JPWO2020194426A1 - Heat pump device equipped with water refrigerant heat exchanger and water refrigerant heat exchanger - Google Patents

Abstract

The water pipe 21 through which liquid water flows, and the refrigerant pipes 22a and 22b which are arranged in contact with the outer peripheral surface of the water pipe 21 and in which the refrigerant that exchanges heat with the water inside the water pipe 21 flows inside. The water pipe 21 is provided with a stirring plate made of a plate material that is arranged in the water pipe 21 and has a spiral shape along the shaft O1 of the water pipe 21. Therefore, by preferably stirring the water in the radial direction of the water pipe in the water pipe, the heat exchange efficiency between the refrigerant in the refrigerant pipe and the water near the shaft of the water pipe can be improved. A heat exchanger and a heat pump device using this water-refrigerant heat exchanger are obtained.

Description

The present invention relates to a water-refrigerant heat exchanger for heat exchange between water and a high-temperature refrigerant, and a heat pump device including a water-refrigerant heat exchanger.

Patent Document 1 discloses a technique relating to a heat exchanger for hot water supply used in a heat pump type water heater. The heat exchanger for hot water supply of this heat pump type water heater has a configuration in which a refrigerant pipe is wound around a water pipe and a twist plate is arranged in the water pipe. By arranging the twisting tape in the water pipe in this way, heat exchange between water and the refrigerant is promoted.

Japanese Unexamined Patent Publication No. 2005-221172

However, in the heat exchanger for hot water supply of the above heat pump type water heater, since the twisting tape is arranged in the water pipe, the cross section orthogonal to the axis of the water pipe is composed of the water pipe and the twisted tape. Two spaces forming an almost semi-circular shape are formed. The water in these two substantially semicircular spaces is difficult to agitate with each other or cannot be agitated with each other. That is, there is a problem that water cannot be sufficiently agitated in the water pipe in the radial direction of the water pipe, and as a result, the heat exchange efficiency is suppressed.

The present invention has been made to solve the above-mentioned problems, and by preferably stirring water in the radial direction of the water pipe in the water pipe, the shaft of the refrigerant and the water pipe in the refrigerant pipe An object of the present invention is to provide a water-refrigerant heat exchanger capable of improving heat exchange efficiency with nearby water, and a heat pump device using the water-refrigerant heat exchanger.

The heat pump device provided with the water refrigerant heat exchanger and the water refrigerant heat exchanger according to the present invention is arranged in contact with the water pipe through which liquid water flows and the outer peripheral surface of the water pipe, and is arranged inside the water pipe. It is provided with a refrigerant pipe in which a refrigerant that exchanges heat with the water of the above water flows inside, and a stirring member made of a plate material that is arranged in the water pipe and has a spiral shape along the axis of the water pipe.

The water-refrigerant heat exchanger according to the present invention and the heat pump device using the water-refrigerant heat exchanger preferably stir water in the radial direction of the water pipe in the water pipe to obtain a refrigerant in the refrigerant pipe. It is possible to improve the heat exchange efficiency between the water and the water near the shaft of the water pipe.

It is a front view which shows the internal structure of the heat pump apparatus of Embodiment 1. FIG. FIG. 5 is an external perspective view of the heat pump device of the first embodiment as viewed diagonally from the front. FIG. 5 is an external perspective view of the heat pump device of the first embodiment as viewed obliquely from behind. It is a figure which shows the refrigerant circuit and the water circuit of the heat pump hot water supply system provided with the heat pump device of Embodiment 1. FIG. FIG. 5 is an external perspective view of the water-refrigerant heat exchanger of the first embodiment as viewed from the front. It is a figure for demonstrating the main part of the water refrigerant heat exchanger of Embodiment 1. FIG. It is a figure for demonstrating the structure of the water pipe of Embodiment 1. FIG. It is a figure for demonstrating the structure of the water pipe of Embodiment 1. FIG. It is a figure for demonstrating the main part of the water refrigerant heat exchanger of Embodiment 1. FIG. It is a figure for demonstrating the water refrigerant heat exchanger of Embodiment 1. FIG. It is a figure for demonstrating the water refrigerant heat exchanger of Embodiment 1. FIG. It is a figure for demonstrating the stirring plate of Embodiment 1. FIG. It is a figure for demonstrating the water refrigerant heat exchanger of Embodiment 1. FIG. It is a figure for demonstrating the stirring plate of Embodiment 1. FIG. It is a figure for demonstrating the stirring plate of Embodiment 1. FIG. It is a figure for demonstrating the main part of the water refrigerant heat exchanger of Embodiment 2. It is a figure for demonstrating the main part of the water refrigerant heat exchanger of Embodiment 3. It is a figure for demonstrating the main part of the water refrigerant heat exchanger of Embodiment 4. It is a figure for demonstrating the main part of the water refrigerant heat exchanger of Embodiment 5. It is a figure for demonstrating the main part of the water refrigerant heat exchanger of Embodiment 6. It is a figure for demonstrating the main part of the water refrigerant heat exchanger of Embodiment 7. It is a figure for demonstrating the modification of the stirring plate used in embodiment of this invention. It is a figure for demonstrating the modification of the stirring plate used in embodiment of this invention. It is a figure for demonstrating the modification of the stirring plate used in embodiment of this invention. It is a figure for demonstrating the modification of the stirring plate used in embodiment of this invention. It is a figure for demonstrating the modification of the water refrigerant heat exchanger used in embodiment of this invention.

Embodiment 1.
The heat pump device provided with the water-refrigerant heat exchanger of the present invention will be described with reference to FIGS. 1 to 14.
FIG. 1 is a front view showing the internal structure of the heat pump device 1. FIG. 2 is an external perspective view of the heat pump device 1 as viewed diagonally from the front. FIG. 3 is an external perspective view of the heat pump device 1 as viewed diagonally from behind. FIG. 4 is a diagram showing a refrigerant circuit and a water circuit of a heat pump hot water supply system including the heat pump device 1.

The heat pump device 1 of the present embodiment is installed outdoors. The heat pump device 1 heats a liquid heat medium. The heat medium in this embodiment is water. The heat pump device 1 heats water to generate hot water. The heat medium in the present invention may be, for example, an aqueous solution of calcium chloride, an aqueous solution of ethylene glycol, alcohol or the like.

As shown in FIG. 1, the heat pump device 1 includes a base 17 that forms a bottom plate of a housing. On the base 17, a machine room 14 is formed on the right side and a blower room 15 is formed on the left side when viewed from the front. The machine room 14 and the blower room 15 are separated by a partition plate 16 extending in the vertical direction. As shown in FIGS. 2 and 3, the housing forming the outer shell of the heat pump device 1 further includes a front panel 18, a back panel 19, and a top panel 20 in addition to the base 17 described above. The front panel 18 is composed of a front surface portion 18a that covers the front surface portion of the housing and a left side surface portion 18b that covers the left side surface of the housing. Further, the back panel 19 is composed of a rear surface portion 19a that covers the rear surface portion of the housing and a right side surface portion 19b that covers the right side surface of the housing. The top panel 20 is configured to cover the upper surface of the housing. These components of the housing are molded from, for example, sheet metal material. The outer surface of the heat pump device 1 is covered by this housing except for the air refrigerant heat exchanger 7 arranged on the rear surface side. Note that FIG. 1 shows a state in which each part of the housing other than the base 17 is removed. Further, in FIG. 1, some constituent devices are not shown.

As shown in FIG. 1, in the machine room 14, as refrigerant circuit parts, a compressor 2 for compressing the refrigerant, an expansion valve 10 for reducing the pressure of the refrigerant (omitted in FIG. 1), a suction pipe 4 for connecting these, and a discharge are provided. A refrigerant pipe such as a pipe 5 is incorporated.

The compressor 2 includes a compression unit (not shown) and a motor (not shown) inside a cylindrical shell. The compression unit performs a compression operation of the refrigerant. The motor drives the compression unit. The motor of the compressor is driven by the electric power supplied from the outside. The refrigerant is sucked into the compressor 2 through the suction pipe 4. A discharge pipe 5 for discharging the refrigerant compressed inside the compressor 2 is connected to the upper part of the compressor 2. The expansion valve 10 (see FIG. 4) has a coil built-in member attached to the outer surface of the main body thereof. By energizing the coil from the outside, the internal flow path resistance adjusting unit is operated to adjust the flow path resistance of the refrigerant. The expansion valve 10 can adjust the pressure of the high-pressure refrigerant on the upstream side thereof and the pressure of the low-pressure refrigerant on the downstream side thereof. The expansion valve 10 is an example of a pressure reducing device that reduces the pressure of the refrigerant.

