JP7195812B2 - Heat source device - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat source device having a configuration in which a common burner heats liquid distribution pipes for heating and hot water supply.

Conventionally, for example, a one-can two-channel type heat exchanger in which a hot water supply exchanger and a heat exchanger for reheating a bath are integrated is provided, and the one-can two-channel type heat exchanger is used with a common burner. A heating type heat source device is used, and FIG. 13 schematically shows a cross-sectional configuration of a one-can two-channel type heat exchanger (see, for example, Patent Document 1).

As shown in the figure, the one-can two-channel type heat exchanger 201 has a hot water supply heat transfer pipe 141 forming a hot water supply heat exchanger and a circulation heating heat transfer pipe 142 forming a reheating heat exchanger. In the figure, a common fin 143 is provided on the outer peripheral side of these heat transfer tubes 141 and 142 . In this one-can, two-channel type heat exchanger 1, as indicated by an arrow A in FIG. Water is led out through the heat transfer pipe 141 for hot water supply arranged at the uppermost stage to supply hot water, and at the time of reheating the bath, hot water passing through the heat transfer pipe 142 for circulation heating at the center stage is heated by the burner. .

If the heat source device is formed by providing such a one-can two-channel type heat exchanger 201, the size of the heat source device can be reduced compared to the case where the heat exchanger for the bath and the heat exchanger for the hot water supply are separately formed. There is an advantage that

Japanese Utility Model Publication No. 8-7307 Japanese Patent No. 4071224

By the way, in recent years, in order to supply a liquid heat medium such as hot water to a heating device such as a hot water mat or a bathroom dryer, a heat source device provided with a heating circuit connected to the heating device has come to be widely used. ing. In a heat source device having such a heating circuit, in order to reduce the size of the heat source device, in the configuration proposed in Patent Document 1, liquid is added to the heating device instead of the heat exchanger for reheating the bath. It is conceivable to provide a heating heat exchanger for supplying a heat medium of 1 to form a one-can two-channel type heat exchanger.

That is, for example, instead of the circulation heating heat transfer pipe 142 forming the heat exchanger for reheating in the configuration of FIG. The heat pipes 141 are provided in such a manner as to sandwich the heat transfer pipes of the heat exchanger for heating from above and below. However, since the capacity required for heating is higher than the reheating capacity, the problem arises that the required capacity for heating is insufficient.

In addition, in a heat source device equipped with a hot water supply function, a user will use hot water supply in the kitchen, washroom, etc., and use hot water supply using a shower in the bathroom. It is strongly desired that a sufficient amount of hot water at the hot water supply set temperature set by the user is discharged from the shower nozzle according to the user's operation, and the temperature of the hot water is too low or the flow rate of hot water is too low. Then you feel very uncomfortable. Moreover, compared to the hot water supply in the kitchen or washroom, the flow rate when using hot water supply using a shower in the bathroom is a little higher. It is also important for the heat source device to be able to supply hot water of the same temperature.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and its object is to provide a heat source device that can provide sufficient hot water supply capacity and heating capacity even in a small size, and that can be used comfortably by users. It is in.

In order to achieve the above objects, the present invention has the following configuration as means for solving the problems. That is, the first invention comprises a hot water supply heat exchanger, a hot water supply circuit having a function of heating water as a liquid heat medium by the hot water supply heat exchanger and supplying hot water to a hot water supply destination, a heating heat exchanger, and the hot water supply heat exchanger. a heating circulation pump that circulates a liquid heat medium through a heating heat exchanger; and a heating circuit that supplies the heat medium from the heating circuit to a heating device connected to the outside to circulate the heat medium. The hot water heat exchanger is configured to circulate through the heating circuit, and the hot water heat exchanger is a main hot water heat exchanger that recovers the sensible heat of the combustion gas of the burner device by a liquid flow conduit forming the hot water heat exchanger. wherein the heating heat exchanger has a main heating heat exchanger for recovering sensible heat of combustion gas of the burner device through a liquid flow conduit forming the heating heat exchanger, and the main hot water supply At least a part of the liquid distribution pipe of the heat exchanger has a two-kind pipe arrangement portion arranged in contact with each other in such a manner that the liquid distribution pipe is vertically sandwiched by the liquid distribution pipe of the main heating heat exchanger. A combined heat exchanger having a configuration in which two types of liquid circulation pipelines of the two-kind pipeline installation section are heated by a common burner device is provided, and the outlet side of the main heating heat exchanger is provided with the A forward passage is formed for circulating liquid that has passed through the main heating heat exchanger toward the heating device, and a return side returns the liquid that has passed through the heating device to the main heating heat exchanger. is formed, and the tip end of the branched passage branched from the outgoing side passage is connected to the return side passage, and the branched passage is connected to the inlet of the main hot water supply heat exchanger. A means for solving the problem is a configuration in which a liquid-water heat exchanger for thermally connecting hot water supply and heating is provided, which is thermally connected to the side passage .

In addition to the configuration of the first invention, the second invention is configured to vary at least one of whether or not the liquid that has passed through the main heating heat exchanger is branched to the branch passage side and the branched flow rate. A liquid branching variable means is provided.

Further, in a third invention, in addition to the configuration of the first or second invention, the hot water supply circuit has a hot water supply heat exchanger for latent heat recovery for recovering latent heat of combustion gas, The hot water supply heat exchanger is connected to the inlet side of the main hot water supply heat exchanger via a pipe line, and the hot water supply/heating thermal connection liquid-water heat exchanger is connected to the latent heat recovery hot water supply heat exchanger. It is characterized by being thermally connected to a pipeline between the main hot water supply heat exchanger.

Furthermore, in a fourth invention, in addition to the configuration of the first, second, or third invention, a reheating circulation passage connected to the bathtub for reheating hot water in the bathtub is provided, and the reheating circulation is provided. A liquid-water heat exchanger for reheating is provided for thermally connecting the passage and the branch passage.

Furthermore, in addition to the configuration of the fourth invention, the fifth invention is characterized in that the reheating liquid-water heat exchanger has a higher rate of liquid in the branch passage than the hot water supply and heating thermal connection liquid-water heat exchanger. It is characterized by being provided on the upstream side of the flow.

Furthermore, a sixth invention, in addition to any one of the first to fifth inventions, is provided in the hot water supply circuit for variably adjusting the total amount of hot water supplied through the hot water supply circuit. A water quantity servo is provided.

According to the present invention, the liquid circulation pipelines of the main hot water supply heat exchanger provided in the hot water supply circuit are in contact with each other in such a manner that they are vertically sandwiched by the liquid circulation pipelines of the main heating heat exchanger provided in the heating circuit. A composite heat exchanger having at least a part of a two-kind pipe installation part, wherein the two liquid distribution pipes of the two-kind pipe installation part are heated by a common burner device. Therefore, it is possible to reduce the size of the heat source device compared to the case where the main hot water heat exchanger and the main heating heat exchanger are separately formed and provided, and the main hot water heat exchanger at the two-kind pipe installation part A sufficient heating capacity can be obtained by heating the liquid distribution pipes of the heating heat exchangers provided above and below the liquid distribution pipes of the vessel with a burner device.

In addition, in the present invention, the lowest (lowest position) passage in the two-kind pipe installation portion is a liquid distribution pipe for heating, and the liquid (heat medium) flowing through this pipe is heated. It is warm when it is circulating, and even when the circulation is stopped, it is almost never cold like a liquid distribution pipe for hot water supply where cold water is introduced from the water supply side. , it is possible to prevent dew condensation from occurring in the liquid distribution pipes of the composite heat exchanger.

In addition, in the present invention, the main hot water supply heat exchanger liquid circulation pipeline is sandwiched between the liquid circulation pipelines of the main heating heat exchanger. Since the ratio of the liquid distribution pipes in the heat exchanger is smaller than the ratio of the liquid distribution pipes in the main heating heat exchanger, the hot water supply capacity may be insufficient only by heating this component. On the other hand, the following configuration can sufficiently make up for the shortage.

That is, in the present invention, the heating circuit includes an outlet side of the main heating heat exchanger for circulating the liquid that has passed through the main heating heat exchanger toward the heating device side. A passage is formed in the heating circuit, and a return-side passage is formed in the heating circuit to return the liquid that has passed through the heating device to the main heating heat exchanger side, and a branch branched from the forward-side passage is formed. The tip side of the passage is connected to the passage on the return side. Further, since the branch passage is provided with a liquid-water heat exchanger for thermally connecting the branch passage to the inlet-side passage of the main hot water supply heat exchanger, If necessary, the lack of hot water supply capacity can be replenished by transferring the heat of the heating circuit to the hot water supply circuit side via this liquid-water heat exchanger for hot water supply/heating thermal connection.

Further, if a liquid branching variable means is provided for varying at least one of whether or not the liquid that has passed through the main heating heat exchanger is branched to the branch passage side and the branched flow rate, the liquid branching variable means can be used to heat the main heating. By varying at least one of whether or not the liquid that has passed through the exchanger is branched to the branch passage side and the flow rate of the branch, the heat of the heating circuit is transferred via the liquid-water heat exchanger for hot water supply and heating thermal connection. It is possible to perform at least one of the presence/absence of the operation to be transmitted to the hot water supply circuit side and the variation of the amount of heat to be transmitted.

Therefore, if it is predicted that the capacity of the heating side will be insufficient by transferring the heat from the heating side to the hot water supply side, the heat from the heating circuit will be transferred to the hot water supply circuit via the liquid-water heat exchanger for hot water supply heating thermal connection. A decrease in heating capacity can be suppressed by not performing the operation to transmit to the side or by reducing the amount of heat to be transmitted. Conversely, only a small heating capacity is required, and it is necessary to compensate for the lack of capacity on the hot water supply side by transmitting the heat of the heating circuit to the hot water supply circuit side via the liquid-water heat exchanger for hot water supply and heating thermal connection. If it is predicted that there will be a , can fully supplement the hot water supply capacity.

Furthermore, the hot water supply circuit has a latent heat recovery hot water supply heat exchanger for recovering the latent heat of the combustion gas, and the latent heat recovery hot water supply heat exchanger is connected to the inlet side of the main hot water supply heat exchanger via a pipe line. and the liquid-water heat exchanger for hot water supply and heating thermal connection is thermally connected to the pipeline between the latent heat recovery hot water supply heat exchanger and the main hot water supply heat exchanger. According to the above, heat efficiency can be improved by providing a hot water supply heat exchanger for recovering latent heat.

In addition, when the liquid-water heat exchanger for hot water supply/heating thermal connection is connected to the inlet side of the hot water supply heat exchanger for latent heat recovery, heat is generated from the heating circuit side via the liquid/water heat exchanger for hot water supply/heating thermal connection. There is a concern that the heat efficiency will decrease due to the introduction of the warmed water into the hot water heat exchanger for latent heat recovery. By connecting to the pipeline between the heat exchanger and the main hot water supply heat exchanger, it is possible to suppress the occurrence of the concern. Then, as described above, heat can be transferred from the heating circuit side to the hot water supply circuit side to make up for the lack of hot water supply capacity.

Further, a reheating circulation passage is provided for reheating hot water in the bathtub connected to the bathtub, and a liquid-water heat exchanger for reheating is provided for thermally connecting the reheating circulation passage and the branch passage. In this configuration, the reheating operation of the bathtub can be improved by thermally connecting the liquid circulation pipe of the heating circuit and the reheating circulation passage through the liquid-water heat exchanger for reheating. A heat source device can be formed.

Furthermore, in a configuration in which a reheating liquid-water heat exchanger is provided, the reheating liquid-water heat exchanger has a higher flow rate of liquid in the branch passage than the hot water supply and heating thermal connection liquid-water heat exchanger. The following effects can be obtained in those provided on the upstream side of the flow.

That is, in this configuration, after the heat of the heating circuit is transmitted to the reheating circulation passage side through the reheating liquid-water heat exchanger, Since the heat is transmitted to the hot water supply circuit side, unlike the case where the heat of the heating circuit is transmitted to the hot water supply circuit side first, it is possible to suppress the lack of heat transmitted to the reheating circulation passage side. It can prevent you from being very uncomfortable.

