JP7217628B2 - 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. 14 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

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, there arises a problem that the heating capacity is insufficient with respect to the required capacity.

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. This makes one feel very uncomfortable, and in consideration of comfortable use, it is necessary to prevent hunting of the burner device, for example.

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 includes a hot water supply heat exchanger, a hot water supply circuit having a function of heating water as a 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 heating heat exchanger. a heating circuit comprising a heating circulation pump for circulating a liquid heat medium through a heat exchanger; supplying the heat medium from the heating circuit to a heating device connected to the outside; The hot water heat exchanger has a main hot water heat exchanger for recovering the sensible heat of the combustion gas of the burner unit by means of liquid flow conduits forming the hot water heat exchanger. , the heating heat exchanger has a main heating heat exchanger for recovering sensible heat of the combustion gas of the burner device through a liquid flow conduit forming the heating heat exchanger, and the main hot water supply heat exchange and a liquid distribution pipe for the main heating heat exchanger, which is the liquid distribution pipe for the main hot water supply heat exchanger. The hot water supply heat exchanger and the heating heat exchanger form a composite heat exchanger, and have a two-kind pipe installation portion that is arranged in contact with each other in a manner sandwiched vertically by the channels. A hot water supply burner device and a heating burner device are separately arranged on the lower side of the composite heat exchanger. The two types of liquid distribution pipelines of the seed pipeline installation portion are heated, and the fuel gas is supplied to the burner device corresponding to each of the hot water supply burner device and the heating burner device. In addition to providing a gas on-off valve that shuts off the gas, a gas proportional valve that uniformly varies the gas supply ratio to both burner devices is provided, and heating operation and hot water supply operation are performed at the same time. Combustion burner determination control for controlling whether to burn only the heating burner device or to burn the hot water supply burner device in addition to the heating burner device according to the hot water supply capacity required during operation, and the combustion burner determination. In the combustion of the combustion burner determined by control, the opening degree of the gas proportional valve is increased as the required hot water supply capacity increases in accordance with the required hot water supply capacity, and the opening of the gas proportional valve is increased as the required hot water supply capacity becomes smaller. Combustion control means for performing proportional valve opening degree control for reducing the opening degree according to a predetermined burner combustion control program, and the heat medium heated through the main heating heat exchanger and the main heat exchanger. Pass either the inlet or outlet passage of the hot water heat exchanger. A hot water supply and heating thermal connection liquid-water heat exchanger is provided for thermally connecting the heat medium to the hot water supply and heating, and when the heating and hot water supply are simultaneously operated, only the heating burner device is burned and the two types of pipes are burned. Means for solving the problem by a configuration having heat medium circulation path control means for circulating the heat medium for circulating the heating circuit through the liquid-water heat exchanger for hot water supply and heating thermal connection when heating the path installation portion. and

In a second invention, in addition to the configuration of the first invention, the heat medium circulation path control means burns only the heating burner device during simultaneous operation of the heating and the hot water supply to Instead of circulating the heat medium for circulating the heating circuit through the liquid-water heat exchanger for hot water supply/heating thermal connection when heating the installation portion, the heating burner device is used during simultaneous operation of the heating and hot water supply. When it is determined that hunting of the hot water supply burner device occurs due to the low temperature of the heat medium when heating the second kind of pipe installation portion by burning only the heat medium, the heat medium is circulated in the heating circuit. is circulated through the liquid-water heat exchanger for hot water supply and heating thermal connection.

Further, in a third invention, in addition to the configuration of the first or second invention, the heat medium circulation path control means predetermines the amount of heat exchanged by the liquid-water heat exchanger for hot water supply and heating thermal connection. The heat medium flow rate through the liquid-water heat exchanger for hot water supply and heating thermal connection is controlled so as to achieve a set heat exchange amount. The set amount of heat exchange may be one value, or may be a value having a specific range.

Furthermore, a fourth invention, in addition to the configuration of the first, second, or third invention, supplies liquid that has passed through the main heating heat exchanger to the outlet side of the main heating heat exchanger. A going-side passage is formed to circulate toward the heating device, and a return-side passage is formed to return the liquid that has passed through the heating device to the main heating heat exchanger side, and from the going-side passage A tip side of the branched passage is connected to the passage on the return side, and the liquid-water heat exchanger for hot water supply and heating thermal connection is provided in the branch passage.