The blower room 15 has a larger space than the machine room 14 in order to secure an air passage. A blower 6 is incorporated in the blower room 15. The blower 6 includes two or three propeller blades and a motor for rotationally driving the propeller blades. The motor and propeller blades are rotated by the electric power supplied from the outside. On the rear surface side of the blower chamber 15, an air refrigerant heat exchanger 7 is installed facing the blower 6. The air refrigerant heat exchanger 7 includes a large number of aluminum thin plate fins and a long refrigerant pipe that comes into close contact with a large number of aluminum thin plate fins and reciprocates several times. Each fin has a vertically long rectangular shape, and is fixed to the refrigerant pipe in a state of being laminated with a minute gap in the horizontal direction. The air-refrigerant heat exchanger 7 has an L-shaped curved flat plate-shaped outer shape. The air refrigerant heat exchanger 7 is installed from the rear surface to the left side surface of the heat pump device 1. The rear end of the air-refrigerant heat exchanger 7 extends to the rear of the machine room 14. Therefore, the partition plate 16 has an L-shaped curved flat plate-shaped outer shape, and is installed so as to partition the space from the front surface of the heat pump device 1 to the rear end portion of the air refrigerant heat exchanger 7. .. In the air refrigerant heat exchanger 7, heat is exchanged between the refrigerant in the refrigerant pipe and the outside air taken in around the fins. The amount of air flowing between the fins and passing through the blower 6 is increased and adjusted, and the amount of heat exchange is increased and adjusted. The air refrigerant heat exchanger 7 is an example of an evaporator that evaporates the refrigerant.

A water-refrigerant heat exchanger 8 is installed on the base 17 at the bottom of the blower chamber 15. The water-refrigerant heat exchanger 8 is housed and installed in a rectangular parallelepiped-shaped storage container 12 in a state of being covered with a heat insulating material. The water-refrigerant heat exchanger 8 is formed by having a plurality of bent portions so that the water pipe and the refrigerant pipe can be stored in the storage container 12 in a state of being in close contact with each other. In the water-refrigerant heat exchanger 8, heat is exchanged between the refrigerant in the refrigerant pipe and the water in the water pipe. Water is heated in the water refrigerant heat exchanger 8. The configuration of the water-refrigerant heat exchanger 8 will be described later.

The outlet portion of the compressor 2 is connected to the refrigerant inlet portion of the water refrigerant heat exchanger 8 via the discharge pipe 5. The refrigerant outlet of the water-refrigerant heat exchanger 8 is connected to the inlet of the expansion valve 10 in the machine room 14 via a refrigerant pipe. The outlet portion of the expansion valve 10 is connected to the refrigerant inlet portion of the air refrigerant heat exchanger 7 via a refrigerant pipe. The refrigerant outlet portion of the air refrigerant heat exchanger 7 is connected to the inlet portion of the compressor 2 via the suction pipe 4. Other refrigerant circuit components may be attached in the middle of each refrigerant pipe.

An electric component storage box 9 is installed in the upper part of the machine room 14. An electronic board is stored in the electrical product storage box 9. Electronic components, electrical components, and the like that make up each module that drives and controls the compressor 2, the expansion valve 10, the blower 6, and the like are mounted on the electronic board. Each module is controlled as follows, for example. The rotation speed of the motor of the compressor 2 is changed to about several tens of rps (Hz) to 100 rps (Hz). The opening degree of the expansion valve 10 is changed. The rotation speed of the blower 6 is changed to a rotation speed of about several hundred rpm to 1,000 rpm. The electrical product storage box 9 is provided with a terminal block 9a for connecting external electrical wiring. As shown in FIGS. 2 and 3, a service panel 27 for protecting the terminal block 9a and the water inlet valve 28 and the hot water outlet valve 29, which will be described later, is attached to the right side surface portion 19b.

The refrigerant is sealed in the sealed space of the refrigerant circuit included in the heat pump device 1. The refrigerant is, for example, a CO ₂ refrigerant.

Next, the water circuits of the heat pump device 1 and the hot water storage device 33 will be described. As shown in FIG. 1, a water circuit component including an internal pipe 30 and an internal pipe 31 is incorporated in the machine room 14. On the right side of the base 17, both are arranged so that the water inlet valve 28 is on the lower side and the hot water outlet valve 29 is on the upper side. The internal pipe 30 connects the water inlet valve 28 and the water inlet portion of the water refrigerant heat exchanger 8. The internal pipe 31 connects between the hot water outlet portion of the water refrigerant heat exchanger 8 and the hot water outlet valve 29.

As shown in FIG. 4, the heat pump device 1 and the hot water storage device 33 constitute a heat pump hot water supply system. The hot water storage device 33 includes, for example, a hot water storage tank 34 having a capacity of about several hundred liters, and a water pump 35 for sending the water in the hot water storage tank 34 to the heat pump device 1. The heat pump device 1 and the hot water storage device 33 are connected via an external pipe 36, an external pipe 37, and electrical wiring (not shown).

The lower part of the hot water storage tank 34 is connected to the inlet of the water pump 35 via a pipe 38. The outer pipe 36 connects the outlet of the water pump 35 and the water inlet valve 28 of the heat pump device 1. The outer pipe 37 connects between the hot water outlet valve 29 of the heat pump device 1 and the hot water storage device 33. The external pipe 37 can communicate with the upper part of the hot water storage tank 34 via the pipe 39 in the hot water storage device 33.

The hot water storage device 33 further includes a mixing valve 40. The mixing valve 40 is connected to a hot water supply pipe 41 branched from the pipe 39, a water supply pipe 42 through which water supplied from a water source such as a water source passes, and a hot water supply pipe 43 through which hot water supplied to the user side passes. There is. The mixing valve 40 adjusts the hot water supply temperature by adjusting the mixing ratio of the hot water flowing from the hot water supply pipe 41, that is, the high temperature water, and the water flowing from the water supply pipe 42, that is, the low temperature water. The hot water mixed by the mixing valve 40 is sent to a terminal on the user side such as a bathtub, a shower, a faucet, and a dishwasher through a hot water supply pipe 43. A water supply pipe 44 branched from the water supply pipe 42 is connected to the lower part of the hot water storage tank 34. The water flowing in from the water supply pipe 44 is stored in the lower side of the hot water storage tank 34.

Next, the configuration of the water-refrigerant heat exchanger 8 will be described in detail with reference to FIGS. 5 to 15. FIG. 5 is an external perspective view of the water refrigerant heat exchanger 8 as viewed from the front.
The water-refrigerant heat exchanger 8 includes a water pipe 21 and a refrigerant pipe 22. The water pipe 21 and the refrigerant pipe 22 are circular pipes made of a metal such as copper. The cross section of the refrigerant pipe 22 has a circular shape. The low-temperature water sent from the hot water storage tank 34 flows through the water pipe 21. Further, a high-temperature and high-pressure refrigerant sent from the compressor 2 flows through the refrigerant pipe 22.

The water-refrigerant heat exchanger 8 is bent and molded so that it can be stored in the storage container 12 in a state where the water pipe 21 and the refrigerant pipe 22 are in close contact with each other. The water pipe 21 is bent and molded in a hollow shape. Since the water pipe 21 is bent, the water pipe 21 includes a curved pipe portion 21a which is a curved pipe portion and a straight pipe portion 21b which is a linear pipe portion. The water pipe 21 includes a plurality of curved pipe portions 21a and a plurality of straight pipe portions 21b. FIG. 6 is a diagram for explaining a main part of the water refrigerant heat exchanger 8. FIG. 6 shows an enlarged view of one end side of the contact portion, which is a region where the water pipe 21 and the refrigerant pipe 22 are in close contact with each other in the water refrigerant heat exchanger 8. Since the other end side of the close contact portion has the same shape as the one end side of the close contact portion shown in FIG. 6, the description thereof will be omitted.

FIG. 7 is a diagram for explaining the configuration of the water pipe 21 of the water refrigerant heat exchanger 8. In FIG. 7, the refrigerant pipe 22 is omitted in order to show the configuration of the water pipe 21. In the following description, the water inlet side (right side in FIG. 7) of the water refrigerant heat exchanger 8 is referred to as the water inlet side IS, and the heat exchange side of the water refrigerant heat exchanger 8 (left side in FIG. 7). ) Is referred to as the heat exchange unit side OS.
On the outer peripheral surface of the water pipe 21, two outer spiral grooves OG1 and OG2, which are continuous spiral grooves, are formed. The number of outer spiral grooves formed on the outer peripheral surface of the water pipe 21 is not limited to two, and may be one or three or more.
On the outer peripheral surface of the water pipe 21, outer spiral convex portions OH1 and OH2, which are spiral convex portions relatively formed by forming two outer spiral grooves OG1 and OG2, are formed. .. The outer peripheral spiral convex portion OH1 is formed so as to be located between the outer peripheral spiral groove OG1 and the outer peripheral spiral groove OG2. The outer peripheral spiral convex portion OH2 is formed so as to be located between the outer peripheral spiral groove OG2 and the outer peripheral spiral groove OG1.