That is, the automatic filling of hot water into the bathtub is performed according to a predetermined sequence program. In most cases, it takes a long time to fill the hot water without reheating it sufficiently. Therefore, if the amount of heat transferred to the reheating circulation passage is insufficient, the automatic hot water filling time will be prolonged and the user will be very uncomfortable, but such a situation can be suppressed.

Furthermore, by providing the hot water supply circuit with a water volume servo for variably adjusting the total volume of hot water supplied through the hot water supply circuit, for example, the total volume of hot water supplied can be reduced as necessary to suppress the hot water supply capacity. Since the temperature of hot water supply can be rapidly increased and stabilized by , the temperature of hot water supply can be stabilized even better. If the hot water supply temperature is stabilized by reducing the total amount of hot water supply, the hot water supply capacity can be increased by increasing the total amount of hot water supply after that. By not performing the operation of reducing the total amount of hot water supply when there is no hot water supply, it is possible to supply hot water in accordance with the required hot water supply capacity.

BRIEF DESCRIPTION OF THE DRAWINGS It is typical explanatory drawing which shows the system configuration|structure of the heat-source apparatus of 1st Example of the heat-source apparatus which concerns on this invention with the heating apparatus etc. which are connected to a heat-source apparatus. FIG. 3 is an explanatory view schematically showing the arrangement configuration of the heat exchanger and the burner device in the example. FIG. 3 is a block diagram showing the main configuration of the control configuration provided in the heat source device of the embodiment; FIG. 3 is a schematic perspective view (a) and a plan view (b) for explaining the configurations of hot water supply and heating burner devices applied to the heat source device of the embodiment. 5 is a graph for explaining the relationship between the combustion surface switching operation of the burner device and the hot water supply capacity when the heat source device of the embodiment is in hot water supply independent operation. 5 is a graph for explaining the relationship between the combustion surface switching operation of the burner device and the hot water supply capacity during simultaneous hot water supply and heating operation of the heat source device of the embodiment. It is a typical system explanatory drawing for demonstrating the system configuration modification of the heat-source apparatus of 1st Example. FIG. 2 is a schematic explanatory diagram showing a system configuration of a heat source device including a reference example ; FIG. 4 is a schematic cross-sectional explanatory view showing an arrangement example of a heat exchanger and a burner device applied to another embodiment of the heat source device according to the present invention; BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic explanatory drawing which shows the arrangement|positioning of a burner apparatus and the aspect of a compound heat exchanger in the heat-source apparatus of this inventor devised which leads to the invention of the heat-source apparatus of an Example. FIG. 3 is a schematic explanatory diagram showing the configuration of a conventionally proposed heat source device having a composite heat exchanger. FIG. 12 is a schematic explanatory diagram for explaining a problem of the heat source device shown in FIG. 11 by simplifying the configuration of FIG. 11; 1 is a schematic explanatory diagram showing a configuration example of a conventionally proposed one-can two-channel type heat exchanger; FIG. 4 is a block diagram showing a control configuration for heating operation control and bathing operation control of the heat source device; FIG. 4 is a graph showing an example of relationship data (PQ data) between a water level (P) and a water volume (Q) of a bathtub used for filling the bathtub with hot water.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described by examples based on the drawings. In the description of the present embodiment, the same reference numerals are given to the parts with the same names as the examples of the description so far, and the redundant description thereof will be omitted or simplified.

FIG. 1 schematically shows the system configuration of the first embodiment of the heat source device according to the present invention. As shown in the figure, the heat source device of this embodiment is a composite heat source device formed by providing a hot water supply circuit 45 and a heating circuit 7 in an instrument case 80 . This heat source device has a combustion chamber 100 in which burner devices 2 (2a, 2b, 2c) for hot water supply and a burner device 5 for heating are provided.

The burner device 2 for hot water supply has a plurality of burner devices 2a, 2b, and 2c, and is divided into sections formed by a combustion surface of the burner device 2a, a combustion surface of the burner device 2b, and a combustion surface of the burner device 2c. It has a burning surface. In other words, the combustion surfaces of the burner devices 2a, 2b, and 2c are divided into separate combustion surfaces. Combustion control means (not shown in FIG. 1) is provided for selectively and sequentially additionally burning the segmented combustion surfaces in a predetermined order (the order of the burner devices 2a, 2b and 2c). Below the hot water supply burner device 2 and heating burner device 5, a combustion fan 15 for air supply and exhaust of these burner devices 2 and 5 is provided.

In the combustion chamber 100, a combined heat exchanger 1 for supplying hot water and heating is provided above the burner device 2 for supplying hot water and the burner device 5 for heating. As shown in FIG. 2, a first-class pipeline installation portion (first-class flow path installation portion) 111 in which only the hot water supply liquid distribution pipeline 13 forming the main hot water supply heat exchanger is arranged, and a hot water supply Two types of pipes are arranged in contact with each other in such a manner that the liquid distribution pipe 13 for the heating is vertically sandwiched by the liquid distribution pipe 12 for heating forming the main heat exchanger for heating (see FIG. 2). The first-class pipeline installation portion 112 and the first-class pipeline installation portion 111 are arranged side by side.

As described above, in this embodiment, the two-kind pipe installation portion 112 of the composite heat exchanger 1 is arranged to connect the liquid distribution pipe 13 of the main hot water heat exchanger to the liquid distribution pipe 12 of the main heating heat exchanger. The two pipe line installation portions 112 of this configuration form a part of the composite heat exchanger 1 . A heating burner device 5 for heating the second pipeline installation portion 112 is provided below the second pipeline installation portion 112, and the liquid distribution pipeline of the second pipeline installation portion 112 is provided. 12 and 13 are configured to be heated by a common (one) burner device (heating burner device 5).

On the other hand, a burner device 2 for supplying hot water for heating the first-class pipeline installation portion 111 is disposed below the first-class pipeline installation portion 111. As shown in FIG. The liquid distribution pipelines 12 and 13 arranged in a part of the side adjacent to the first pipeline installation part 111 in the second pipeline installation part 112 protrude above the burner device 2 for hot water supply. are arranged.

In this embodiment, even if the combustion gas from the heating burner device 5 spreads toward the first pipe line installation portion 111 when only the heating burner device 5 burns, the hot water supply gas is spread in the spread portion. Since the liquid distribution pipelines 12 and 13 of the second-class pipeline installation portion 112 are arranged so as to protrude from the upper side of the burner device 2, it is this that is heated by the spread combustion gas. It becomes the liquid distribution pipelines 12 and 13 of the two-kind pipeline installation part 112 .

Since the two-kind pipe arrangement portion 112 is arranged in such a manner that the liquid circulation pipe 13 for supplying hot water is vertically sandwiched by the liquid circulation pipe 12 for heating, the burner device 5 for heating burns. Heated by the spread of the gas is the heating liquid conduit 12 disposed below the hot water supply liquid conduit 13 . Therefore, it is possible to prevent the hot water supply liquid distribution pipeline 13 arranged on the first pipeline installation portion 111 side from being heated by the heating burner device 5 during the single heating operation. It is possible to suppress the boiling of the heat medium such as water remaining in the hot water supply liquid circulation pipe 13 arranged on the arrangement portion 111 side.

The composite heat exchanger 1 has fins 43. The fins 43 are provided so as to rise above the hot water supply burner device 2 and the heating burner device 5, and are arranged in a direction perpendicular to the paper surface of FIG. 1), and as shown in FIG. 2, the surface direction of each fin 43 is aligned with the array of burner devices 2a, 2b, 2c for supplying hot water. It is configured to be a direction orthogonal (or substantially orthogonal) to the direction. Both the liquid distribution conduit 13 of the first conduit arrangement part 111 and the liquid distribution conduits 12, 13 of the second conduit arrangement part 112 are connected to corresponding conduit inserts formed in these common fins 43. are inserted into the holes 103 and 104 (the liquid circulation pipeline 13 is inserted into the pipeline insertion hole 103, and the liquid circulation pipeline 12 is inserted into the pipeline insertion hole 104). Once formed, it is very easy to manufacture.

Further, in the two-kind pipe arrangement portion 112, among the three pipes arranged in the vertical direction (liquid distribution pipe 12 for heating and liquid distribution pipe 13 for hot water supply), the middle pipe is The following effects can be obtained by forming the liquid flow conduit 13 into which low-temperature water is introduced. In other words, depending on the arrangement of the heating liquid circulation conduit 12 and the hot water supply liquid circulation conduit 13 in the two-kind conduit arrangement portion 112, the heat absorption amount of the heating liquid circulation conduit 12 and the hot water supply liquid circulation A difference occurs in the amount of heat absorbed on the side of the pipe line 13, and by providing the middle pipe line in the vertical direction in the second type pipe line installation part 112 as the liquid distribution pipe line 13 for hot water supply in a manner that is in contact with each other, The structure is such that the amount of heat absorbed per one liquid circulation pipe 13 can be increased.

Since FIG. 1 is a system diagram, it is shown in a manner different from that of FIG. The liquid circulation conduit 13 and the liquid circulation conduits 12, 13 of the two-kind conduit arrangement portion 112 are arranged. However, since FIG. 2 is also a schematic configuration diagram, the number of the liquid circulation conduits 12, 13, etc. is not necessarily shown accurately, and the number and arrangement of the liquid circulation conduits 12, 13 are not always shown. Intervals and the like are not limited to those shown in FIG. 1, and may be set as appropriate.

In this embodiment, a hot water supply heat exchanger 4 for latent heat recovery for recovering the latent heat of the combustion gas of the burner devices 2 and 5 is connected to the hot water supply liquid flow conduit 13 forming the main hot water supply heat exchanger. A heating heat exchanger 6 for recovering the latent heat of the combustion gas of the burner devices 2 and 5 is connected to the heating liquid distribution pipe 12 forming the main heating heat exchanger. ing. The hot water supply heat exchanger 4 for recovering latent heat and the heat exchanger 6 for heating use the heat medium (here, water) passing through the liquid flow conduits forming the respective heat exchangers to heat the burners 2 and 5. The latent heat of the combustion gas is recovered, and both the hot water supply heat exchanger 4 for latent heat recovery and the heating heat exchanger 6 recover not only the latent heat of the combustion gas of the burner devices 2 and 5 but also the sensible heat. is.

Both the hot water supply heat exchanger 4 for latent heat recovery and the heating heat exchanger 6 for latent heat recovery are arranged on the upper side of the composite heat exchanger 1, and the hot water supply heat exchanger 4 for latent heat recovery is arranged. A partition 115 is provided on the upper side of the composite heat exchanger 1 to separate the space from the installation space of the heating heat exchanger 6 for latent heat recovery. Due to this partition 115, the combustion gas (exhaust gas) of the burner device 5 for heating passes through the space in which the latent heat recovery heating heat exchanger 6 is installed after passing through the composite heat exchanger 1, and then passes through the space for latent heat recovery. The water is discharged from the exhaust port 116 through the installation space of the hot water supply heat exchanger 4 . That is, the heating heat exchanger 6 for latent heat recovery is disposed upstream of the flow of combustion gas from the burner device 5 for heating that has passed through the composite heat exchanger 1, and the latent heat recovery heat exchanger 6 is disposed downstream of the flow. A hot water supply heat exchanger 4 is provided.

With such a configuration, the combustion gas at the time of combustion of the burner device 5 for heating is about 160 to about 250° C. after passing through the composite heat exchanger 1. After the latent heat is recovered through and cooled, it passes through the arrangement area of the hot water supply heat exchanger 4 for latent heat recovery. Boiling of water in the hot water supply heat exchanger 4 can be suppressed. In addition, the latent heat recovery heating heat exchanger 6 is arranged above the latent heat recovery hot water supply heat exchanger 4 via a partition 115, and when the hot water supply burner device 2 burns alone, Also, boiling of water in the heating heat exchanger 6 for latent heat recovery can be suppressed.