Furthermore, in a fifth invention, in addition to the configuration of any one of the first to fourth inventions, the hot water supply burner device includes a plurality of burner devices, and the plurality of burner devices and the heating burner device are combined. A gas on-off valve is provided for switching the supply and shutoff of fuel gas to each burner device, and a gas proportional valve is provided for uniformly varying the ratio of gas supply to all burner devices. The number of burner stages, which is the number of combustion burners among the plurality of hot water supply burner devices, is increased according to a predetermined burner stage number variable program in accordance with the required hot water supply capacity to correspond to the required hot water supply capacity. Burner stage number control for decreasing the burner stage number as the burner stage number decreases, and corresponding to the required hot water supply capacity, the opening degree of the gas proportional valve is increased as the required hot water supply capacity increases, and the gas proportional valve is increased as the required hot water supply capacity becomes smaller. Combustion control means for performing proportional valve opening control for reducing the opening of the proportional valve, wherein the combustion control means has a setting capacity that predetermines the required hot water supply capacity during simultaneous operation in which the heating operation and the hot water supply operation are performed at the same time. When the capacity is less than the set capacity, only the heating burner device is burned, and when the capacity is equal to or higher than the set capacity, in addition to the combustion of the heating burner device, the hot water supply burner device is burned according to the burner stage variable program. and

Furthermore, in the sixth invention, in addition to the configuration of the fifth invention, when there is no region in which the hot water supply capacity is the same in the vertically adjacent stages of the burner stage variable program, the same area is formed. The heat medium circulation path control means circulates the heat medium heated through the main heating heat exchanger through the hot water supply/heating thermal connection liquid-water heat exchanger to circulate through the heating circuit. It is characterized in that the heat of the heat medium is transferred to the hot water supply circuit side.

Furthermore, in a seventh invention, in addition to the configuration of any one of the first to sixth inventions, at least one of the main hot water supply heat exchanger and the main heating heat exchanger has the burner device. A latent heat recovery heat exchanger for recovering latent heat of combustion gas is connected.

According to the present invention, a first-class pipeline installation section in which only a liquid distribution pipeline for hot water supply forming a main hot water supply heat exchanger provided in a hot water supply circuit is arranged; the main hot water supply heat exchanger; and a two-kind pipe installation portion in which a liquid distribution pipe of a main heating heat exchanger provided in a heating circuit is arranged, wherein the hot water supply heat exchanger and the heating heat exchanger are combined heat. Since it is formed as an exchanger, it is possible to reduce the size of the heat source device as compared with the case where the main hot water supply heat exchanger and the main heating heat exchanger are separately formed and provided.

In addition, in the two-kind pipe arrangement portion of the composite heat exchanger, the heating liquid distribution pipes of the heating heat exchanger are provided above and below the liquid distribution pipe of the main hot water heat exchanger. , The lowermost (lowest position) passage of the second type pipe installation part is a liquid distribution pipe for heating, and the liquid (heat medium) flowing through this pipe is heated and circulated. However, even if the circulation is stopped, it is rarely as cold as the liquid distribution line for hot water supply, in which cold water is introduced from the water supply side. It is possible to prevent condensation from occurring in the pipeline.

Furthermore, according to the present invention, in the two-kind pipe arrangement portion of the composite heat exchanger, the liquid distribution pipe for heating of the heat exchanger for heating is arranged above and below the liquid distribution pipe for the main hot water supply heat exchanger. is provided, it is possible to increase the arrangement ratio of the liquid distribution pipes for heating, and to obtain sufficient heating capacity by heating the part where the second kind of pipes are arranged by the heating burner device. On the other hand, regarding the hot water supply operation, depending on the hot water supply capacity, the liquid distribution pipe for hot water supply arranged in the second kind pipe installation part is heated by the hot water supply burner device, or the first kind pipe installation part is heated. Sufficient hot water supply capacity can be obtained by heating an appropriate liquid flow line among the provided hot water supply liquid flow lines with a hot water supply burner device.

Further, in the present invention, at the time of simultaneous heating and hot water supply operation in which heating operation and hot water supply operation are performed at the same time, only the heating burner device is burned or in addition to the heating burner device, in accordance with the required hot water supply capacity. combustion burner determination control for controlling whether the hot water supply burner device also burns, and in combustion of the combustion burner determined by the combustion burner determination control, corresponding to the required hot water supply capacity, the gas as the required hot water supply capacity increases. Combustion control means for performing proportional valve opening control for increasing the opening of the proportional valve and decreasing the opening of the gas proportional valve as the required hot water supply capacity decreases according to a predetermined burner combustion control program. Therefore, burner combustion control can be accurately performed during the simultaneous operation of heating and hot water supply.