The refrigerant pipe 22 is branched into a plurality of circular pipes in the middle so that a plurality of parallel flow paths are formed. In the example of the water-refrigerant heat exchanger 8 shown in FIG. 5, the refrigerant pipe 22 is branched into two refrigerant pipes 22a and 22b. As shown in FIGS. 6 and 7, the refrigerant pipe 22a is spirally wound around the outer periphery of the water pipe 21 along the outer peripheral spiral groove OG1 formed on the outer peripheral surface of the water pipe 21 by brazing or the like. It is joined. As shown in FIGS. 6 and 7, the refrigerant pipe 22b is spirally wound around the outer periphery of the water pipe 21 along the outer peripheral spiral groove OG2 formed on the outer peripheral surface of the water pipe 21 by brazing or the like. It is joined.
The number of refrigerant pipes to which the refrigerant pipe 22 branches is not limited to two, but may be one or three or more, and may correspond to the number of outer spiral grooves formed on the outer peripheral surface of the water pipe 21. More desirable.

FIG. 8 is a cross-sectional view of the straight pipe portion 21b parallel to the axis O1 of the straight pipe portion 21b of the water pipe 21. In FIG. 8, the refrigerant pipe 22 is omitted. In the example of the water refrigerant heat exchanger 8 shown in FIG. 8, two inner spiral grooves IG1 and IG2 are formed on the inner peripheral surface of the water pipe 21. The inner spiral groove IG1 is formed at a position corresponding to the outer spiral convex portion OH1 on the wall portion of the water pipe 21. The inner spiral groove IG2 is formed at a position corresponding to the outer spiral convex portion OH2 on the wall portion of the water pipe 21.

On the inner peripheral surface of the water pipe 21, two inner spiral grooves IG1 and IG2 are formed to form relatively formed spiral convex portions IH1 and IH2. Has been done. The inner peripheral spiral convex portion IH1 is formed so as to be located between the inner peripheral spiral groove IG1 and the inner peripheral spiral groove IG2. The inner peripheral spiral convex portion IH2 is formed so as to be located between the inner peripheral spiral groove IG2 and the inner peripheral spiral groove IG1.
The inner peripheral spiral convex portion IH1 is formed at a position corresponding to the outer peripheral spiral groove OG2 on the wall portion of the water pipe 21. The inner peripheral spiral convex portion IH2 is formed at a position corresponding to the outer peripheral spiral groove OG1 on the wall portion of the water pipe 21.

When molding the water pipe 21, a cylinder is used as a material, and by deforming the cylinder so as to twist around the axis of the cylinder, the inner peripheral spiral grooves IG1, IG2 and the inner circumference are formed on the inner peripheral surface of the cylinder. The spiral convex portions IH1 and IH2 can be formed, and the outer peripheral spiral grooves OG1 and OG2 and the outer peripheral spiral convex portions OH1 and OH2 can be formed on the outer peripheral surface of the cylinder. Therefore, the water pipe 21 having the inner peripheral spiral grooves IG1 and IG2, the inner peripheral spiral convex portions IH1 and IH2, the outer peripheral spiral grooves OG1 and OG2, and the outer peripheral spiral convex portions OH1 and OH2 can be formed at low cost.

FIG. 9 is an explanatory diagram showing the relationship between the refrigerant pipe 22, the water pipe 21, and the stirring plate 50. Note that in FIG. 9, the hatching for the cross section of the water pipe 21 and the refrigerant pipe 22 is omitted. FIG. 10 is an explanatory view showing the relationship between the water pipe 21 and the stirring plate 50 corresponding to the AA cross section of FIG. In FIG. 10, the refrigerant pipe 22 is not shown. FIG. 11 is an explanatory view showing the relationship between the water pipe 21 and the stirring plate 50, corresponding to the BB cross section of FIG. In FIG. 11, the refrigerant pipe 22 is not shown. FIG. 12 is an explanatory view of the stirring plate 50. FIG. 13 is an enlarged view of FIG. 9, and is an explanatory view showing the relationship between the refrigerant pipe 22, the water pipe 21, and the stirring plate 50.

As shown in FIG. 9, the water-refrigerant heat exchanger 8 includes a stirring plate 50 as a stirring member. The stirring plate 50 is composed of a plate material having a spiral shape along the shaft O1 of the water pipe 21. The shaft O1 is the shaft of the water pipe 21, the shaft of the curved pipe portion 21a, and the shaft of the straight pipe portion 21b. The surface of the stirring plate 50 is smooth. As shown in FIGS. 10 and 11, the projected outer peripheral image of the stirring plate 50 when viewed from the axis O1 direction has a circular shape. This plate material is a steel material, but a metal material such as a copper material or an aluminum material may be used. This plate material is an elongated plate. Since the stirring plate 50 can be formed by winding a steel plate, it can be formed at a lower cost than when it is formed by using a layered manufacturing method (so-called 3D printer). The stirring plate 50 having a spiral shape may be formed by a layered manufacturing method using a metal material such as a steel material, a copper material, or an aluminum material. The stirring plate formed by the additive manufacturing method can improve the molding accuracy of the shape as compared with the stirring plate formed by winding the steel plate material. In addition, as referred to in this specification, "a stirring plate made of a plate material exhibiting a spiral shape" means a stirring plate formed by winding a plate material and a stirring plate formed by a layered manufacturing method.

As shown in FIG. 12, one round of the stirring plate 50 with respect to the shaft O1 is defined as one stirring unit 51.
As shown in FIG. 12, there are at least two types of the stirring unit 51, a large-diameter stirring unit 51a and a small-diameter stirring unit 51b having an outer diameter smaller than that of the large-diameter stirring unit 51a. As shown in FIG. 13, the outer circumference of the large-diameter stirring unit 51a comes into contact with the inner peripheral spiral groove IG1. The size of the outer shape of the small-diameter stirring portion 51b is formed to be smaller than the inner diameters of the inner peripheral spiral convex portions IH1 and IH2.
As shown in FIG. 12, in the stirring plate 50, the ends of the three large-diameter stirring portions 51a are integrally connected to each other so as to be in series with the shaft O1. The three large-diameter stirring units 51a connected in series with the shaft O1 are referred to as a large-diameter stirring unit group Fa. The large-diameter stirring unit group Fa is composed of three large-diameter stirring units 51a in the first embodiment, but may be composed of one or more large-diameter stirring units 51a.

As shown in FIG. 13, the large-diameter stirring unit group Fa of the stirring plate 50 is in contact with the inner peripheral spiral groove IG1 of the water pipe 21, and as a result, the stirring plate 50 is positioned with respect to the water pipe 21. ..
In particular, the water-refrigerant heat exchanger 8 is configured so that the direction of rotation of the spiral of the inner peripheral spiral groove IG1 of the water pipe 21 and the direction of rotation of the spiral of the stirring plate 50 coincide with each other. That is, the inner peripheral spiral groove IG1 is configured to be a spiral that rotates clockwise from the water inlet side IS of the water pipe 21 toward the heat exchange part side OS, and the stirring plate 50 is the water pipe 21. It is configured to be a spiral that rotates clockwise from the IS on the water inlet side to the OS on the heat exchange part side. Therefore, a part of the large-diameter stirring portion group Fa of the stirring plate 50 meshes with the inner peripheral spiral groove IG1 of the water pipe 21, and the contact area between the water pipe 21 and the stirring plate 50 can be further secured, and the water pipe 21 can be secured. And the stirring plate 50 can be more preferably positioned.
Further, as shown in FIG. 11, the projected outer peripheral image of the stirring plate 50 when viewed from the axis O1 direction has a circular shape, and as shown in FIG. 11, when viewed from the axis O1 direction. The projected image of the inner peripheral spiral groove IG1 of the water pipe 21 has a circular shape. Therefore, the large-diameter stirring unit group Fa of the stirring plate 50 is positioned with respect to the inner peripheral spiral groove IG1 of the water pipe 21. When doing so, the contact area with the inner peripheral spiral groove IG1 can be further secured, and positioning can be preferably performed.

In the first embodiment, the large-diameter stirring unit group Fa of the stirring plate 50 is brazed to the inner peripheral surface (inner peripheral spiral groove IG1) of the water pipe 21. In this way, by fixing the diameter stirring part group Fa of the stirring plate 50 to the inner peripheral surface of the water pipe 21 by brazing or other fixing method, the water pipe 21 and the large diameter stirring part group Fa are relative to each other. The movement is suppressed, and the generation of sound due to the relative movement of the water pipe 21 and the large-diameter stirring unit group Fa and the generation of wear due to the occurrence of rubbing are suppressed.
The portion of the stirring plate 50 to be fixed to the inner surface of the water pipe 21 may be provided at a position where the curved pipe portion 21a of the water pipe 21 and the stirring plate 50 are easily displaced from the shaft O1 of the water pipe 21. In this case, the unevenness of the flow rate of water in the water pipe 21 is further suppressed, the difference in the amount of heat transfer from the refrigerant pipes 22a and 22b to the water pipe 21 is further suppressed, and the decrease in heat exchange efficiency is further suppressed. As a result, heat can be efficiently applied to the water flowing in the water pipe 21, so that the heating efficiency of the water flowing in the water pipe 21 can be increased.
If the large-diameter stirring part group Fa of the stirring plate 50 can be suitably positioned with respect to the inner peripheral spiral groove IG1 of the water pipe 21, the diameter stirring part group Fa of the stirring plate 50 may be placed on the inner circumference of the water pipe 21. It does not have to be fixed to the surface by brazing or other fixing method. As described above, when the diameter stirring part group Fa of the stirring plate 50 is not fixed to the inner peripheral surface of the water pipe 21 but only positioned, the cost for fixing and the manufacturing process can be reduced.