Since FIG. 1 and FIG. 8, which will be described later, are system diagrams, the arrangement configuration of the hot water supply heat exchanger 4 for latent heat recovery and the heating heat exchanger 6 for latent heat recovery is also different from that in FIG. , actually, the hot water supply heat exchanger 4 for latent heat recovery, the heating heat exchanger 6 for latent heat recovery, etc. are arranged in a manner like the schematic cross-sectional configuration diagram shown in FIG. It is However, the number of hot water supply heat exchangers 4 for recovering latent heat and the heat exchangers for heating 6 for latent heat recovery, the number of installation intervals, etc. are not limited to those shown in FIG. 2, and may be set as appropriate. be.

As shown in FIG. 1, on the outlet side of the main heating heat exchanger (heating liquid flow line 12 forming the main heating heat exchanger), A pipeline 60 is formed as a passage on the forward side for circulating the liquid (hot water) toward the heating devices 70 and 71, and the liquid (water) that has passed through the heating devices 70 and 71 is used as heating heat for latent heat recovery. A pipe line 61 is formed as a passage on the return side returning to the exchanger, and the tip side of a branch passage 65 branched from the pipe line 60 is connected to the pipe line 61. A liquid-water heat exchanger 33 for hot water supply/heating thermal connection is provided, which is thermally connected to the inlet side passage of the main hot water supply heat exchanger.

The hot water supply and heating thermally connecting liquid-water heat exchanger 33 is thermally connected to the pipeline between the latent heat recovery hot water supply heat exchanger 4 and the main hot water supply heat exchanger. Post-heat exchange water temperature detection means 133 for detecting the temperature of the water that has passed through the thermal connection liquid-water heat exchanger 33 is provided.

As shown in FIGS. 4(a) and 4(b), in this embodiment, the hot water supply burner device 2 (2a, 2b, 2c) has a plurality of flame ports 110 arranged along the longitudinal direction. A plurality of burners 107 having a combustion surface formed by arranging one or more flame port rows (here, one row) are arranged in a manner perpendicular to the flame port rows. The burner arrangement 2a is formed by four burners 107, the burner arrangement 2b by three burners 107 and the burner arrangement 2c by six burners 107, so that each burner arrangement 2a, 2b , 2c, the area ratio of the sectional combustion surfaces is approximately 4:3:6. The heating burner device 5 is formed by arranging nine burners 109 having flame ports 110 arranged in the same direction as the burners 107 forming the hot water supply burner device 2 .

Fuel gas is supplied to these hot water supply burner device 2 and heating burner device 5 through a gas supply passage 16 shown in FIG. Solenoid valves 18 respectively indicate gas proportional valves.

Also, as can be seen by referring to both FIG. 4 and FIG. 2, a composite heat exchanger is provided above each combustion surface of the hot water supply burner device 2 (2a, 2b, 2c) and the heating burner device 5. The hot water supply liquid distribution line 13 of 1 and the heating liquid distribution line 12 of the combined heat exchanger 1 are connected to corresponding heating liquid distribution lines 12, 13 disposed below these liquid distribution lines 12, 13. The burner device 5 and the burner device 2 (2a, 2b, 2c) for hot water supply are arranged to have a pipeline part extending parallel or substantially parallel to the row of flame ports 110 . The liquid distribution pipelines of the hot water supply heat exchanger 4 for latent heat recovery and the heating heat exchanger 6 for latent heat recovery also have pipeline portions that extend parallel or substantially parallel to the rows of flame ports 110 of the burner devices 2 and 5. The liquid distribution pipes of the hot water supply heat exchanger 4 for latent heat recovery and the heating heat exchanger 6 for latent heat recovery are arranged on the upper surface side of both burner devices 2 and 5 as a whole. is set.

FIG. 11 shows a schematic explanatory diagram of the configuration of a heat source device having a composite heat exchanger proposed in Patent Document 2. In this heat source device, a burner device for hot water supply is shown. 2 and a burner device 102 for reheating the bath are arranged side by side. A composite type heat exchanger 101 for hot water supply and reheating is provided above the hot water supply burner device 2 and the reheating burner device 102, and the hot water supply burner device 2 and the reheating burner device 101 are provided. A combustion fan 15 for air supply and exhaust of the burner device is provided below each of the burner devices 102 .

The composite type heat exchanger 101 has fins 43 provided so as to extend over the upper side of the hot water supply burner device 2 and the upper side of the reheating burner device 102, and the fins 43 are perpendicular to the paper surface. are arranged in multiple directions at intervals. Pipeline insertion holes 103 and 113 are formed in each of the fins 43, and a liquid distribution pipe (water flow pipe) 13 for hot water supply and a A liquid flow conduit (water conduit) 105 is provided.

In a heat source device having such a composite type heat exchanger 101, the heat source device is less expensive than a case where a heat exchanger for hot water supply and a heat exchanger for reheating are separately formed and arranged in the heat source device. However, as shown in FIG. 12A, for example, when the reheating burner device 102 burns alone, the combustion gas of the reheating burner device 102 expands. As shown by the arrows in the figure, since the hot water supply liquid distribution pipe 13 adjacent to the reheating liquid distribution pipe 105 is also heated, the liquid stays in the liquid distribution pipe 13. There was a problem that the water in the water boiled.

Further, as shown in FIG. 12(b), when the hot water supply burner device 2 burns alone, the combustion gas of the hot water supply burner device 2 expands, and as shown by the arrow in the figure, the hot water supply liquid flows. There is also a problem that the liquid circulation pipeline 105 for reheating adjacent to the pipeline 13 side is also heated, and the water staying in the liquid circulation pipeline 105 boils. Therefore, for example, as shown in FIG. 10, the first-class pipeline installation portion 111 is arranged at a position corresponding to the combustion surface of the burner device 2 for hot water supply, and the second-class pipeline installation portion 112 is arranged at a position corresponding to the combustion surface of the burner device for heating. A similar problem can occur when placed in a position corresponding to the combustion surface of 5.

In the invention described in Patent Document 2, as shown in FIG. 11, for example, the space above the burner device 2 for hot water supply and the space above the burner device 102 for reheating are separated. A partition 106 is provided, and the partition 106 is formed, for example, by arranging the plate surfaces of two stainless steel plates 106a and 106b facing each other with a gap therebetween, and it is proposed to allow air to pass through the gap. there is With this configuration, even if the volume of the combustion gas expands when the burner devices 2, 102 burn independently, only the liquid flow conduits 13, 104 provided above the respective burner devices 2, 102 can cope with the burner devices. 2,102, and is said to be able to keep the adjacent liquid flow lines 104, 13 free from impingement of the combustion gases.

However, in the configuration in which such partitions are provided, the provision of the partitions and the provision of the configuration for passing air complicates the structure accordingly and increases the manufacturing cost. will occur.

On the other hand, in this embodiment, as shown in FIG. , the burner device 5 for heating is arranged, and the liquid distribution pipes 12 and 13 are arranged in a part of the second kind pipe arrangement portion 112 on the side adjacent to the first kind pipe arrangement portion 111. However, since it is arranged in such a manner that it protrudes upward from the burner device 2 for hot water supply, the liquid in the first pipe line arrangement part 111 does not need to be provided with a partition like the invention proposed in Patent Document 2. Boiling of the water in the distribution pipe 13 can be suppressed.

That is, since the volume of the combustion gas of the burner devices 2 and 5 expands during combustion of the burner devices 2 and 5, the burner device 5 for heating disposed below the two-kind pipe line portion 112 is used alone. , the combustion gas spreads to the side of the first pipeline installation portion 111, but is disposed in a part of the second pipeline installation portion 112 on the side adjacent to the first pipeline installation portion 111. Since the liquid distribution pipes 12 and 13 are arranged to protrude above the hot water supply burner device 2, it is the protruding liquid distribution pipe 12 that is heated by the expanded combustion gas. , 13.

Since the two-kind pipe arrangement portion 112 is arranged in such a manner that the liquid circulation pipe 13 for supplying hot water is vertically sandwiched by the liquid circulation pipe 12 for heating, the burner device 5 for heating burns. Heated by the spread of the gas is the heating liquid conduit 12 disposed below the hot water supply liquid conduit 13 . Therefore, it is possible to prevent the hot water supply liquid distribution pipeline 13 arranged on the first pipeline installation portion 111 side from being heated by the heating burner device 5 during the single heating operation. It is possible to suppress the boiling of the heat medium such as water remaining in the hot water supply liquid circulation pipe 13 arranged on the arrangement portion 111 side.

Therefore, during the heating single operation (when the hot water supply burner device 2 is stopped and only the heating burner device 5 is burned, and the circulation of the heat medium in the hot water supply liquid distribution pipe 13 is stopped) It is possible to continuously burn the burner device 5 for heating, or to shorten the combustion-off time even when performing intermittent operation in which the burner device 5 for heating is repeatedly turned on and off during single heating operation. Therefore, the heating capacity can be improved. Moreover, unlike the configuration in which a partition is provided between the space above the burner device 5 for heating and the space above the burner device 2 for hot water supply, the structure can be simplified and the number of parts can be reduced, so the cost can be reduced. .

In the composite heat exchanger 1 applied to the present embodiment, when only the hot water supply burner device 2 arranged on the lower side of the first pipe line installation portion 111 burns, the burner on the hot water supply side The volume of the combustion gas in the device 2 expands, and the combustion gas spreads to the side of the two-kind pipe arrangement part 112, and the liquid distribution pipe 12 for heating and arranged to protrude above the burner 2 for supplying hot water. , and the heating liquid distribution pipe 12 adjacent to the heating liquid distribution pipe 12 protruding is also heated by the combustion gas of the hot water supply burner device 2 .

Therefore, the liquid heat medium remaining in the heating liquid distribution pipe 12 is heated by the combustion gas of the hot water supply burner device 2. Since the liquid distribution pipe 13 for hot water supply is sandwiched between the liquid distribution pipes 12 for heating, the water passing through the liquid distribution pipe 13 for hot water supply causes the liquid distribution pipe 12 for heating. Since the heat of the heat medium inside is radiated, it is possible to prevent the heat medium staying in the liquid distribution pipe 12 for heating from boiling.

Furthermore, the lowest (lowest position) passage in the two-kind pipe installation portion 112 of the composite heat exchanger 1 is the liquid circulation pipe 12 for heating, and the liquid (heat medium) flowing through this pipe is If it is heated and circulated, it is warm, and even if the circulation is stopped, it is cold like the liquid distribution pipe 13 for hot water supply to which cold water is introduced from the water supply side. Since there is almost no condensation, it is possible to prevent dew condensation from occurring in the liquid distribution pipe 12 of the composite heat exchanger 1 .

As shown in FIG. 1, in this embodiment, the hot water supply circuit 45 includes the hot water supply heat exchanger 4 for latent heat recovery and a water supply passage 46 provided on the water inlet side of the hot water supply heat exchanger 4 for latent heat recovery. , a passage 34 provided on the water outlet side of the latent heat recovery hot water heat exchanger 4, a hot water supply liquid distribution pipe 13 (main hot water heat exchanger) of the composite heat exchanger 1, and the composite heat exchanger 1 and a hot water supply passage 47 provided on the water outlet side of the liquid circulation pipe 13 for hot water supply.

The hot water supply circuit 45 is a hot water supply liquid distribution pipe 13 (the main hot water supply heat exchanger) to heat the water, and then lead the heated water to the hot water supply destination through the hot water supply passage 47 . In the hot water supply circuit 45, the water supply passage 46 is provided with a water volume sensor 19 as flow rate detection means for detecting the amount of water passing through the water supply passage 46, and the passage 34 is provided with a hot water supply high limit switch 36, A hot water supply pipe thermistor 151 is provided in the middle of the hot water supply liquid distribution pipe 13 of the composite heat exchanger 1 .