In addition, in the two-kind pipe arrangement portion of the composite heat exchanger as applied to the present invention, during simultaneous operation of hot water supply and heating, the combustion heat amount of the heating burner device is transferred to the liquid distribution pipe for heating. If a large amount of heat is absorbed, the hot water supply capacity decreases. Absorbs a large amount of combustion heat. Therefore, since the temperature of the heat medium is low, the hot water supply capacity exhibited when only the heating burner device is burned becomes small, and the hot water supply capacity and the hot water supply burner device in addition to the heating burner device. There are times when the hot water supply capacity cannot be accurately switched when the hot water is burned, and there is a possibility that hunting may occur in the hot water supply burner device.

On the other hand, in the present invention, the heat medium heated through the main heating heat exchanger and the heat medium passing through either the inlet side passage or the outlet side passage of the main hot water supply heat exchanger A liquid-water heat exchanger for thermally connecting the hot water supply and heating is provided, and the heat medium circulation path control means burns only the heating burner device during simultaneous operation of the heating and hot water supply. By circulating the heat medium that circulates the heating circuit through the liquid-water heat exchanger for hot water supply and heating thermal connection when heating the two-kind pipe installation part, such a problem (hot water supply burner (Occurrence of device hunting) can be prevented.

That is, when the heat medium circulating in the heating circuit is circulated through the liquid-water heat exchanger for hot water supply/heating thermal connection, the heat medium that has been heated through the heating liquid circulation pipe is heated. Since heat can be transmitted to the hot water supply circuit side, the hot water supply capacity exhibited when only the heating burner device is burned can be increased, and the hot water supply capacity and the hot water supply capacity can be combined with the heating burner device. It becomes possible to accurately switch the hot water supply capacity when the burner device is also used for combustion, so that hunting of the hot water supply burner device can be prevented.

As described above, in the two-kind pipe arrangement portion of the composite heat exchanger as applied to the present invention, during the simultaneous operation of hot water supply and heating, the combustion heat amount of the heating burner device is transferred to the heating liquid. If the flow pipe absorbs a large amount of heat, the hot water supply capacity decreases. Therefore, if the temperature of the heat medium passing through the liquid flow pipe for heating is low, there is a possibility that the hot water supply burner device will hunt (increase). . Therefore, when heating only the heating burner device during the simultaneous operation of heating and hot water supply to heat the two-kind pipe installation portion, the temperature of the heat medium is low, so that hunting of the hot water supply burner device occurs. If it is determined that the hot water supply burner device is circulated through the liquid-water heat exchanger for hot water supply heating thermal connection, the heat medium circulating in the heating circuit is circulated very accurately. can be prevented.

Further, in the present invention, the medium circulation path control means controls the hot water supply/heating thermal connection liquid so that the amount of heat exchanged by the hot water supply/heating thermal connection liquid-water heat exchanger becomes a predetermined set heat exchange amount. -By adopting a configuration that controls the flow rate of the heat medium passing through the water heat exchanger, for example, the heat medium that circulates in the heating circuit is added to the hot water supply heating thermal connection liquid-water heat exchanger hot water heat exchanger side It is possible to accurately suppress the problem that the heating capacity becomes insufficient due to the temperature of the heat medium circulating in the heating circuit becoming too low due to an excessive amount of heat. That is, it is possible to appropriately balance the hot water supply side and the heating side, and it is possible to realize a heat source device that is very convenient to use.

Further, an outgoing passage is formed on the outlet side of the main heat exchanger for heating so that the liquid that has passed through the main heat exchanger for heating flows toward the heating device. A return-side passage is formed to return the liquid to the main heating heat exchanger side, and the tip end of the branch passage branched from the going-side passage is connected to the return-side passage, and the branch passage According to the configuration in which the hot water supply and heating thermal connection liquid-water heat exchanger is provided, the heat medium for circulating the heating circuit is passed through the branch passage as necessary, and the hot water supply and heating thermal connection liquid - water heat By transmitting the heat of the heating circuit to the hot water supply circuit side via the heat exchanger, it is possible to make up for the lack of hot water supply capacity.

Further, the combustion control means increases the required hot water supply capacity according to a burner stage number variable program in which the burner stage number, which is the number of combustion burners among the plurality of hot water supply burner devices, is determined in advance in correspondence with the required hot water supply capacity. a burner stage number control for increasing the burner stage number as the required hot water supply capacity decreases and decreasing the burner stage number as the required hot water supply capacity becomes smaller; According to the configuration in which proportional valve opening degree control is performed to decrease the opening degree of the gas proportional valve as the required hot water supply capacity becomes smaller, the hot water supply operation can be performed finely and accurately.