Further, as shown in FIG. 12, in the stirring plate 50, the ends of each of the four or more small-diameter stirring portions 51b are integrally connected to each other so as to be in series with the shaft O1. Four or more small-diameter stirring units 51b connected in series with the shaft O1 are referred to as a small-diameter stirring unit group Fb. The axis of the small-diameter stirring unit group Fb is configured to coincide with the shaft O1 of the water pipe 21, but it does not necessarily have to coincide with the shaft O1 of the water pipe 21. The water in the water pipe 21 enters and exits the inside and outside of the small diameter stirring unit group Fb through the gap of the small diameter stirring unit group Fb, and the water in the water pipe 21 is agitated.

In the first embodiment, the outer diameter of the water pipe 21 is 12 mm, the inner diameter of the water pipe 21 is 10 mm, the outer diameters of the refrigerant pipes 22a and 22b are 4 mm, the inner diameters of the refrigerant pipes 22a and 22b are 2 mm, and the stirring plate 50. The thickness of the plate material constituting the above is 0.5 mm, and the outer diameter of the small diameter stirring unit 51b is 8 mm, but the present invention is not limited to this, and these dimensions may be changed as appropriate.

FIG. 14 is a partially enlarged cross-sectional view taken along the axis O1 showing the relationship between the refrigerant pipe 22, the water pipe 21, and the stirring plate 50. As shown in FIG. 14, the plate material constituting the stirring plate 50 has a short side S and a long side L in a cross section along the axis O1. The long side L is arranged along the axis O1.
As shown in FIG. 12, in a plurality of small-diameter stirring units 51b constituting the small-diameter stirring unit group Fb, the distance K between adjacent short sides S along the axis O1 is larger than the length of the long side L of the small-diameter stirring unit 51b. Is also long composed. As described above, since the distance K between the adjacent short sides S is longer than the long side L of the small diameter stirring unit 51b, the distance between the adjacent short sides S is longer than the long side L of the small diameter stirring unit 51b. Compared to the case where K is shorter, it promotes the flow of water entering and exiting the inside and outside of the small diameter stirring unit group Fb through the gap of the small diameter stirring unit group Fb (see FIG. 12), and promotes the flow of water in and out of the small diameter stirring unit group Fb, and in the water pipe 21. Water can be agitated even more preferably.
It is desirable that the small-diameter stirring unit group Fb is configured so that the length of the interval K is shorter than three times the diameter of the small-diameter stirring unit 51b. The distance K between the short sides S is the distance between the adjacent stirring portions 51 in the axis O1 direction. Further, the width between the short sides S is the length of the long sides L connected to both short sides S.

Further, since the long side L of the plate material constituting the stirring plate 50 is arranged along the axis O1, the long side L does not face the water flow, but the short side S faces the water flow. Have been placed. Since the short side S is arranged so as to face the flow of water, it is possible to suppress a decrease in the flow path area of the water pipe 21 as compared with the case where the long side L faces the flow of water, and the flow of water can be suppressed. The heat exchange efficiency can be improved while suppressing the increase in pressure loss.
Further, as described above, the decrease in the flow path area of the water pipe 21 can be suppressed, it is not necessary to use a water pump having a high output in order to secure a predetermined water flow rate, and a significant increase in cost is suppressed. Further, since the water pipe 21 is long and has a plurality of curved pipe portions 21a (see FIG. 5), the axis of the small diameter stirring portion group Fb of the stirring plate 50 may deviate from the axis O1 of the water pipe 21. However, since the increase in pressure loss of the water flow is suppressed, the unevenness of the flow rate of water in the water pipe 21 is suppressed, and the water temperature and the refrigerant pipes 22a and 22b to the water pipe 21 in the circumferential direction of the water pipe 21 are suppressed. The difference in the amount of heat transfer is suppressed, and the improvement in heat exchange efficiency is not suppressed. Therefore, in the water refrigerant heat exchanger 8, the decrease in the water flow path area in the water pipe 21 is suppressed, the increase in the pressure loss of the water flow is suppressed, and the water pipe diameter for ensuring the water flow rate is large. It is possible to improve the heat exchange efficiency between water and the refrigerant while suppressing the increase in cost due to the increase in diameter and the accompanying increase in the size of the housing.

As shown in FIG. 12, in the stirring plate 50, the large-diameter stirring unit group Fa and the small-diameter stirring unit group Fb are alternately connected in series with the shaft O1. The stirring plate 50 is configured such that the length along the axis O1 in one large-diameter stirring unit group Fa is shorter than the length along the axis O1 in one small-diameter stirring unit group Fb. The reason for this configuration is that the large-diameter stirring unit group Fa is for fixing or positioning the stirring plate 50 with respect to the water pipe 21, and the large-diameter stirring unit group Fa constituting the large-diameter stirring unit group Fa. This is because it is desired to reduce the number of stirring units 51a as much as possible and increase the number of small diameter stirring units 51b constituting the small diameter stirring unit group Fb for stirring the water in the water pipe 21.

The water-refrigerant heat exchanger 8 of the first embodiment configured as described above can exert the following effects. Note that FIG. 15 is a diagram for explaining the operation and effect of the first embodiment, and is a partially enlarged cross-sectional view along a shaft O1 showing the relationship between the refrigerant pipe 22, the water pipe 21, and the stirring plate 50.
Refrigerant pipes 22a and 22b are fixed to the outer peripheral surface of the water pipe 21. Therefore, for example, when water is flowed into the water pipe 21 in a state where nothing is arranged inside the water pipe 21, the water flowing near the axis O1 of the water pipe 21 is the water near the inner peripheral surface of the water pipe 21. Compared to the above, it is difficult to exchange heat with the refrigerant flowing in the refrigerant pipes 22a and 22b.

On the other hand, in the water-refrigerant heat exchanger 8 of the first embodiment, as shown in FIG. 15, when paying attention to one cross-sectional portion of the small-diameter stirring portion 51b, it is different from the water inlet side IS of the cross-sectional portion. , The heat exchange portion side OS of the cross-sectional portion, the inner peripheral side of the cross-sectional portion, and the outer peripheral side of the cross-sectional portion have spaces. Therefore, when water flows from the water inlet side IS to the heat exchange part side OS in the water pipe 21, the Karman vortex KW flows in the water flowing on the inner peripheral side and the outer peripheral side of the cross-sectional portion of the small diameter stirring unit 51b. Occurs. When such Kalman vortex KW is generated at each part of the small-diameter stirring unit group Fb, the water flowing in the water pipe 21 goes out from the small-diameter stirring unit group Fb to the outside of the small-diameter stirring unit group Fb, or small-diameter stirring. It enters the small-diameter stirring part group Fb from the outside of the part group Fb. That is, in the water pipe 21, water is preferably agitated in the radial direction of the water pipe 21. In other words, the water near the shaft O1 of the water pipe 21 having low heat exchange efficiency and the water near the inner peripheral surface of the water pipe 21 having high heat exchange efficiency flow while being agitated by the small diameter stirring unit group Fb. The heat exchange efficiency between the water flowing in the 21 and the refrigerant flowing in the refrigerant pipes 22a and 22b is improved.

In the water refrigerant heat exchanger 8 of the first embodiment, the large-diameter stirring unit group Fa and the small-diameter stirring unit group Fb are alternately connected. Since the large-diameter stirring unit group Fa is brazed to the inner peripheral surface (inner peripheral spiral groove IG1) of the water pipe 21, the refrigerant in the refrigerant pipes 22a and 22b, the refrigerant pipes 22a and 22b, and the water pipe 21 , The large-diameter stirring unit group Fa, and the small-diameter stirring unit group Fb are thermally conducted in this order. Therefore, the small-diameter stirring unit group Fb can transfer the heat electrically conducted from the large-diameter stirring unit group Fa to the water around the small-diameter stirring unit group Fb, and the water and the refrigerant flowing in the water pipe 21 can be transferred. The heat exchange efficiency with the refrigerant flowing in the pipes 22a and 22b can be further improved.

In the refrigerant heat exchanger 8, as shown in FIG. 13, the refrigerant pipes 22a and 22b are configured to come into contact with the water pipe 21 along the outer peripheral spiral grooves OG1 and OG2. Therefore, since the outer peripheral spiral grooves OG1 and OG2 are formed on the outer peripheral surface of the water pipe 21, the outer peripheral spiral grooves OG1 and OG2 of the water pipe 21 have no groove as compared with the case where there is no groove on the outer peripheral surface of the water pipe 21. When the refrigerant pipes 22a and 22b are brought into contact with each other, the contact area can be increased, and as a result, the heat exchange efficiency between water and the refrigerant can be improved.