Further, the hot water supply passage 47 is provided with a heat exchange side thermistor 23 for detecting the temperature of the outlet side of the liquid circulation pipe 13 for hot water supply of the composite heat exchanger 1 and a hot water outlet thermistor 24 for detecting the hot water supply temperature. ing. In addition, in this embodiment, a method of calculating the temperature of the incoming water without providing an incoming water temperature detecting means for detecting the temperature of the incoming water for hot water supply is applied (although not shown, a method of detecting the temperature of the incoming water for calculating the temperature of the supplied water is applied). means), for example, during stable combustion of the hot water supply burner device 2, the inlet water temperature is back-calculated from the combustion amount, the water amount, and the outlet hot water temperature, and is stored. A heat source device that obtains the inlet water temperature for hot water supply by calculation is well known, so the description thereof will be omitted, but the temperature of inlet water for hot water supply can be obtained by an appropriate method.

The hot water supply passage 47 is provided with a water amount servo 20 for variably adjusting the total amount of hot water supplied through the hot water supply circuit 45, and the hot water supply passage 47 is connected to the water supply passage 46 via the hot water supply bypass passage 22. A bypass servo 21 is provided at the connecting portion of the bypass passage 22 with the water supply passage 46 .

The heating circuit 7 has a heating liquid circulation passage 8, and the heating liquid circulation passage 8 includes a heating heat exchanger 6 for recovering the latent heat and a heating circulation pump (heating liquid circulation pump) 9. , a cistern 10, a heating high temperature thermistor 40, a heating high limit switch 77, a heating water pipe thermistor 52, and a heating low temperature thermistor 41 are provided. It has a function of circulating a liquid heat medium (for example, water) through the heat exchanger 1 and the heating liquid circulation line 12 .

The heating liquid circulation passage 8 has passages 59 to 65 and 108, and the passage 108 does not pass the heat medium (for example, water) in the heating circuit 7 to the latent heat recovery heating heat exchanger 6. It functions as a latent heat heat exchange bypass passage for circulating to The passage 108 is provided with a passage 119 having a low temperature capacity switching valve 118, and the passage 108 is provided with an orifice at the portion indicated by R in the figure. Note that the passage 119 and the low temperature capacity switching valve 118 can be omitted in some cases. The heating high temperature thermistor 40 detects the temperature of the heat medium on the outlet side of the main heating heat exchanger (heating liquid distribution pipe 12 forming the main heating heat exchanger). The thermistor 41 detects the temperature of the heat medium on the inlet side of the main heating heat exchanger.

The capacity of the cistern 10 is, for example, 1800 cc, and the cistern 10 is provided with a water level electrode 44 and an overflow passage 66 . The cistern 10 is connected to the water supply passage 46 via the water supply electromagnetic valve 42 and the water supply passage 165 .

In this embodiment, the hot water supply circuit 45 and the heating circuit 7 are thermally connected via the liquid-water heat exchanger 33 for hot water supply/heating thermal connection. The liquid-water heat exchanger 33 for hot water supply and heating thermal connection uses a branch passage 65 branched from the passage 60 on the outlet side of the heating liquid distribution pipe 12 forming the composite heat exchanger 1 to transfer latent heat in the hot water supply circuit 45 . It is thermally connected between the hot water supply heat exchanger 4 for recovery and the liquid circulation pipe 13 for hot water supply (main hot water supply heat exchanger) forming the composite heat exchanger 1 .

An appropriate heating device is connected to the heating circuit 7 . In this figure, heating devices 70, 71 are connected to the heating circuit 7 via external passages 72, 73, 74, and the heating circuit 7 has a function of supplying a heat medium to the heating devices 70, 71. . The heating device 70 is, for example, a high-temperature heating device such as a bathroom dryer, and the heating device 70 is provided with a thermal valve 76 . On the other hand, the heating device 71 is a low-temperature heating device such as a warm water mat, and is provided with a thermal valve 48 that selectively switches the connection between the heating liquid circulation passage 8 in the instrument case 80 and the external passage 73. The supply of heat medium to the heating device 71 is controlled.

Further, in the heat source device of this embodiment, the heating liquid circulation passage 8 of the heating circuit 7 is thermally connected to the bath reheating circulation passage 26 via the reheating liquid-water heat exchanger 25. . The reheating circulation passage 26 is provided with a reheating circulation pump 27, a bath thermistor 28, a running water switch 29, a water level sensor 30, and a thermistor 31 for bath. 75.

In addition, the reheating liquid-water heat exchanger 25 is provided on the upstream side of the liquid flow in the branch passage 65 from the hot water supply and heating thermal connection liquid-water heat exchanger 33, and the reheating liquid- A reheating liquid flow control valve 32 is provided on the inlet side of the water heat exchanger 25 . The reheating liquid flow rate control valve 32 controls whether or not the heat medium (water in this case) circulating in the heating circuit 7 is introduced to the branch passage 65 side and adjusts the introduction amount by opening and closing the valve and opening the valve. It functions as a liquid branch variable means that switches depending on the amount.

The reheating liquid flow rate control valve 32 is controlled by the control of the liquid branching variable control means described later, and the reheating liquid-water Whether or not the heat medium is introduced into the heat exchanger 25 and the liquid-water heat exchanger 33 for hot water supply/heating thermal connection and the introduction amount are adjusted. Further, in the reheating liquid-water heat exchanger 25, heat exchange is performed between the heat medium introduced from the branch passage 65 and the water circulating in the reheating circulation passage 26, thereby reheating the hot water in the bathtub. In the hot water supply/heating thermal connection liquid-water heat exchanger 33, when the heat medium is introduced from the branch passage 65 side, heat exchange is performed between the heat medium and the hot water supply circuit.

As described above, the reheating liquid flow rate control valve 32 is opened to introduce water (hot water) into the reheating liquid-water heat exchanger 25, and the reheating circulation pump 27 is driven to reheat the bath. Reheating is performed, but if the reheating circulation pump 27 is stopped, heat exchange between the heat medium passing through the heating circuit 7 and the water in the reheating circulation passage 26 is not performed (more precisely, reheating circulation Although some of the water staying in the passage 26 is heat-exchanged, almost no heat-exchange is performed).

In the drawing of FIG. 1, reference numeral 49 is a pouring passage, reference numeral 50 is a pouring electromagnetic valve, reference numeral 79 is a pouring amount sensor, reference numeral 37 is drain recovery means, reference numeral 38 is a drain passage, and reference numeral 39 is a drain neutralizer. , 76 denote thermal valves, respectively.

Although the remote control device is not shown in FIG. 1, the remote control device is signal-connected to the control device of the heat source device. do. In addition, in a dwelling such as a home, a remote control device 53 with a hot water temperature setting, a reheating switch, an automatic switch (operation switch for automatic hot water filling), etc. is provided in the kitchen and bathroom where hot water is supplied, and the washroom. A remote control device 53 with a switch for drying the bathroom (heating device) is provided in the living room, and a remote control device 53 with a floor heating (heating device) switch is provided in the living room. are generally provided, and they will be collectively referred to as a remote control device 53, and in the description using FIG.

In this embodiment, the hot water supply operation is performed, for example, as follows. That is, when the user of the heat source device opens a hot water tap (not shown) provided on the tip side of the hot water supply passage 47 while the operation of the remote control device 53 is on, the water is introduced from the water supply passage 46 . water is introduced into the hot water supply passage 47 through the hot water supply heat exchanger 4 for latent heat recovery and the liquid distribution pipe 13 (main hot water supply heat exchanger) for hot water supply of the composite heat exchanger 1, and the water quantity sensor 19 reaches a predetermined operating flow rate of hot water supply, combustion control of the burner device 2, rotation control of the combustion fan 15, etc. are appropriately performed by the control means, and hot water at the hot water supply set temperature preset in the remote control device 53 is supplied. It is formed and supplied to the hot water supply destination (normally, feedforward control is performed based on the hot water supply set temperature, the flow rate detected by the water quantity sensor 19, the temperature detected by the detection means for the incoming water temperature, or the estimated temperature by the incoming water temperature estimating means). Combustion is also performed by the burner device 5 for heating as required, and detailed description of this operation will be given later.

Further, when the automatic switch provided in the remote control device 53 is turned on, hot water having a hot water supply set temperature preset in the remote control device 53 is formed in the same manner as in the hot water supply operation, and the hot water is poured. When the electromagnetic valve 50 is opened, hot water is poured into the bathtub 75 from the hot water supply passage 47 through the hot water pouring passage 49 to fill the bath.

On the other hand, when the heat medium (liquid) for heating is supplied from the heating liquid circulation passage 8 to the heating devices 70 and 71 without supplying hot water (for example, by operating a clothes dryer, a bathroom heater/dryer, a floor heater, etc.) When the heating circulation pump 9 is driven to circulate the liquid (hot water in this case), the liquid discharged from the discharge side of the heating circulation pump 9 is shown by the arrow A in FIG. , is introduced into the heating liquid distribution line 12 (main heating heat exchanger) of the composite heat exchanger 1 through the passage 59 . At this time, the combustion of the heating burner device 5 and the rotation control of the combustion fan 15 are appropriately performed to heat the liquid.

The liquid that has passed through the heating liquid distribution pipe 12 of the combined heat exchanger 1 passes through the passage 60 as indicated by arrow C, and then branches off in passage 64. As shown, for example, when the high temperature side heating device 70 connected to the heating liquid circulation passage 8 is activated, the supply is supplied to the high temperature side heating device, and after passing through the high temperature side heating device 70, the arrow It returns to the passage 61 side as indicated by D' and is introduced into the cistern 10 as indicated by arrow F. At this time, for example, when the heating switch (SW) of the bathroom heater/dryer is turned on (ON), the thermal valve 76 in the corresponding high temperature side heating device 70 is opened, and the high temperature side heating device 10 is opened. The incoming temperature of the heat medium for heating is maintained at a high temperature (for example, 80° C.) in response to a signal from the controller.

When the hot-side heater is not operating, the thermal valve 76 in the hot-side heater 70 is closed and the liquid through passage 64 as indicated by arrow D is indicated by arrow H. , and is introduced into the cistern 10 through the latent heat heat exchange bypass passage 108 as shown in FIG.

Further, for example, when the reheating switch (SW) is turned on (ON) in the bathroom, the corresponding reheating liquid flow control valve 32 is opened, and the liquid ( The heat medium) passes through the reheating liquid-water heat exchanger 25 on the passage 65 side , and further through the hot water supply and heating thermal connection liquid-water heat exchanger 33, as indicated by arrow E', to the passage 61. go to the side. By circulating hot water in the bathtub 76 in the reheating circulation passage 26 while passing the liquid maintained at a high temperature through the reheating liquid-water heat exchanger 25, reheating of the bath is appropriately performed. The liquid that has passed through the passage 61 returns to the suction side of the heating circulation pump 9 through the cistern 10 and the passage 62 as described above.

There is a possibility that Legionella bacteria and Escherichia coli may occur in bath water. However, in this embodiment, the bath water is insulated from the hot water passing through the circuit on the heating side by the liquid-water heat exchanger 25 for reheating, and the hot water (city water) for hot water passing through the hot water supply circuit 45 and the heating circuit. Since the heat medium (hot water in this case) passing through 7 is insulated by the hot water supply/heating thermal connection liquid-water heat exchanger 33, the bathtub hot water and the hot water supply are separated from the hot water supply/heating thermal connection liquid-water. The heat exchanger 33 and the liquid-water heat exchanger 25 for reheating are double-insulated. In addition, since the heat medium circulating in the heating circuit 7 is configured to be circulated at 60° C. or higher, in the unlikely event that the reheating liquid-water heat exchanger 25 has a pinhole or the like, the insulation state cannot be maintained. Even if such a situation occurs and fungi generated in the hot water in the bathtub enter the heating circuit 7 side, the bacteria are sterilized by heat, so there is no possibility that the fungi will enter the hot water in the hot water supply circuit 45 side.

