illustrated in FIG. 11, the intermediate reinforcing plate 107 has the same shape and the same thickness as those of the reinforcing plates 104a and 104b, and has a channel hole 109b. The intermediate reinforcing plate 107 is sandwiched between the isolation plate 106a and the isolation plate 106b, and can withstand a force occurring due to a difference between the pressure of the second fluid and the pressure of the third fluid.
The heat transfer plate group 102a and the heat transfer plate group 102b are brazed with the isolation plate 106a, the intermediate reinforcing plate 107, and the isolation plate 106b sandwiched therebetween so that the plate heat exchanger 1 can serve as both the first heat exchanger 4 and the second heat exchanger 5. Since the outermost member of the heat transfer plate group 102a is the second fluid, and the outermost member of the heat transfer plate group 102b is the first fluid, a channel configuration of a fluid flow schematically illustrated in FIG. 4 is formed so that the second fluid does not contact the third fluid at a low temperature. Thus, a decrease in the outlet temperature of the second fluid can be suppressed so that thermal efficiency of the plate heat exchanger 1 can be enhanced.
REFERENCE SIGNS LIST
1 plate heat exchanger, 2 heat pump outdoor unit, 3 compressor, 4 first heat exchanger, 5 second heat exchanger, 6a, 6b electronic expansion valve, 7 third heat exchanger, 8, 8b refrigerant, 9 water circuit, 10 water, 11 heating appliance, 12 water heat exchange tank, 13 clean water, 101a heat transfer plate, 101b heat transfer plate, 102a heat transfer plate group, 102b heat transfer plate group, 103a to 103g nozzle, 104a, 104b reinforcing plate, 105a, 105b side plate, 106a, 106b isolation plate, 107 intermediate reinforcing plate, 108 fundamental part, 109a to 109c channel hole, 110a, 110b corrugated shape, 111a to 111d narrowing portion, 112a to 112d heat nontransfer space.
Patent Grant
10161687