Further, in the heat exchanger for hot water supply of the heat pump type water heater of Patent Document 1, two substantially semicircular spaces formed by a water pipe and a twisting tape are formed. Water flowing through this semicircular space is unlikely to be agitated. Therefore, among those contributing to heat exchange from the refrigerant to water flowing through the semicircular space, the ratio of heat exchange by heat conduction is large and the ratio of heat exchange by stirring is small. Of those that contribute to heat exchange from the refrigerant to water flowing through the semicircular space, the fact that the ratio of heat exchange due to heat conduction is large means that the area of the flow path of water flowing in the water pipe is reduced accordingly. It ends up.
On the other hand, in the water-refrigerant heat exchanger 8 of the first embodiment, since the water in the water pipe 21 is suitably agitated by the small-diameter stirring unit group Fb of the stirring plate 50, the water flowing from the refrigerant in the water pipe 21 Among those contributing to heat exchange to, the ratio of heat exchange by heat conduction is smaller than that of Patent Document 1, and the ratio of heat exchange by stirring is larger than that of Patent Document 1.
Therefore, the water refrigerant heat exchanger 8 of the first embodiment contributes to heat exchange from the refrigerant to the water flowing in the water pipe 21 as compared with the hot water supply heat exchanger of the heat pump type water heater of the cited document 1. By increasing the ratio of heat exchange by stirring, the decrease in the flow path area of the water pipe 21 can be suppressed, and the heat exchange efficiency can be improved while suppressing the increase in the pressure loss of the water flow. can. Further, as described above, the decrease in the flow path area of the water pipe 21 can be suppressed, it is not necessary to use a water pump having a high output in order to secure a predetermined water flow rate, and a significant increase in cost is suppressed. In addition, the water refrigerant heat exchanger 8 suppresses a decrease in the water flow path area in the water pipe 21 as compared with the hot water supply heat exchanger of the heat pump type water heater of Reference 1, and the flow of water is suppressed. To improve the heat exchange efficiency between water and refrigerant while suppressing the increase in pressure loss, increasing the diameter of the water pipe to secure the water flow rate, and suppressing the cost increase due to the increase in the size of the housing. Can be done.

Embodiment 2.
The heat pump device provided with the water-refrigerant heat exchanger according to the second embodiment of the present invention will be described with reference to FIG. In the heat pump device provided with the water-refrigerant heat exchanger of the second embodiment, the configuration of the water-refrigerant heat exchanger 58 is different from the configuration of the water-refrigerant heat exchanger 8 of the first embodiment. For other configurations, the same parts are designated by the same reference numerals, and detailed description thereof will be omitted. FIG. 16 is an explanatory diagram showing the relationship between the refrigerant pipe 22, the water pipe 21, and the stirring plate 60 in the water refrigerant heat exchanger 58.

The stirring plate 60 as the stirring member of the second embodiment corresponds to the small diameter stirring unit group Fb of the first embodiment over the entire length. That is, the stirring plate 60 is composed of a plate material having a spiral shape along the shaft O1 of the water pipe 21. The surface of the stirring plate 60 is smooth. The projected outer peripheral image of the stirring plate 60 when viewed from the axis O1 direction has a circular shape. The size of the outer shape of the stirring plate 60 is configured to be smaller than the inner diameters of the inner peripheral spiral convex portions IH1 and IH2. It should be noted that one round of the stirring plate 60 with reference to the shaft O1 is defined as one stirring unit 61.
Since the stirring plate 60 is arranged meandering along the shaft O1, it is in contact with the inner peripheral spiral groove IG1 or the inner peripheral spiral groove IG2 of the water pipe 21, and as a result, the stirring plate 50 is in contact with the water pipe 21. Is positioned with respect to.

In particular, the water-refrigerant heat exchanger 8 is configured so that the direction of rotation of the spiral of the inner peripheral spiral groove IG1 or the inner peripheral spiral groove IG2 of the water pipe 21 and the direction of rotation of the spiral of the stirring plate 50 match. Has been done. Therefore, a part of the stirring plate 60 meshes with the inner peripheral spiral groove IG1 or the inner peripheral spiral groove IG2 of the water pipe 21, and the contact area between the water pipe 21 and the stirring plate 60 can be further secured. Positioning with the stirring plate 60 can be performed even more preferably.

In the second embodiment, the stirring plate 60 is brazed to the inner peripheral surface (inner peripheral spiral groove IG1 or inner peripheral spiral groove IG2) of the water pipe 21. In this way, by fixing the stirring plate 60 to the inner peripheral surface of the water pipe 21 by brazing or other fixing method, the relative movement between the water pipe 21 and the stirring plate 60 is suppressed, and the water pipe 21 and the water pipe 21 The generation of sound due to the generation of contact due to the relative movement with the stirring plate 60 and the generation of wear due to the generation of rubbing are suppressed.
If the stirring plate 60 can be suitably positioned with respect to the inner peripheral spiral groove IG1 or the inner peripheral spiral groove IG2 of the water pipe 21, the stirring plate 60 may be brazed or brazed to the inner peripheral surface of the water pipe 21. It does not have to be fixed by other fixing methods. As described above, when the stirring plate 60 is not fixed to the inner peripheral surface of the water pipe 21 but only positioned, the cost for fixing and the manufacturing process can be reduced.

In the second embodiment, the diameter of the stirring plate 60 is 8 mm, but the diameter is not limited to this, and these dimensions may be changed as appropriate.
As shown in FIG. 16, the stirring portion 61 of the stirring plate 60 has a short side S and a long side L in a cross section along the shaft O1. In a state where the stirring plate 60 is arranged in a serpentine manner along the shaft O1, the angle α1 formed by the long side L of the stirring unit 61 and the shaft O1 is the angle formed by the short side S of the stirring unit 61 and the shaft O1. It is arranged so as to be smaller than α2.

Further, the distance K between the short sides S adjacent to each other along the axis O1 in the stirring unit 61 is longer than the length of the long side L of the stirring unit 61. It is desirable that the stirring unit 61 is configured so that the length of the interval K is shorter than the length of three times the diameter of the stirring unit 61.
Further, since the stirring plate 60 is arranged so that the angle α1 of the long side L with respect to the axis O1 is smaller than the angle α2 of the short side S with respect to the axis O1, the short side S is water rather than the long side L. Facing the flow. Since the short side S faces the water flow rather than the long side L, the inside of the water pipe 21 by the stirring plate 60 is compared with the case where the long side L faces the water flow rather than the short side S. The decrease in the water flow path area is suppressed, the increase in pressure loss of the water flow is suppressed, the diameter of the water pipe is increased to secure the water flow rate, and the cost associated with the increase in the size of the housing is increased. It is possible to improve the heat exchange efficiency between water and the refrigerant while suppressing the increase.

Since the stirring plate 60 is arranged in a meandering manner along the shaft O1, the water flowing in the water pipe 21 flows while being further vigorously stirred at the meandering shape of the stirring plate 60. As a result, the water in the water pipe 21 is more preferably agitated in the radial direction of the water pipe 21, so that the heat exchange efficiency between the refrigerant in the refrigerant pipe 22 and the water in the vicinity of the shaft O1 of the water pipe 21 is improved. Can be further improved.

The stirring plate 60 of the water refrigerant heat exchanger 58 of the first embodiment is brazed to the inner peripheral surface of the water pipe 21. Therefore, the heat of the refrigerant is thermally conducted in the order of the refrigerant in the refrigerant pipes 22a and 22b, the refrigerant pipes 22a and 22b, the water pipe 21, the large-diameter stirring unit group Fa, and the small-diameter stirring unit group Fb. Therefore, the stirring plate 60 can transfer the heat electrically conducted from the water pipe 21 to the water around the stirring plate 60, and flows in the water flowing in the water pipe 21 and in the refrigerant pipes 22a and 22b. The heat exchange efficiency with the refrigerant can be further improved.

Further, in the heat exchanger for hot water supply of the heat pump type water heater of Patent Document 1, two substantially semicircular spaces formed by a water pipe and a twisting tape are formed. Water flowing through this semicircular space is unlikely to be agitated. Therefore, among those contributing to heat exchange from the refrigerant to water flowing through the semicircular space, the ratio of heat exchange by heat conduction is large and the ratio of heat exchange by stirring is small. Of those that contribute to heat exchange from the refrigerant to water flowing through the semicircular space, the fact that the ratio of heat exchange due to heat conduction is large means that the area of the flow path of water flowing in the water pipe is reduced accordingly. It ends up.
On the other hand, in the water refrigerant heat exchanger 58 of the second embodiment, since the water in the water pipe 21 is suitably agitated by the stirring plate 60, it contributes to heat exchange from the refrigerant to the water flowing in the water pipe 21. Among those to be used, the ratio of heat exchange by heat conduction is smaller than that of Patent Document 1, and the ratio of heat exchange by stirring is larger than that of Patent Document 1.
Therefore, the water refrigerant heat exchanger 58 of the second embodiment contributes to heat exchange from the refrigerant to the water flowing in the water pipe 21 as compared with the hot water supply heat exchanger of the heat pump type water heater of the cited document 1. By increasing the ratio of heat exchange by stirring, the decrease in the flow path area of the water pipe 21 can be suppressed, and the heat exchange efficiency can be improved while suppressing the increase in the pressure loss of the water flow. can. Further, as described above, the decrease in the flow path area of the water pipe 21 can be suppressed, it is not necessary to use a water pump having a high output in order to secure a predetermined water flow rate, and a significant increase in cost is suppressed. In addition, the water refrigerant heat exchanger 58 suppresses a decrease in the water flow path area in the water pipe 21 as compared with the hot water supply heat exchanger of the heat pump type water heater of Reference 1, and the flow of water is suppressed. To improve the heat exchange efficiency between water and refrigerant while suppressing the increase in pressure loss, increasing the diameter of the water pipe to secure the water flow rate, and suppressing the cost increase due to the increase in the size of the housing. Can be done.