The discharge side of the heating circulation pump 9 is also connected to a passage 73 for supplying liquid to a heating device 71 on the low temperature side, such as a hot water mat. When it is turned ON, liquid maintained at a low temperature (eg, forward temperature of 60° C.) for heating is supplied to an appropriate low-temperature side heating device 71 (eg, hot water mat, etc.) according to the opening and closing of the corresponding thermal valve 48. be done.

In addition, temperature control when liquid is supplied to the heating device 70 on the high temperature side and temperature control when liquid is supplied to the heating device 71 on the low temperature side are operated in a state where the passage of the heating liquid circulation passage 8 is cold. Appropriate control such as temperature control at the time of cold start, control at the time of reheating the bath, and combustion control of the heating burner device 5 and rotation control of the combustion fan 15 are performed as necessary. As an example of the heating operation control and the hot water filling and reheating control in the bathtub, there is a control example using a control configuration as shown in FIG. , and other suitable known control methods and suitable control methods to be proposed in the future are applied.

The control configuration shown in FIG. 14 is formed by signal-connecting a control device 54 having combustion control means 52 to remote control devices 167, 168 and 169 of the heat source device. In the figure, a remote control device 167 is a bath remote control device, a remote control device 168 is a remote control device for a heating device (high-temperature heating device) 70, and a remote control device 169 is a remote control device for a heating device (low-temperature heating device) 71. be. The remote control device 167 is provided with a bath set temperature input operation section 163, a reheating switch 160, and an automatic bath switch 164. The remote control device 168 has a heating operation switch 161, and the remote control device 169 has a heating operation switch 166. is provided.

The heating operation switches 161 , 166 are switches that issue ON/OFF operation commands for the operation of the corresponding heating devices 70 , 71 . When the heating operation switch 161 is turned on, the thermal valve 76 of the heating device 70 is energized, and after a predetermined time (for example, 1 minute), the thermal valve 76 opens (positive temperature coefficient (PTC)). When the heating operation switch 161 is turned off, the thermal valve 76 is turned off after a predetermined time (for example, 20 seconds) has passed. closes. When the heating operation switch 166 is turned on, the thermal valve 48 is opened by the combustion control means 52, and when the heating operation switch 166 is turned off, the thermal valve 48 is closed by the combustion control means 52.

Combustion control means 52 receives an ON signal from heating operation switch 161 and performs combustion control of burner 5 (including combustion amount control by opening gas solenoid valve 14, opening amount control of gas proportional valve 18, etc.) and combustion. Rotation control of the fan 15 is performed, and the circulation pump 9 for heating is driven. The combustion control means 52 controls the combustion of the burner 5 so that the liquid of 80° C. can be supplied when the high temperature heating device 70 is operated (FB; feedback control is performed so that the detected temperature of the heating high temperature thermistor 40 becomes 80° C.). By controlling the rotation of the combustion fan 18 and the like, the heating heat exchanger (the heating liquid distribution pipe 12 forming the main heating heat exchanger and the latent heat recovery heating heat exchanger 6) is operated. Heat is applied to heat the liquid circulating through the heating liquid circulation passage 7 . The heated liquid is discharged from the main heating heat exchanger at about 80° C., passes through the conduit 60 as indicated by arrow C in FIG. As indicated by arrow D in FIG.

The liquid supplied to the heating device 70 radiates heat when passing through the pipes in the heating device 70, and in a state where the temperature has dropped to about 60° C., for example, passes through the pipe 74 and is shown by the arrow D' in FIG. , it is introduced into the heating heat exchanger 6 (latent heat exchanger) through a pipeline 61 and heated by the heating heat exchanger 6 . This heated liquid is drawn out through conduit 62 and introduced into cistern device 10 as indicated by arrow F in FIG. It is introduced into the heating circulation pump 9 through the pipe line 62 . After that, the liquid is introduced into the main heating heat exchanger (sensible heat exchanger) (liquid distribution pipe 12) through the pipe 59 as indicated by arrow A in FIG. It is heated by the heat exchanger and circulates through the heating liquid circulation passage 7 in the same manner as described above.

In the state where the reheating liquid flow control valve 32 is open (=during reheating, high temperature reheating heating), the liquid passing through the conduit 60 is shown by the arrow D as described above. As shown by the flow introduced into the heating device (high-temperature heating device) 70 side and then introduced into the pipeline 61, and as shown by arrow E ', the pipeline (branch passage) 65, the reheating liquid-water heat exchange It splits through vessel 25 and is introduced into line 61 .

Further, when the high-temperature heating device 70 operates, the combustion control means 52 normally allows the liquid of 60° C. to be supplied to the low-temperature heating device 71 when operating the low-temperature heating device 71 . Also at this time, the combustion control of the burner 5 and the rotation control of the combustion fan 18 are the same as in the operation of the high-temperature heating device 70, and the temperature of the heating high-temperature thermistor 40 is referred to from the main heating heat exchanger. A liquid having an appropriate temperature (for example, about 80° C.) is drawn out as a result, and the combustion control means 52 opens the reheating liquid flow rate control valve 32 to control the liquid as indicated by arrows C, E′ , and D', by passing in the order shown in F, the pipeline 60, the pipeline 65 (upstream side of the reheating liquid-water heat exchanger 25), the reheating liquid-water heat exchanger 25, the pipeline 65 (reheating The heating liquid-water heat exchanger 25 (downstream side), the pipe 61, the heating heat exchanger 6 for latent heat recovery, the pipe 62, the cistern device 10, and the pipe 62 are passed in order, and the heating circulation pump 9 to be introduced into

When the high-temperature heating device 70 is in operation, the liquid discharged from the heating circulation pump 9 radiates heat when passing through the pipeline of the high-temperature heating device 70, so the temperature drops to about 60° C., and the thermal valve 48 is opened. 1, the liquid is introduced into the low-temperature heating device 71 through the conduit 73 to lower the temperature of the liquid than if the liquid were introduced directly from the main heat exchanger. becomes lower. The liquid, which has been radiated through the low-temperature heating device 71 and has a low temperature of, for example, 40° C. or less, passes through the conduit 74, is introduced into the conduit 61, and circulates through the heating liquid circulation passage 7 in the same manner as described above.

When the high-temperature heating device 70 is not operating, the temperature of the liquid introduced into the low-temperature heating device 71 is controlled by the combustion control means 52 based on the temperature detected by the heating low-temperature thermistor 41. That is, during normal operation of the low-temperature heating device 71 , the detected temperature of the heating low-temperature thermistor 41 is sent to the conduit 73 so as to be, for example, 60° C. (FB; feedback control). At this time, the low temperature capability switching valve (thermal valve) 118 is opened to adjust the amount of combustion of the burner 5 and the combustion amount is sent to the pipeline 73 .

In addition, immediately after the operation of the low-temperature heating device 71 is started, the liquid in the internal passages and pipes 73 of the low-temperature heating device 71 is cold. In the dash operation (cold start), the low temperature capacity switching valve (thermal valve) 118 is opened so that the temperature detected by the heating high temperature thermistor 40 becomes, for example, 80° C. for a predetermined hot dash set time such as 30 minutes. Then, the combustion amount of the burner 5 is adjusted (controlled) and sent to the pipeline 61 .

When both the low-temperature heating device 71 and the high-temperature heating device 70 are operated, liquid is drawn out from the main heating heat exchanger at about 80° C., and after the liquid passes through the pipeline 60, it flows through the pipeline 64. After flowing in two directions, one through the pipe 65 and the other through the pipe 65, it is introduced into the pipe 61 and flows in the direction indicated by the arrow D' . Also, when only the low-temperature heating device 71 is in operation, after passing through the pipeline 60 , it flows in the direction indicated by the arrow E 1 ′ on the pipeline 65 side and is introduced into the pipeline 61 .

A bath set temperature input operation unit 163 shown in FIG. 14 is an operation unit for setting the temperature of hot water in the bathtub. Information on the set temperature is applied to the combustion control means 52 . The automatic bath switch 164 is an ON/OFF switch for automatically filling the bathtub 75 with hot water, keeping warm, and retaining water. After warming and retaining water, it will automatically turn off. Further, the reheating switch 160 is an on-switch for a single reheating operation of bath water, and the ON signal of the reheating switch 160 is applied to the combustion control means 52 . When the combustion control means 52 finishes the reheating operation, the reheating switch 160 is automatically turned off.

When the automatic bath switch 164 is turned on, the combustion control means 52 heats the water passing through the liquid distribution pipe 13 of the main hot water supply heat exchanger by, for example, combustion of the burner 2, and the water is supplied from the hot water supply passage 47 to the pouring passage. Hot water is poured into the bathtub 75 through 49. At this time, for example, as shown in FIG. Based on the detected water level, hot water is poured up to the set water level of the bathtub. When the bath water temperature detected by the bath thermistor 28 obtained by driving the bath water circulation pump 27 is lower than the bath set temperature, the reheating liquid flow rate control valve 32 is opened so as to reach the bath set temperature. , the bathtub hot water circulation pump 27 is turned on, and the bathtub hot water is reheated. The combustion control means 52 also reheats the hot water in the bathtub so that the hot water temperature detected by the bath thermistor 28 is equal to the bath set temperature even when the ON signal of the reheating switch 160 is applied.

FIG. 3 shows a block diagram of the characteristic control configuration of the heat source device of this embodiment. , combustion control means 52 and pump drive control means 55 . The controller 54 includes a remote controller 53, a hot water thermistor 24, a water sensor (flow rate sensor) 19, a reheating liquid flow rate control valve 32, gas solenoid valves 14 and 17, a gas proportional valve 18, a combustion fan 15, a heating circulating pump 9, heating high temperature thermistor 40, heating low temperature thermistor 41, and heat exchange side thermistor 23.

The branching hot water supply side temperature variable means 51 controls the reheating liquid flow rate control valve 32 to vary at least one of the presence or absence of the liquid branched to the branch passage 65 side and the flow rate, thereby increasing the temperature of the hot water supply and heating. By varying the amount of heat supplied from the heating circuit 7 side to the hot water supply circuit 45 side via the liquid-water heat exchanger 33 for connection, the temperature of the water flowing through the hot water supply circuit 45 side is varied. The branching hot water supply side temperature variable means 51 also performs control to open the reheating liquid flow control valve 32 when reheating the hot water in the bathtub and to close the reheating liquid flow control valve 32 after reheating.

When increasing the temperature of the water flowing through the hot water supply circuit 45, the branch corresponding hot water supply side temperature variable means 51 causes the liquid that has passed through the main heating heat exchanger to pass through the branch passage 65 or increases the flow rate of the liquid. The reheating liquid flow control valve 32 is controlled as follows. On the other hand, when it is not necessary to raise the temperature of the water flowing through the hot water supply circuit 45 side, the liquid that has passed through the main heating heat exchanger is not passed to the branch passage 65 side, or reheating is performed so as to reduce the flow rate of the heat medium. It controls the liquid flow control valve 32 for the liquid.

The branching hot water supply side temperature varying means 51 is based on the post-heat exchange water temperature detected by the post-heat exchange water temperature detection means 133, the flow rate detected by the water quantity sensor 19, and the temperature detected by the water supply temperature detection means. , has heat exchange capacity estimation means for estimating the heat exchange capacity of the liquid-water heat exchanger 33 for hot water supply/heating thermal connection (not shown). Then, based on the heat exchange capacity estimated by the heat exchange capacity estimating means, the reheating liquid flow rate control valve 32 is opened and closed and the valve opening amount is controlled.

Specifically, for example, the heat exchange capacity estimating means is obtained by Tout, which is the detected temperature of the water temperature after heat exchange detected by the after-heat-exchange water temperature detecting means 133, the detected flow rate of the water quantity sensor 19, and the bypass ratio in the hot water supply circuit 45. When the flow rate of water passing through the hot water supply and heating thermal connection liquid-water heat exchanger 33 is Q and the detected temperature of the water supply temperature detection means is Tin, the water supply temperature is heated by the hot water supply heat exchanger 4 for latent heat recovery. Based on the temperature ΔT to be heated (for example, a predetermined temperature within the range of 1 to 2° C.), the heat exchange capacity of the hot water supply and heating thermal connection liquid-water heat exchanger 33 is expressed as {Tout−(Tin+ΔT)}Q Based on this value, the opening amount of the reheating liquid flow rate control valve 32 is controlled by the branching hot water supply side temperature varying means 51 .

When the heat medium (hot water) of the heating circuit 7 is supplied to the branch passage 65, if the hot water in the bathtub is reheated, the heating circuit 7 is heated through the liquid-water heat exchanger 33 for hot water supply and heating thermal connection. Although the amount of heat supplied from the side to the hot water supply circuit 45 side becomes smaller, such a timing is not often encountered, and the heat medium is transferred to the branch passage 65 side while the water circulation operation in the reheating circulation circuit 26 is stopped. By doing so, the heat of the heat medium of the heating circuit 7 is transferred to the hot water supply side without almost transferring the heat from the heat medium of the heating circuit 7 to the reheating circulation circuit 26 side, and the hot water supply capacity is improved. can be replenished.

The combustion control means 52 controls the hot water thermistor 24, the water quantity sensor (flow rate sensor) 19, the heat exchange thermistor 23, the heating high temperature thermistor 40, and the heating low temperature thermistor based on the signal (command, set temperature value, etc.) from the remote control device 53. 41 or the like is referred to, opening/closing control of the gas electromagnetic valves 14 and 17 and control of the opening amount of the gas proportional valve 18 are performed, and the burner device 2 (2a, 2b, 2c) for supplying hot water and the burner device 2 (2a, 2b, 2c) for heating are controlled. Combustion control of the burner 5 is performed. Further, the combustion control means 52 drives the combustion fan 15 during combustion of the burner devices 2 and 5, and performs appropriate control, for example, by making the rotational speed correspond to the amount of combustion of the burner devices 2 and 5, or the like.

As described above, the heat source device of the present embodiment performs the hot water supply operation in which hot water is supplied at the hot water supply set temperature through the hot water supply circuit 45, and the heat medium (hot water) heated through the heating circuit 7 is supplied to the heating devices 70 and 71. It has a function of performing a heating operation by circulating the heat medium to the heating devices 70 and 71, and the combustion control means 52 controls each of them during individual operation (during individual hot water supply operation and individual heating operation) and between hot water supply and heating. Combustion control is performed to switch the combustion surfaces of the hot water supply burner device 2 (2a, 2b, 2c) and the heating burner 5 between simultaneous operation and the following.

In other words, the combustion control means 52, during the single hot water supply operation, when the required hot water supply capacity required for the hot water supply operation is less than the predetermined water passage installation unit switching reference capacity (for example, No. 16.5), the first kind pipe installation unit 111 Only the burner device 2 (2a, 2b, 2c) for hot water supply on the lower side of is burned, and when the standard capacity for switching the waterway arrangement part (for example, No. 16.5) is exceeded, the burner device 2 (2a, 2b , 2c) and the burner device 5 for heating on the lower side of the type 2 pipeline installation portion 112 are burned. Further, the combustion control means 52 sequentially adds the value of the hot water supply request capacity required for the hot water supply operation to the branch corresponding hot water supply side temperature varying means 51 .

The combustion control of the hot water supply burner devices 2 (2a, 2b, 2c) performed by the combustion control means 52 is performed by a plurality of burners forming the respective hot water supply burner devices 2a, 2b, 2c as shown in FIG. The combustion surfaces (divided combustion surfaces) divided by the burner 107 are selectively and sequentially additionally burned in a predetermined order each time the combustion capacity required of the burner device 2 for hot water supply is increased by one step. .

For example, in burner combustion in single hot water supply operation, as shown in the number of switching stages (1) in Table 1, the first combustion surface is the combustion surface of the four burners 107 of the burner device 2a for hot water supply. be. In Table 1, as shown in FIG. 1, A is the combustion surface of the hot water supply burner device 2a, B is the combustion surface of the hot water supply burner device 2b, and C is the combustion surface of the hot water supply burner device 2c. , the combustion surface of the burner device 5 for heating is denoted by D. FIG.

The hot water supply characteristic (hot water output characteristic) obtained by combustion of only the hot water supply burner device 2a is, for example, when the temperature of water entering the hot water supply circuit 45 is 15° C., according to the hot water supply set temperature, the characteristic line a ₁ in FIG. and the characteristic line _a2 . That is, even when only the burner device 2a for hot water supply is burned, the hot water supply characteristic varies depending on the opening amount of the gas proportional valve 18. It becomes the characteristic of characteristic line a1, and as the valve opening amount of the gas proportional valve 18 increases, it approaches the characteristic line _{a2 side} in _FIG . Means 52 proportionally controls the amount of supplied gas by controlling the valve opening amount of gas proportional valve 18 corresponding to the hot water supply set temperature and the hot water supply flow rate.

When the combustion capacity corresponding to the hot water supply demand capacity is further increased, the combustion control means 52 controls the combustion surfaces of the four burners 107 of the burner device 2a and the three burners 107 of the burner device 2b, that is, a total of seven burners. Combustion is performed on the combustion surface of 107 (see Table 1, hot water supply single combustion, switching stage number (2)). The hot water supply characteristics obtained by the combustion of the burner devices 2a and 2b are the hot water supply characteristics within the region sandwiched between the characteristic lines _b1 and b2 in _FIG . becomes possible.

That is, the hot water supply characteristics obtained by combustion of the _burner devices 2a and 2b correspond to the valve opening amount of the gas proportional valve 18, and when the valve opening amount of the gas proportional valve 18 is the minimum opening, As the valve opening amount of the gas proportional valve 18 increases, it approaches the characteristic line b2 _side in _FIG . The valve opening amount of the gas proportional valve 18 is controlled in accordance with the temperature and the hot water supply flow rate to proportionally control the supply gas amount.

Further, when the combustion capacity corresponding to the hot water supply demand capacity is further increased, the combustion control means 52 changes the combustion surfaces of the four burners 107 of the burner device 2a, the three burners 107 of the burner device 2b, and the combustion surfaces of the three burners 107 of the burner device 2c. Combustion is performed on the combustion surfaces of a total of thirteen burners 107 of the three burners 107 (see Table 1, hot water supply single combustion, switching stage number (3)). _The hot water supply characteristics obtained by combustion of these burner devices 2a, 2b, and 2c are sandwiched between the characteristic line c1 and the characteristic line c2 in _FIG . It is possible to supply hot water within the area.

That is, the hot water supply characteristics obtained by combustion of the burner devices 2a, 2b, and 2c correspond to the valve opening amount of the gas proportional valve 18, and when the valve opening amount of the gas proportional valve 18 is the minimum opening, the characteristic line _c1 in FIG. As the valve opening amount of the gas proportional valve 18 increases, it approaches the characteristic line c2 _side of _FIG . The amount of supplied gas is proportionally controlled by controlling the opening amount of the gas proportional valve 18 corresponding to the hot water supply set temperature and the hot water supply flow rate.

Further, the combustion control means 52 controls the hot water supply burner device 2 (2a , 2b and 2c), the heating burner device 5 on the lower side of the two-kind pipe installation portion 112 is burned (see single hot water supply combustion, number of switching stages (4) in Table 1). Also, at this time, the combustion control means 52 gives a command to the pump drive control means 55 to drive the circulation pump 9 for heating.

The hot water supply characteristics obtained by combustion of the hot water supply burner devices 2a, 2b, 2c and the heating burner device 5 are, for example, when the temperature of the water entering the hot water supply circuit 45 is ₁₅ ° C., and the characteristic line d1 in FIG. It is possible to supply hot water in the area sandwiched between lines _d2 and d2. That is, the hot water supply characteristics obtained by combustion of the burner devices 2a, 2b, 2c and the heating burner device 5 correspond to the valve opening amount of the gas proportional valve 18, and when the valve opening amount of the gas proportional valve 18 is the minimum opening degree, _The characteristics of the characteristic line d1 in _FIG . 5 are obtained, and as the valve opening amount of the proportional gas valve 18 increases, the characteristics of the characteristic line d2 in _FIG . 5 are approached. , the combustion control means 52 controls the gas proportional valve 18 corresponding to the hot water supply set temperature and the hot water supply flow rate.

Even in hot water supply independent operation, when the burner device 5 for heating is used for combustion, the liquid circulation pump 9 is driven to circulate the heat medium (hot water) in the heating circuit 7. By absorbing and recovering the heat on the heating circuit 7 side to the hot water supply side via the liquid _- water heat exchanger 33, high hot water supply in the area sandwiched between the characteristic line d1 and the characteristic line d2 in _FIG . It can supply hot water according to its capacity.

That is, in this embodiment, all the combustion surfaces of the hot water supply burner device 2 and the heating burner device 5 are burned, and in addition to controlling the valve opening amount of the gas proportional valve 18, the heat medium of the heating circuit 7 is At this time, the branching hot water supply side temperature variable means 51 opens the reheating liquid flow rate control valve 32, and the hot water supply circuit 7 from the hot water supply circuit via the hot water supply heating thermal connection liquid-water heat exchanger 33 By moving the heat to the 45 _side , it is possible to supply hot water with high hot water supply capacity in the area sandwiched between the characteristic line d1 and the characteristic line d2 in _FIG .

The combustion control means 52 controls the lower side of the two-kind pipe installation portion 112 when the necessary combustion capacity required for the heating operation is less than the predetermined heating control switching reference capacity (for example, 7.3 kw) during the heating single operation. The nine burners 109 of the heating burner device 5 are controlled on and off (on-off combustion (intermittent combustion) that repeats on and off at each predetermined on-off timing), and at this time, the gas proportional valve 18 is opened Minimize valve volume.

On the other hand, when the required combustion capacity required for the heating operation is equal to or higher than the heating control switching reference capacity, the nine burners 109 of the burner device 5 for heating continue to burn, and at this time, the required combustion capacity is reached. Correspondingly, the valve opening amount of the gas proportional valve 18 is controlled to proportionally control the supply gas amount.

In this embodiment, the combustion control means 52 has hot water supply/heating simultaneous operation control means (not shown), and when hot water supply and heating are simultaneously operated, the hot water supply/heating simultaneous operation control means performs control as follows. . In other words, the hot water supply/heating simultaneous operation control means is operated to give priority to the temperature adjustment on the hot water supply side, and the heating side is in the state obtained by the temperature adjustment on the hot water supply side (that is, temperature adjustment corresponding to the heating side). not performed) or stand by.

Specifically, when the required hot water supply capacity (required combustion capacity required for hot water supply operation) required of the heat source device is equal to or lower than the predetermined simultaneous combustion combustion surface switching reference capacity (for example, No. 4.6), Only the combustion control of the burner device 2 for hot water supply is performed while the combustion of the burner device 5 is stopped, and when the required hot water supply capacity is greater than the reference capacity for switching the combustion surface during simultaneous combustion (for example, No. 4.6), While burning the burner device 5, the combustion control of the burner device for hot water supply is performed in accordance with the required hot water supply capacity.

That is, in the region shown _on the characteristic line _a1 or to the left of the characteristic line a1 in FIG. In the area shown on the right _side of the characteristic line a1, the valve opening amounts of the gas solenoid valves 14 and 17 and the gas proportional valve 18 correspond to the required hot water supply capacity, as described below. control. For example, when the necessary combustion capacity first exceeds the switching reference capacity from a state smaller than the simultaneous combustion combustion surface switching reference capacity (for example, No. 4.6), first, nine of the heating burner devices 5 The combustion surface of the burner 107 is burned (see Table 1, hot water supply and heating simultaneous combustion, number of switching stages (1)).