Embodiment 3.
The heat pump device provided with the water-refrigerant heat exchanger according to the third embodiment of the present invention will be described with reference to FIG. In the heat pump device provided with the water-refrigerant heat exchanger of the fourth embodiment, the configuration of the water-refrigerant heat exchanger 68 is different from the configuration of the water-refrigerant heat exchanger 8 of the first embodiment. For other configurations, the same parts are designated by the same reference numerals, and detailed description thereof will be omitted.

FIG. 17 is an explanatory diagram showing the relationship between the refrigerant pipe 22, the water pipe 21, and the stirring plate 50 in the water refrigerant heat exchanger 68.
The refrigerant heat exchanger 68 includes two stirring plates 50 according to the first embodiment. The large-diameter stirring unit group Fa of one stirring plate 50 is in contact with the inner peripheral spiral groove IG1 of the water pipe 21, and as a result, the stirring plate 50 is positioned with respect to the water pipe 21 and fixed by brazing. Has been done. The large-diameter stirring unit group Fa of the other stirring plate 50 is in contact with the inner spiral groove IG2 of the water pipe 21, and as a result, the stirring plate 50 is positioned with respect to the water pipe 21 and is brazed. It is fixed. The brazing of the stirring plate 50 and the inner spiral groove IG1 and the brazing of the stirring plate 50 and the inner spiral groove IG2 may be omitted.

That is, the two stirring plates 50 are arranged in a two-row state in the water pipe 21.
In the fourth embodiment, two stirring plates 50 are arranged in a two-row state in the water pipe 21, but the present invention is not limited to this, and three or more stirring plates 50 are arranged in the water pipe 21 in a multi-row state. It may be configured to be arranged in a state. That is, "in the water pipe 21, a plurality of stirring plates 50 are arranged in any one of the two-row state, the three-row state, the four-row state, and the five-row state" means "water pipe. Inside, a plurality of stirring plates are arranged so as to overlap in the direction along the axis of the water pipe. "
With this configuration, since the two stirring plates 50 are arranged in the water pipe 21 in a two-row state, water is compared with the case where one stirring plate 50 is arranged in the water pipe 21. The water flowing in the pipe 21 can be flowed while being agitated in a more complicated manner. As a result, by more preferably stirring the water in the radial direction of the water pipe 21 in the water pipe 21, the heat exchange efficiency between the refrigerant in the refrigerant pipe 22 and the water in the vicinity of the shaft O1 of the water pipe 21 is achieved. Can be further improved.

Embodiment 4.
The heat pump device provided with the water-refrigerant heat exchanger according to the fourth embodiment of the present invention will be described with reference to FIG. In the heat pump device provided with the water-refrigerant heat exchanger of the fourth embodiment, the configuration of the water-refrigerant heat exchanger 78 is different from the configuration of the water-refrigerant heat exchanger 8 of the first embodiment. For other configurations, the same parts are designated by the same reference numerals, and detailed description thereof will be omitted.

FIG. 18 is an explanatory diagram showing the relationship between the refrigerant pipe 22, the water pipe 21, and the stirring plate 80 in the water refrigerant heat exchanger 78.
The refrigerant heat exchanger 78 includes a stirring plate 80 as two stirring members. The surface of the stirring plate 80 is smooth. Both stirring plates 80 are arranged in the water pipe 21 in a direction orthogonal to the axis O1. The stirring plate 80 corresponds to the stirring plate 60 of the third embodiment, and is arranged meandering along the axis O1. Since the method of fixing the stirring plate 80 to the water pipe 21 (positioning method) is the same as that of the second embodiment, the description thereof will be omitted.

In the fourth embodiment, the refrigerant heat exchanger is provided with two stirring plates 80, but the present invention is not limited to this, and a plurality of three or more may be provided. With this configuration, when two stirring plates 80 are arranged in the water pipe 21 in a direction orthogonal to the shaft O1, one stirring plate 80 is arranged on the shaft O1 in the water pipe 21. In comparison with the above, the water flowing in the water pipe 21 can be flowed while being agitated in a more complicated manner. As a result, by more preferably stirring the water in the radial direction of the water pipe 21 in the water pipe 21, the heat exchange efficiency between the refrigerant in the refrigerant pipe 22 and the water in the vicinity of the shaft O1 of the water pipe 21 is achieved. Can be further improved.

Embodiment 5.
A heat pump device including the water-refrigerant heat exchanger according to the fifth embodiment of the present invention will be described with reference to FIG. In the heat pump device provided with the water-refrigerant heat exchanger of the fifth embodiment, the configuration of the water-refrigerant heat exchanger 88 is different from the configuration of the water-refrigerant heat exchanger 8 of the first embodiment. For other configurations, the same parts are designated by the same reference numerals, and detailed description thereof will be omitted.

FIG. 19 is an explanatory diagram showing the relationship between the refrigerant pipe 22, the water pipe 21, and the stirring plates 90, 91 in the water refrigerant heat exchanger 88.
The refrigerant heat exchanger 88 includes two stirring plates 90 and 91 as stirring members. The stirring plates 90 and 91 are made of a plate material having a spiral shape along the shaft O1 of the water pipe 21. The surfaces of the stirring plates 90 and 91 are smooth. As shown in FIG. 19, the projected outer peripheral images of the stirring plates 90 and 91 when viewed from the axis O1 direction have a circular shape.

The outer shape of the stirring plate 91 is configured to be smaller than the inner shape of the stirring plate 90. A stirring plate 90 is arranged along the shaft O1 in the water pipe 21, and a stirring plate 90 is arranged along the shaft O1 in the stirring plate 90.
With this configuration, in the water pipe 21, the stirring plate 91 is arranged in the stirring plate 90, so that one stirring plate 80 is arranged in the water pipe 21 on the shaft O1 as compared with the case where one stirring plate 80 is arranged in the shaft O1. Therefore, the water flowing in the water pipe 21 can be flowed while being agitated in a more complicated manner. As a result, by more preferably stirring the water in the radial direction of the water pipe 21 in the water pipe 21, the heat exchange efficiency between the refrigerant in the refrigerant pipe 22 and the water in the vicinity of the shaft O1 of the water pipe 21 is achieved. Can be further improved.

Embodiment 6.
A heat pump device including the water-refrigerant heat exchanger according to the sixth embodiment of the present invention will be described with reference to FIG. In the heat pump device provided with the water-refrigerant heat exchanger of the sixth embodiment, the configuration of the water-refrigerant heat exchanger 98 is different from the configuration of the water-refrigerant heat exchanger 8 of the first embodiment. For other configurations, the same parts are designated by the same reference numerals, and detailed description thereof will be omitted.

FIG. 20 is an explanatory diagram showing the relationship between the refrigerant pipe 22, the water pipe 21, and the stirring plate 50 in the water refrigerant heat exchanger 98.
The refrigerant heat exchanger 98 includes a plurality of stirring plates 50 according to the first embodiment. The stirring plates 50 are arranged so as to be adjacent to each other along the shaft O1 in the water pipe 21.
That is, the length of the stirring plate 50 of the sixth embodiment in the shaft O1 direction is shorter than the length of the stirring plate 50 of the first embodiment in the shaft O1 direction, and the number of stirring plates 50 is increased in the water pipe 21 by that amount. By being arranged, the water-refrigerant heat exchanger 98 of the sixth embodiment has the same function and effect as the water-refrigerant heat exchanger 8 of the first embodiment.
Further, the total length of the stirring plate 50 of the sixth embodiment in the shaft O1 direction is shorter than the total length of the stirring plate 50 of the first embodiment in the shaft O1 direction, so that the length of the stirring plate 50 of the sixth embodiment is shorter than the total length of the stirring plate 50 in the shaft O1 direction. Since the stirring plate 50 can be manufactured using a plate material shorter than that of the stirring plate 50 of the first embodiment, the stirring plate 50 can be manufactured at low cost.

Embodiment 7.
A heat pump device including the water-refrigerant heat exchanger according to the seventh embodiment of the present invention will be described with reference to FIG. In the heat pump device provided with the water-refrigerant heat exchanger of the seventh embodiment, the configuration of the water-refrigerant heat exchanger 108 is different from the configuration of the water-refrigerant heat exchanger 8 of the first embodiment. For other configurations, the same parts are designated by the same reference numerals, and detailed description thereof will be omitted.