In this embodiment, since the two-kind pipeline installation part 112 is provided above the heating burner device 5, the hot water supply side is heated even by combustion of only the heating burner device 5, and the gas proportional The capacity of the hot water supply side also changes according to the valve opening amount of the valve 18. For example, when the temperature of the water entering the hot water supply circuit 45 is ₁₅ ° C., the characteristic line a1 and the characteristic line a2 in _FIG . The hot water supply characteristics of the area between the sides are obtained. That is, when the valve opening amount of the gas proportional valve 18 is the minimum opening, the characteristic of the characteristic line a1 in _FIG . ₆ is obtained. Since the characteristic of the characteristic line _a2 is obtained at the maximum opening, the hot water supply and heating simultaneous operation control means of the combustion control means 52 controls the valve opening amount of the gas proportional valve 18 corresponding to the hot water supply set temperature and the hot water supply flow rate. to proportionally control the amount of gas supplied.

Further, the hot water supply/heating simultaneous operation control means of the combustion control means 52 increases the required combustion capacity in accordance with the hot water supply demand capacity by one step, in addition to the burner device 5 for heating, the three burners 107 of the burner device 2b are activated. Combustion is performed on the combustion surfaces of a total of 12 burners 107 and 109 (see hot water supply/heating simultaneous combustion, switching stage number (2) in Table 1). At this time, the characteristic line b1 and the characteristic line b2 _side of _FIG . A hot water supply characteristic in the region between is obtained.

In other words, when the valve opening amount of the gas proportional valve 18 is the minimum opening, the characteristic of the characteristic line b1 in _FIG . ₆ is obtained. The characteristics of the characteristic line b2 _are obtained at the maximum opening. Therefore, the hot water supply/heating simultaneous operation control means of the combustion control means 52 controls the valve opening amount of the gas proportional valve 18 corresponding to the hot water supply set temperature and the hot water supply flow rate to proportionally control the supply gas amount.

The hot water supply/heating simultaneous operation control means of the combustion control means 52 changes the hot water supply request capacity from a state greater than the simultaneous combustion combustion surface switching reference capacity to a switching reference capacity or less. When the state changes from the switching reference capacity or less to the switching reference capacity or higher, the combustion of the heating burner device 5 is not immediately started even if the combustion surface switching reference capacity during simultaneous combustion is exceeded (the heating burner device 5 is not ignited), and an additional switching reference capability set to a value larger than the simultaneous combustion combustion surface switching reference capability (for example, here, the capability corresponding to the characteristic line b1 in FIG. ₆ ) , the ability to burn the heating burner device 5 and the hot water supply burner device 2b with the minimum opening amount of the gas proportional valve 18), the heating burner device is burned and the heating burner device 5 and combustion control of the burner device 2 for hot water supply.

Then, the hot water supply/heating simultaneous operation control means of the combustion control means 52 stops combustion of the heating burner device 5 when the hot water supply demand capacity changes from a state larger than the switching reference capacity to a state equal to or lower than the switching reference capacity. Only the combustion control of the burner device 2 for supplying hot water is performed (as a standby for heating).

As described above, in this embodiment, under the control of the hot water supply/heating simultaneous operation control means of the combustion control means 52, when the hot water supply required capacity required for the hot water supply operation is greater than the predetermined switching reference capacity, the hot water supply required capacity By performing combustion control of the burner device 5 for heating or by performing combustion control of the burner device 5 for heating and the burner device 2 for hot water supply in correspondence, the first pipe line installation part 111 and the second pipe It is possible to appropriately heat the liquid distribution pipe 13 for hot water supply, which is arranged in both the channel arrangement portion 112, and supply hot water at an appropriate flow rate of the hot water supply set temperature.

On the other hand, when the required hot water supply capacity required for the hot water supply operation is equal to or less than the switching reference capacity, only the combustion control of the burner device 2 for hot water supply is performed while the combustion of the burner device 5 for heating is stopped. The liquid circulation pipeline 13 for supplying hot water arranged in the part 111 and the liquid circulation pipeline 13 for supplying hot water in the part of the second-class pipeline installation part 112 adjacent to the first-class pipeline installation part 111 are connected. It is possible to appropriately heat and supply hot water at an appropriate flow rate at the hot water supply set temperature without hardly heating the liquid distribution pipe 13 for hot water supply arranged in the second kind pipe installation part 112. .

In this embodiment, when the required hot water supply capacity required for the hot water supply operation is equal to or less than the switching reference capacity, the heating of the heat medium in the heating circuit 7 is not performed by stopping the combustion of the burner device 5 for heating. Since there is no heating side, the temperature of the heat medium on the heating side may drop, but since the user does not directly touch the heat medium on the heating side, it is difficult to perceive the drop in temperature of the heat medium. When the requested hot water supply capacity required for the hot water supply operation is equal to or less than the switching reference capacity, there is a high possibility that hot water is being supplied at a small flow rate in, for example, the kitchen or washroom, and this time may not last long. is high, it is considered that the simultaneous operation time of heating and hot water supply when the requested hot water supply capacity is equal to or less than the switching reference capacity is rather short.

Therefore, for example, if the hot water supply request capacity during simultaneous operation (operation) of hot water supply and heating is equal to or less than the switching reference capacity and the hot water supply is stopped, the heating becomes independent operation so that the burner device 5 for heating is burned. Therefore, the possibility that the heating burner device 5 does not burn for a long period of time even though the user desires the heating operation is very low. there is no hindrance to

Further, in this embodiment, when the hot water supply and heating are simultaneously operated, after the hot water supply request capacity required for the hot water supply operation changes from a state larger than the switching reference capacity to a switching reference capacity or less, the switching reference capacity is changed from a state of the switching reference capacity or less to the switching reference. When the state changes to exceed the capacity, the burner device 5 for heating is burned and the burner device 2 for hot water supply is burned when the additional switching reference capacity set to a value larger than the switching reference capacity is reached. Combustion control is also performed, and when the required hot water supply capacity required for the hot water supply operation changes from a value larger than the switching reference capacity to below the switching reference capacity, the combustion of the heating burner device 5 is stopped and the hot water supply burner is turned off. By performing only combustion control of the device 2, the following effects can be obtained.

In this embodiment, the switching means for switching the presence/absence of supply of the heat medium from the heating circuit 7 to the heating devices 70 and 71 is formed by the thermal valves 48 and 76 that open and close according to the temperature of the heat medium. The opening/closing control of the valves is not performed quickly like the electromagnetic valve, but is performed slowly. Opening and closing operations do not follow quickly.

On the other hand, as described above, the switching reference capability is used as a reference for stopping the heating burner device 5 at the time of simultaneous operation of hot water supply and heating, and the additional switching is used as a reference for restarting the combustion of the heating burner device 5. Two mutually different values of the standard capacity are given, the additional inclusion or the liquid adaptation force is set to a value higher than the switching standard capacity, and during the hot water supply and heating simultaneous operation, the heating for heating is performed according to these standard capacity and the hot water supply demand capacity. By stopping the burner device 5 and restarting combustion (reigniting), control adapted to the opening and closing operations of the thermal valves 48 and 76 is performed to frequently stop and restart combustion (on/off) of the burner device 5 for heating. can be prevented, and the life of the heating burner device 5 can be lengthened.

In addition, when the hot water supply request capacity is further increased, the hot water supply/heating simultaneous operation control means of the combustion control means 52 further increases a total of 22 burners 107 of the heating burner device 5 and all the hot water supply burner devices 2a, 2b, and 2c. (See Table 1, hot water supply and heating simultaneous combustion, number of switching stages (3)).

_At this time, the characteristic line d1 and the characteristic line d2 in _FIG . A hot water supply characteristic in the region between is obtained. That is, when the valve opening amount of the gas proportional valve 18 is the minimum opening, the characteristic of the characteristic line d1 in _FIG . ₆ is obtained. _The characteristic of the characteristic line d2 is obtained at the maximum opening. Therefore, the combustion control means 52 controls the valve opening amount of the gas proportional valve 18 corresponding to the hot water supply set temperature and the hot water supply flow rate to proportionally control the amount of supplied gas.

6, a total of 22 burners 107 and 109 of the heating burner device 5 and all the hot water supply burner devices 2a, 2b, and 2c were allowed to burn at maximum (the gas proportional valve 18 When combustion is performed with the opening degree maximized, the combustion heat amount of the heating burner device 5 is completely absorbed by the liquid distribution pipe 12 for heating, and the heat is absorbed by the liquid distribution pipe 13 for hot water supply. The hot water supply characteristics when it is not possible are shown.

As can be seen by comparing the characteristic line d2 and the characteristic line c in _FIG . If all the combustion heat of these burner devices 5, 2a, 2b, and 2c is absorbed by the hot water supply liquid flow conduit 13, the characteristics of the characteristic line d2 in _FIG . However, when all the combustion heat of the heating burner device 5 is absorbed by the heating liquid distribution pipe line 12, the characteristics of the characteristic line c in FIG. hot water supply capacity.

For this reason, for example, in the area within the dashed frame E in FIG. However, in this embodiment, a liquid-water heat exchanger 33 for hot water supply and heating thermal connection is provided, and the heat medium (hot water) in the heating circuit 7 is converted to the hot water supply circuit 45. By transferring heat to the heat medium (water), it is possible to make up for such a decrease in hot water supply capacity.

By the way, in a device that is provided with a single combustion fan 15 to perform hot water supply and heating operations as in the present embodiment, the combustion fan 15 can be used for hot water supply alone and heating alone. drive. Therefore, the burner device 2 for hot water supply and the burner device 5 for heating are arranged side by side. As for the configuration in which the heat exchanger is provided, when the heating operation is performed while the hot water supply operation is intermittently performed, the hot water remaining in the hot water supply heat exchanger is cooled by the air blown from the combustion fan 15 during the period when the hot water supply operation is stopped. This causes a cold water sandwich phenomenon in which the hot water supply temperature fluctuates.

On the other hand, in the present embodiment, a type 1 pipe line installation portion 111 in which a liquid flow pipe line 13 for hot water supply is arranged is provided above the burner device 2 for hot water supply, and is installed in parallel with the burner device 2 for hot water supply. On the upper side of the burner device 5 for heating, a two-kind pipe line installation part 112 is arranged in contact with the liquid circulation line 12 for heating so as to vertically sandwich the liquid circulation line 13 for hot water supply. The following effects can be obtained due to the characteristic configuration in which the

In other words, when the heating single operation is performed and the combustion fan 15 is driven together with the combustion of the heating burner device 5, the hot water staying in the liquid distribution pipe 13 of the first pipe installation portion 111 stops supplying hot water. Even if it is cooled by the wind from the combustion fan 15 thereafter, the hot water remaining in the liquid distribution pipe 13 of the second type pipe installation part is heated by the combustion of the burner device 5 for heating, so the main Warm water remains in the hot water supply liquid distribution pipe 13 forming the hot water supply heat exchanger, and the heat medium (hot water) supplied through the hot water supply circuit 45 is connected to the first type pipe installation part 111 and the heating Since hot water is supplied through the two-kind pipe line installation portion 112 heated by the burner device 5 for the cold water, the cold water sandwich phenomenon can be suppressed.

In the present embodiment, as shown in the fourth figure from the right side of FIG. When the burner device 5 for liquid is burned, it is heated by the combustion gas that spreads and rises toward the burner device 2 for hot water supply from the combustion surface of the burner device 5, but the heat of the combustion gas is transferred to the lower side of the liquid flow pipe 13. Since most of the heat is absorbed by the liquid circulation pipeline 12 provided in contact with the liquid circulation pipeline 13, the heat quantity of the combustion gas absorbed by the liquid circulation pipeline 13 is not so large.

Therefore, even if this part of the liquid distribution pipe 13 is heated by the spread of the combustion gas from the heating burner device 5, this alone cannot suppress the cold water sandwich phenomenon of the hot water supplied. The liquid distribution pipes 13 (the first, second, and third liquid distribution pipes 13 from the right side in FIG. 2) arranged above the heating burner device 5 are used for combustion of the heating burner device 5. The heat of the gas can be sufficiently absorbed, and warm water remains in these liquid distribution pipes 13, so that the cold water sandwich phenomenon can be suppressed as described above.

In other words, the configuration of the present embodiment can suppress the boiling of the liquid (water) in the liquid distribution pipe 13 on the hot water supply side during single heating operation, and can operate efficiently. It is also possible to suppress the cold water sandwich phenomenon that is a concern when heating operation is performed while cooling.

As in the heat source device shown in FIG. 11, the burner device 2 for supplying hot water and the burner device 102 for reheating the bath are arranged side by side, and the liquid distribution pipe for supplying hot water is placed above the burner device 2 for supplying hot water. In the case of a configuration in which a passage 13 is provided, a reheating liquid distribution pipe 105 is provided above the reheating burner device 102, and combustion fans are provided on the hot water supply side and the reheating side, both of them can be used. The combustion fan is driven both during hot water supply independent operation and reheating independent operation. In this case, however, the combustion fan on the non-combustion side is driven to prevent the combustion gas from flowing backward, so the amount of air blown is small.

In other words, the blowing of air for preventing the backflow of the combustion gas does not significantly decrease the temperature of the hot water in the heat exchanger on the side where combustion is not performed, and the two combustion fans as shown in FIG. In the configuration in which 15 is provided, there is little concern about the occurrence of the cold water sandwich phenomenon, but as described above, if a partition or the like is not provided, water in the heat exchanger on the non-burning side during single combustion for hot water supply and reheating This will cause problems such as boiling.

On the other hand, the heat source device of this embodiment can prevent the problem of boiling of the heat medium such as water, and can suppress the cold water sandwich phenomenon as described above. It is an excellent heat source device capable of stabilizing the temperature of hot water supply even when heating is simultaneously operated, and furthermore, it is possible to reduce the cost because of its simple configuration.

As a modification of this embodiment, FIG. 7 shows the thermal connection configuration of the outlet-side passage of the latent heat recovery hot water supply heat exchanger 4 to the hot water supply/heating thermal connection liquid-water heat exchanger 33. An example of a configuration different from that of FIG. 1 is shown. In the example shown in FIG. 7, in the hot water supply and heating thermal connection liquid-water heat exchanger 33, by driving the heating circulation pump 9, the liquid flowing out from the heating liquid distribution line 12 of the composite heat exchanger 1 A hot heat medium (here, water) is introduced and flows as indicated by arrow B in FIG. ) is introduced into the hot water supply/heating thermal connection liquid-water heat exchanger 33 and circulated.

That is, the heat medium introduced into the hot water supply/heating thermal connection liquid-water heat exchanger 33 from the heating liquid distribution pipe 12 side is introduced from the water supply side outlet of the hot water supply/heating thermal connection liquid-water heat exchanger 33. The water that flows in and is introduced from the hot water supply heat exchanger 4 for latent heat recovery into the hot water supply/heating thermal connection liquid-water heat exchanger 33 is the heat medium outlet ( A liquid-water heat exchanger 33 for hot water supply/heating thermal connection is formed by opposing heat exchangers in which the water flows in from the water outlet) and the heat medium from the liquid distribution pipe 12 flows in opposite directions. ing. For example, while introducing a hot heat medium (here, hot water) heated from the heating liquid distribution pipe 12 into the hot water supply heating thermal connection liquid-water heat exchanger 33, the hot water supply heat exchanger 4 for latent heat recovery When warm hot water or water is introduced into the hot water supply/heating thermal connection liquid-water heat exchanger 33, the heat on the heating circuit side can be transferred to the hot water supply circuit side (the hot water supply side can absorb the heat on the heating side).

FIG. 8 shows the configuration of the heat source device including the configuration of the reference example as the system configuration of the second embodiment, and the second embodiment will be described below. In the explanation of the second embodiment, the parts having the same names as those of the first embodiment are denoted by the same reference numerals, and redundant explanations thereof will be omitted or simplified.

As shown in FIG. 8, the second embodiment has a hot water supply and heating thermal system which is provided on the inlet side of the liquid distribution pipe line 13 (main hot water supply heat exchanger) of the composite heat exchanger 1 in the first embodiment. The connection liquid-water heat exchanger 33 is provided on the outlet side of the hot water supply liquid circulation pipe 13 (main hot water heat exchanger) forming the composite heat exchanger 1, and is configured in this first embodiment. The configuration of the portion different from the configuration of the reference example.

Further, in the second embodiment, as in the modification of the first embodiment, the liquid-water heat exchanger 33 for hot water supply/heating thermal connection is formed by opposed heat exchangers. That is, in the second embodiment, the hot water supply/heating thermal connection liquid-water heat exchanger 33 is introduced into the hot water supply/heating thermal connection liquid-water heat exchanger 33 from the heating liquid flow pipe line 12 side. The heat medium flows from the water supply side outlet of the hot water supply and heating thermal connection liquid-water heat exchanger 33, and the water introduced from the main hot water supply heat exchanger to the hot water supply and heating thermal connection liquid-water heat exchanger 33 is Counter heat exchange in which the water flows in from the heat medium outlet (water outlet) of the liquid-water heat exchanger 33 for hot water supply and heating thermal connection, and the heat medium from the liquid distribution pipe 12 flows in opposite directions to each other. It is made up of vessels.

Except for these differences, the configuration of the second embodiment is the same as that of the first embodiment, and the second embodiment can achieve substantially the same effects as the first embodiment and its modification.

It should be noted that the present invention is not limited to the above embodiments, and can take various forms without departing from the technical scope of the present invention. For example, each of the above embodiments has a control configuration as shown in FIG. 3, but the control configuration in the heat source device of the present invention is not particularly limited and may be set as appropriate.

Moreover, the heat source device of the present invention does not necessarily have the composite heat exchanger 1 as shown in FIG. can also be Thus, in the heat source device of the present invention, like the two-kind pipe line installation portion 112 of the composite heat exchanger 1 applied to each of the above embodiments, the main liquid distribution pipe line of the main hot water supply heat exchanger is It has at least a part of the two-kind pipe installation part 112 arranged in contact with each other in a manner sandwiched vertically by the liquid distribution pipe of the heating heat exchanger, and two of the two-kind pipe installation parts 112 It suffices that the seed liquid flow conduits 12, 13 have a configuration in which they are heated by a common burner device.

In addition, in the case of the configuration as shown in FIG. 9, the burner device can be formed by providing, for example, one burner device having a plurality of switchable combustion surfaces, and FIG. It schematically shows a state in which one is burning. Further, in a system configuration having a heat exchanger configured as shown in FIG. It becomes a form that extends over the entire arrangement position of 13.

Further, the heat source device of the present invention is formed, for example, in a configuration as shown in FIG . The details of the system configuration are not particularly limited as long as the passage (duct) on the entrance side of the heat exchanger and the heating circuit 7 are thermally connected, and can be set as appropriate. By enabling the circulation path switching of the heat medium of the heating circuit 7 by the hot water supply side temperature varying means 51 to be performed as in each of the above embodiments, the same effects as those of the above embodiments can be obtained. For example, in each of the above-described embodiments, a method of obtaining the temperature of the incoming water by calculation was applied without providing the incoming water temperature detection means for detecting the temperature of the incoming hot water. good too.

Furthermore, the branching hot water supply side temperature varying means 51 preferably performs both opening/closing control and valve opening amount control of the reheating liquid flow control valve, but may perform only opening/closing control.

Moreover, it may have other functions such as a heat collecting function for collecting solar heat, and a configuration such as a hot water storage tank.

Furthermore, the post-heat exchange water temperature detection means 133 may be omitted. However, if the post-heat-exchange water temperature detection means 133 is provided, it is possible to accurately grasp the capacity of the hot water supply/heating connection liquid (water heat exchanger 33), and it is easy to grasp the state of heat transfer from the heating circuit 7 side to the hot water supply circuit 45 side. Therefore, it is preferable.

Further, the heat source device of the present invention may be provided with a burner device for burning oil instead of the burner device for gas combustion provided in each of the above embodiments.

INDUSTRIAL APPLICABILITY The present invention can provide sufficient hot water supply and heating capacity even in a small size, and can suppress boiling of the heat medium in the heat exchanger during single operation of hot water supply and heating, so it can be used as a heat source device for home and business use. Available.

REFERENCE SIGNS LIST 1 heat source device 2 hot water supply burner device 4 hot water supply heat exchanger for latent heat recovery 5 heating burner device 6 heating heat exchanger for latent heat recovery 7 heating circuit 8 heating liquid circulation passage 9 heating circulation pump 10 cistern Reference Signs List 12, 13 Liquid distribution pipe 14, 17 Gas solenoid valve 15 Combustion fan 18 Gas proportional valve 19 Water quantity sensor 20 Water quantity servo 24 Hot water output thermistor 23 Heat exchange side thermistor 25 Bath heat exchanger 32 Liquid distribution control valve for reheating 33 Hot water supply Liquid-water heat exchanger for heating connection 40 Heating high temperature thermistor 41 Heating low temperature thermistor 51 Hot water supply side temperature variable means for branching 52 Combustion control means 53 Remote controller 56 Hot water supply side temperature variable means for branching 54 Control means 55 Pump drive control means 111 1 type Pipeline installation portion 112 Type 2 pipeline installation portion 133 Post-heat exchange water temperature detection means

Claims (6)

A hot water supply heat exchanger, a hot water supply circuit having a function of heating water, which is a liquid heat medium, by the hot water supply heat exchanger and supplying hot water to a hot water supply destination, a heating heat exchanger, and a heating heat exchanger. a heating circuit including a heating circulation pump for circulating a heat medium, supplying the heat medium from the heating circuit to a heating device connected to the outside and circulating the heat medium through the heating circuit. wherein the hot water heat exchanger has a main hot water heat exchanger for recovering sensible heat of the combustion gas of the burner device through a liquid flow conduit forming the hot water heat exchanger, and the heat exchange for heating The apparatus has a main heating heat exchanger for recovering the sensible heat of the combustion gases of the burner unit by means of a liquid distribution line forming said heating heat exchanger, said main hot water heat exchanger liquid distribution line. has at least a part of the two-kind pipe installation portion disposed in contact with each other in a manner sandwiched vertically by the liquid distribution pipes of the main heating heat exchanger, and the two-kind pipe installation portion A combined heat exchanger having a configuration in which the two types of liquid distribution pipelines are heated by a common burner device, and the main heating heat exchanger is provided on the outlet side of the main heating heat exchanger A going-side passage is formed for circulating the liquid that has passed through toward the heating device, and a return-side passage is formed for returning the liquid that has passed through the heating device to the main heating heat exchanger, A tip end side of a branch passage branched from the side passage is connected to the return side passage, and the branch passage is thermally connected to the inlet side passage of the main hot water supply heat exchanger. A heat source device characterized by being provided with a liquid-water heat exchanger for hot water supply and heating thermal connection to be connected. 2. The liquid branch variable means for varying at least one of whether or not the liquid that has passed through the main heating heat exchanger is branched to the branch passage side and the flow rate of the branched liquid is provided. heat source equipment. The hot water supply circuit has a latent heat recovery hot water supply heat exchanger for recovering the latent heat of the combustion gas, and the latent heat recovery hot water supply heat exchanger is connected to the inlet side of the main hot water supply heat exchanger via a pipe line. and the liquid-water heat exchanger for hot water supply/heating thermal connection is thermally connected to a pipeline between the latent heat recovery hot water supply heat exchanger and the main hot water supply heat exchanger. 3. The heat source device according to claim 1 or 2, characterized in that: A reheating circulation passage is provided for reheating hot water in the bathtub connected to the bathtub, and a liquid-water heat exchanger for reheating is provided for thermally connecting the reheating circulation passage and the branch passage. 4. The heat source device according to claim 1, wherein the heat source device is characterized by: 5. The liquid-water heat exchanger for reheating is provided upstream of the liquid-water heat exchanger for hot water supply and heating thermal connection in the flow of the liquid in the branch passage according to claim 4. heat source equipment. 6. The hot water supply circuit according to claim 1, further comprising a water volume servo for variably adjusting a total volume of hot water supplied through the hot water supply circuit. heat source equipment.

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