FIG. 21 is an explanatory diagram showing the relationship between the water pipe 21 and the stirring plate 50 in the water refrigerant heat exchanger 108. In FIG. 21, the refrigerant pipe 22 is not shown for convenience of explanation. Further, in FIG. 21, the inner peripheral spiral grooves IG1 and IG2, the inner peripheral spiral convex portions IH1 and IH2, the outer peripheral spiral grooves OG1 and OG2, and the outer peripheral spiral convex portions OH1 and OH2 of the water pipe 21 are not shown.
The refrigerant heat exchanger 108 includes a plurality of stirring plates 50 according to the first embodiment. Each stirring plate 50 is arranged only in the straight pipe portion 21b in the water pipe 21.
With this configuration, the water-refrigerant heat exchanger 108 of the seventh embodiment has the same effect as that of the first embodiment. In addition, when the stirring plate 50 is arranged at a plurality of predetermined positions of the water pipe 21 instead of arranging the stirring plate 50 in the entire area of the water pipe 21 for cost reduction, the stirring plate 50 is arranged in the straight pipe portion 21b. It is desirable to place 50. When the stirring plate 50 is arranged in the straight pipe portion 21b, the axis of the small-diameter stirring portion group Fb of the stirring plate 50 tends to be along the axis O1, and as a result, the distance between the outer shape of the stirring plate 50 and the inner peripheral surface of the water pipe 21. However, it becomes uniform over the entire circumference of the inner peripheral surface of the water pipe 21, and the water entering and exiting the inside and outside of the small-diameter stirring unit group Fb can be uniformly agitated over the entire circumference of the inner peripheral surface of the water pipe 21.

In each of the above embodiments, the projected outer peripheral image of the stirring plates 50, 60, 80, 90, 91 when viewed from the axis O1 direction has a circular shape. Not limited to this, the projected outer peripheral images of the stirring plates 50, 60, 80, 90, 91 when viewed from the axis O1 direction are hexagonal as shown in FIG. 22 and elliptical as shown in FIG. 23. It may be formed into any one of a polygon and a regular polygon. In this way, the projected outer peripheral image of the stirring plates 50, 60, 80, 90, 91 when viewed from the axis O1 direction is formed into any one of an elliptical shape, a polygonal shape, and a regular polygonal shape. Then, since the outer shape changes in the circumferential direction of the spiral compared to the case where the image is formed in a circular shape, the flow of water entering and exiting the inside and outside of the stirring plates 50, 60, 80, 90, 91 is complicated. Therefore, the water in the water pipe 21 can be agitated more preferably.
The output of the compressor 2 of the heat pump device 1, the performance of the air refrigerant heat exchanger 7, the performance of the water refrigerant heat exchanger 8, the length of the water pipe 21, the physical properties of the refrigerant, etc., and the setting of the heat pump device 1. A stirring plate is provided for the temperature gradient characteristics of water in the axis O1 direction of the water pipe 21 and the temperature gradient characteristics of the refrigerant in the refrigerant pipe 22 in the shaft O1 direction of the water pipe 21 determined by the boiling capacity, the set boiling temperature, etc. It may be changed to the optimum shape.

The surfaces of the stirring plates 50, 60, 80, 90, 91 of each of the above embodiments are smooth, but the surface is not limited to this, and as shown in FIG. 24, the stirring plates 50, 60, 80, Concavities and convexities D may be formed on the surfaces of 90 and 91. With this configuration, the flow of water entering and exiting the inside and outside of the stirring plates 50, 60, 80, 90, 91 becomes complicated, and the water is further stirred in the water pipe 21 in the radial direction of the water pipe 21. When this is performed appropriately, the heat exchange efficiency between the refrigerant in the refrigerant pipe 22 and the water in the vicinity of the shaft O1 of the water pipe 21 can be further improved.

FIG. 25 is a diagram of another embodiment corresponding to the AA cross section of FIG. 9, and is an explanatory diagram showing the relationship between the water pipe 21 and the stirring plates 50, 60, 80, 90, 91. In FIG. 25, the refrigerant pipe 22 is not shown. Edges R may be formed at both ends in the circumferential direction of the cross section perpendicular to the axis O1 in the stirring plates 50, 60, 80, 90, 91 of each of the above embodiments. That is, at the end of the long side L of the stirring plates 50, 60, 80, 90, 91, an edge portion R rising from the long side L is formed. With this configuration, water entering and exiting the inside and outside of the stirring plates 50, 60, 80, 90, 91 collides with the edge R, complicating the flow of water, and in the water pipe 21, the radial direction of the water pipe 21. By more preferably stirring the water in the water pipe 22, the heat exchange efficiency between the refrigerant in the refrigerant pipe 22 and the water in the vicinity of the shaft O1 of the water pipe 21 can be further improved.

In the stirring plates 50, 60, 80, 90, 91 of each of the above embodiments, the outer dimensions of the stirring portions constituting the stirring plate may be different from each other. With this configuration, the flow of water entering and exiting the inside and outside of the stirring plates 50, 60, 80, 90, 91 becomes complicated, and the water is further stirred in the water pipe 21 in the radial direction of the water pipe 21. When this is performed appropriately, the heat exchange efficiency between the refrigerant in the refrigerant pipe 22 and the water in the vicinity of the shaft O1 of the water pipe 21 can be further improved.
For example, in a place where the temperature difference between water and the refrigerant is small and the temperature of water is low, the heating efficiency effect by stirring the water is low. Since the heating efficiency effect of stirring water is high in a place where the temperature of water is high, the stirring plates 50, 60, 80, 90, 91 may be configured as a large outer shape. In this case, the decrease in the flow path area due to the stirring plates 50, 60, 80, 90, 91 at the place where the water temperature is low is further suppressed, and the water is agitated violently at the place where the water temperature is high. As a result, the pressure loss of the water flow in the water pipe 21 can be further suppressed, and heat can be efficiently applied to the water flowing in the water pipe 21, so that the heating efficiency of the water flowing in the water pipe 21 can be improved. It will be possible.

In the stirring plates 50, 60, 80, 90, 91 of each of the above embodiments, the length of the long side or the distance between the short sides of the stirring portion constituting the stirring plate may be different from each other. With this configuration, the flow of water entering and exiting the inside and outside of the stirring plates 50, 60, 80, 90, 91 becomes complicated, and the water is further stirred in the water pipe 21 in the radial direction of the water pipe 21. When this is performed appropriately, the heat exchange efficiency between the refrigerant in the refrigerant pipe 22 and the water in the vicinity of the shaft O1 of the water pipe 21 can be further improved.
In addition, the output of the compressor 2 of the heat pump device 1, the performance of the air refrigerant heat exchanger 7, the performance of the water refrigerant heat exchanger 8, the length of the water pipe 21, the physical properties of the refrigerant, etc., and the heat pump device 1. A stirring plate for the temperature gradient characteristics of water in the axis O1 direction of the water pipe 21 and the temperature gradient characteristics of the refrigerant in the refrigerant pipe 22 in the axis O1 direction of the water pipe 21 determined by the set boiling capacity, the set boiling temperature, etc. The length of the long side or the distance between the short sides of the stirring part constituting the above may be changed optimally with each other. Since the effect is low, the distance between the short sides is set to be long, and in places where the temperature difference between water and the refrigerant is large and the temperature of the water is high, the heating efficiency effect by stirring the water is high, so even if the distance between the short sides is set short. good. In this case, the decrease in the water flow path area is further suppressed in the place where the water temperature is low, and the water is agitated violently in the place where the water temperature is high. As a result, the pressure loss of the water flow in the water pipe 21 can be further suppressed, and heat can be efficiently applied to the water flowing in the water pipe 21, so that the heating efficiency of the water flowing in the water pipe 21 can be improved. It will be possible.

The water pipe 21 of each of the above embodiments includes outer peripheral spiral grooves OG1 and OG2, outer peripheral spiral convex portions OH1, OH2, inner peripheral spiral grooves IG1, IG2, and inner peripheral spiral convex portions IH1 and IH2.
Not limited to this, as shown in FIG. 26, the water pipe 21 includes the outer peripheral spiral grooves OG1 and OG2, the outer peripheral spiral convex portions OH1 and OH2, the inner peripheral spiral grooves IG1 and IG2, and the inner peripheral spiral convex portions IH1 and IH2. It may be omitted and may have a cylindrical shape. In this case, a part of the stirring plates 50, 60, 80, 90, 91 is brought into contact with the inner peripheral surface of the water pipe 21. Alternatively, in this case, a part of the stirring plates 50, 60, 80, 90, 91 is fixed to the inner peripheral surface of the water pipe 21 by brazing or the like. Further, the refrigerant pipes 22a and 22b are fixed to the outer peripheral surface of the water pipe 21 by brazing or the like.
With this configuration, it is possible to omit the steps of forming the outer peripheral spiral grooves OG1 and OG2, the outer peripheral spiral convex portions OH1, OH2, the inner peripheral spiral grooves IG1 and IG2, and the inner peripheral spiral convex portions IH1 and IH2 in the water pipe 21. Therefore, the water-refrigerant heat exchanger can be manufactured at low cost.

In the first to sixth embodiments, the stirring plates 50, 60, 80, 90, 91 may be arranged in the entire region of the water pipe 21 around which the refrigerant pipe 22 is wound. In this case, the action of the stirring plates 50, 60, 80, 90, 91 described above can be greatly enhanced, and the heat exchange efficiency of the water refrigerant heat exchanger 8 can be greatly enhanced, so that the water flowing in the water pipe 21 can be greatly enhanced. It is possible to increase the heating efficiency of. Further, the stirring plates 50, 60, 80, 90, 91 may be arranged in a predetermined part of the region of the water pipe 21 around which the refrigerant pipe 22 is wound. The material cost and processing cost of the water refrigerant heat exchanger 8 may increase due to the stirring plates 50, 60, 80, 90, 91, but when they are arranged in a predetermined part of the area of the water pipe 21 The increase in material cost and processing cost of the water refrigerant heat exchanger 8 is suppressed, and the pressure loss of the water flow in the water pipe 21 is further suppressed. The output of the compressor 2 of the heat pump device 1, the performance of the air refrigerant heat exchanger 7, the performance of the water refrigerant heat exchanger 8, the length of the water pipe 21, the physical properties of the refrigerant, etc., and the setting boiling of the heat pump device 1. Minimize the optimum location for the temperature gradient characteristics of water in the length direction of the water pipe 21 and the temperature gradient characteristics of the refrigerant in the refrigerant pipe 22 in the length direction of the water pipe 21 determined by the capacity, set boiling temperature, etc. Stirrers 50, 60, 80, 90, 91 may be arranged. For example, in a place where the temperature difference between water and the refrigerant is large and the temperature of water is high, the heating efficiency effect by stirring the water is high, so the stirring plate is minimized. 50, 60, 80, 90, 91 may be arranged. In this case, the decrease in the water flow path area is further suppressed at the place where the water temperature is low, and the water is agitated at the place where the water temperature is high. As a result, the pressure loss of the water flow in the water pipe 21 can be further suppressed and heat can be efficiently applied to the water flowing in the water pipe 21, so that the increase in the cost of the water refrigerant heat exchanger 8 can be suppressed while suppressing the increase in the cost. It is possible to increase the heating efficiency of the water flowing in the water pipe 21.

1 Heat pump device 2 Compressor 4 Suction pipe 5 Discharge pipe 6 Blower 7 Air refrigerant heat exchanger 8, 58, 68, 78, 88, 98, 108 Water refrigerant heat exchanger 9 Electrical equipment storage box 9a Terminal block 10 Expansion valve 12 Storage container 14 Machine room 15 Blower room 16 Partition plate 17 Base 18 Front panel 18a Front 18b Left side 19 Back panel 19a Rear 19b Right side 20 Top panel 21 Water pipe 21a Curved pipe 21b Straight pipe 22, 22a, 22b Coolant pipe 27 Service panel 28 Water inlet valve 29 Hot water outlet valve 30, 31 Internal pipe 33 Hot water storage device 34 Hot water storage tank 35 Water pump 36, 37 External pipe 38, 39 Pipe 40 Mixing valve 41 Hot water supply pipe 42 Water supply pipe 43 Hot water supply pipe 44 Water supply Tubes 50, 60, 80, 90, 91 Stirring plate 51, 61 as a stirring member Stirring part 51a Large diameter stirring part 51b Small diameter stirring part D Concavo-convex Fa Large diameter stirring part group Fb Small diameter stirring part group IG1, IG2 Inner circumference spiral groove IH1, IH2 Inner circumference spiral convex part IS Water inlet side K spacing KW Kalman vortex L Long side O1 axis OS Heat exchange part side OG1, OG2 Outer spiral groove OH1, OH2 Outer spiral convex part R Edge S Short side α1, α2 Horn

Claims (24)

A water pipe through which liquid water flows,
A refrigerant pipe that is arranged in contact with the outer peripheral surface of the water pipe and through which a refrigerant that exchanges heat with the water inside the water pipe flows.
A stirring member arranged in the water pipe and made of a plate material having a spiral shape along the axis of the water pipe.
Water refrigerant heat exchanger equipped with. The water-refrigerant heat exchanger according to claim 1, wherein the stirring member is formed by winding the plate material in a spiral shape. The plate material constituting the stirring member has a short side and a long side in a cross section along the axis.
The water-refrigerant heat exchanger according to claim 1 or 2, wherein the long side is arranged along the axis. The plate material constituting the stirring member has a short side and a long side in a cross section along the axis.
The water-refrigerant heat exchanger according to claim 1 or 2, wherein the angle formed by the long side and the shaft is smaller than the angle formed by the short side and the shaft. An inner spiral groove, which is a spiral groove along the axis, is formed on the inner peripheral surface of the water pipe.
The water-refrigerant heat exchanger according to any one of claims 1 to 4, wherein at least a part of the stirring member is in contact with the inner spiral groove. The water-refrigerant heat exchanger according to claim 5, wherein the direction of rotation of the spiral of the inner peripheral spiral groove and the direction of rotation of the spiral of the stirring member match. On the outer peripheral surface of the water pipe, an outer spiral convex portion, which is a spiral convex portion, is formed at a position corresponding to the inner peripheral spiral groove.
On the outer peripheral surface of the water pipe, an outer spiral groove, which is a spiral groove relatively formed by forming the outer spiral convex portion, is formed.
The water refrigerant heat exchanger according to claim 5 or 6, wherein the refrigerant pipe is in contact with the water pipe along the outer peripheral spiral groove. The projected outer peripheral image of the stirring member when viewed from the axial direction is any one of claims 1 to 7, which is any one of a circular shape, an elliptical shape, and a polygonal shape. The water refrigerant heat exchanger described. In the stirring member, a plurality of stirring parts are arranged in series and connected integrally.
The stirring unit has the short side and the long side in a cross section along the axis.
The water-refrigerant heat exchange according to any one of claims 3 to 8, wherein the distance between the adjacent short sides in the cross section along the axis is longer than the length of the long side. vessel. The stirring member includes a plurality of stirring parts connected in series, and the stirring member includes a plurality of stirring parts.
At least one of the plurality of stirring portions is a large-diameter stirring portion that abuts on the inner peripheral surface of the water pipe.
The water-refrigerant heat exchanger according to any one of claims 5 to 9, wherein at least one of the plurality of stirring units is a small-diameter stirring unit having a smaller outer diameter than the large-diameter stirring unit. The water-refrigerant heat exchanger according to any one of claims 1 to 10, wherein the stirring member meanders along the shaft. The water-refrigerant heat exchanger according to any one of claims 1 to 11, wherein a plurality of the stirring members are arranged in the water pipe so as to overlap each other in a direction along the axis. The water-refrigerant heat exchanger according to any one of claims 1 to 12, wherein a plurality of the stirring members are arranged in the water pipe in a direction orthogonal to the axis. A plurality of the stirring members having different external sizes are provided.
The water-refrigerant heat exchange according to any one of claims 1 to 13, wherein the stirring member having a smaller outer shape is arranged in the stirring member having a larger outer shape. vessel. The water-refrigerant heat exchanger according to any one of claims 1 to 14, wherein a plurality of the stirring members are arranged so as to be adjacent to each other in the axial direction in the water pipe. The water pipe includes a curved pipe portion which is a curved pipe portion and a straight pipe portion which is a plurality of linear pipe portions.
The water-refrigerant heat exchanger according to any one of claims 1 to 15, wherein the stirring member is arranged in at least two straight pipe portions. The water-refrigerant heat exchanger according to any one of claims 1 to 16, wherein a plurality of irregularities are provided on the surface of the stirring member. The water-refrigerant heat exchanger according to any one of claims 3 to 17, wherein an edge portion rising from the long side is formed at the end of the long side. The water refrigerant heat exchanger according to any one of claims 5 to 18, wherein the stirring member is fixed to the inner peripheral surface of the water pipe. The stirring member includes a plurality of stirring parts, and the stirring member includes a plurality of stirring parts.
The water-refrigerant heat exchanger according to any one of claims 1 to 19, wherein the external dimensions of the plurality of stirring units are different from each other. The stirring member includes a plurality of stirring parts connected in series, and the stirring member includes a plurality of stirring parts.
The stirring unit has the short side and the long side in a cross section along the axis.
The water-refrigerant heat exchanger according to any one of claims 3 to 20, wherein the length of the long side or the distance between the stirring portions adjacent to each other along the axis is different. The water-refrigerant heat exchanger according to any one of claims 1 to 21, wherein the stirring member is arranged in the entire area of the water pipe around which the refrigerant pipe is wound. The water-refrigerant heat exchanger according to any one of claims 1 to 21, wherein the stirring member is arranged in a predetermined part of a region of the water pipe around which the refrigerant pipe is wound. .. A compressor that compresses the refrigerant and
The water-refrigerant heat exchanger according to any one of claims 1 to 23, which exchanges heat between the refrigerant compressed by the compressor and water.
A decompression device that decompresses the refrigerant that has been heat-exchanged by the water-refrigerant heat exchanger.
An evaporator that exchanges heat between the refrigerant decompressed by the decompression device and the outside air,
A heat pump device equipped with.

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