Further, if there is no region in which the hot water supply capacity is the same in the number of stages adjacent to each other in the burner stage number variable program, the same area is formed. A medium circulation path control means circulates the heat medium circulating in the heating circuit through the liquid-water heat exchanger for hot water supply/heating thermal connection, and transfers the heat of the heat medium circulating in the heating circuit to the hot water supply circuit side. According to the transmission configuration, even if there is no region where the hot water supply capacity is the same in the number of stages adjacent to each other in the burner stage number variable program, the heat medium heated through the main heat exchanger for heating is used for the hot water supply and heating. When switching the number of burner stages between a plurality of hot water supply burner devices by circulating through the thermal connection liquid-water heat exchanger and transferring the heat of the heat medium circulating in the heating circuit to the hot water supply circuit side Hunting can be suppressed.

Furthermore, in the present invention, if at least one of the main hot water supply heat exchanger and the main heating heat exchanger is connected to a latent heat recovery heat exchanger for recovering the latent heat of the combustion gas of the burner device, the efficiency can be improved. Realization of an expensive heat source device can be made possible.

4 is a schematic graph for explaining the control method of the embodiment of the heat source device according to the present invention; FIG. 3 is an explanatory view schematically showing the arrangement configuration of a composite heat exchanger and a burner device in the heat source device of the embodiment; 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 latent heat recovery heat exchanger 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. FIG. 11 is a schematic system explanatory diagram for explaining the system configuration of the heat source device of the second embodiment; FIG. 11 is a schematic explanatory diagram showing the system configuration of the heat source device of the third embodiment; 4 is a graph schematically showing an example of the relationship between the degree of opening of the gas proportional valve and the hot water supply capacity during simultaneous operation of hot water supply and heating. FIG. 11 is a graph schematically showing another relationship example between the degree of opening of the gas proportional valve and the hot water supply capacity during simultaneous operation of hot water supply and heating; 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. 1 is a schematic explanatory diagram showing a configuration example of a conventionally proposed one-can two-channel type heat exchanger; FIG. 5 is a schematic graph for explaining a control method for performing combustion control by controlling the number of stages of a heating burner and a plurality of hot water supply burners.

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. 3 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 a burner device 2 (2a, 2b, 2c) for hot water supply and a burner device 5 for heating are provided. They are arranged separately on the lower side. A detailed configuration of the composite heat exchanger 1 will be described later.

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, each combustion surface of the burner devices 2a, 2b, and 2c forms a sectioned combustion surface, and the heat source device has the above-mentioned capacity every time the capability required of the burner device 2 for hot water supply is increased by one level. Combustion control means (not shown in FIG. 3) are provided for selectively sequentially additionally burning the segmented combustion surfaces in a predetermined order (the order of the burner devices 2a, 2b, 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. 3, 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. 3, and the surface direction of each fin 43 is orthogonal (or substantially orthogonal) to the arrangement direction of the burner devices 2a, 2b, 2c for supplying hot water. It is configured in such a manner as to be oriented. 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. 3 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 disposed on the upper side of the composite heat exchanger 1, and as shown in FIG. A partition 115 is provided on the upper side of the composite heat exchanger 1 to separate the installation space of the hot water supply heat exchanger 4 and the installation space of the latent heat recovery heating heat exchanger 6 . 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. 3 and FIG. 9, 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. 4, and may be set as appropriate. be.

As shown in FIG. 3, on the output side of the main heating heat exchanger, the liquid (hot water) that has passed through the main heating heat exchanger (heating liquid distribution line 12) is supplied to a heating device 70, A pipeline 60 is formed as a passage on the going side for circulating toward the 71 side, and a passage on the return side for returning the liquid (water) that has passed through the heating devices 70 and 71 to the latent heat recovery heating heat exchanger. A pipe line 61 is formed, and the tip side of a branch passage 65 branched from the pipe line 60 is connected to the pipe line 61. Hot water supply and heating thermal connection liquid-water heat thermally connected to either the inlet side passage or the outlet side passage (here, the inlet side) of the hot water supply liquid distribution pipe 13) forming the exchanger 1 A exchanger 33 is provided.

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. 6(a) and 6(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. Burner arrangement 2a is formed by three burners 107, burner arrangement 2b by five burners 107 and burner arrangement 2c by four burners 107, so that each burner arrangement 2a, 2b , 2c has an area ratio of approximately 3:5:4. The heating burner device 5 is formed by arranging four 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 the hot water supply burner device 2 (2a, 2b, 2c) and the heating burner device 5 through the gas supply passage 16 shown in FIG. Further, gas on-off valves (gas electromagnetic valves) 17 and 14 are provided corresponding to the plurality of burner devices 2a, 2b, 2c and the heating burner device 5, respectively, for supplying and shutting off the fuel gas to the burner devices. In addition, a gas proportional valve 18 is provided to uniformly vary the ratio of gas supply to all burner devices.

Further, as can be seen by referring to both FIG. 6 and FIG. 2, a composite heat exchange device is provided above each combustion surface of the burner device 2 (2a, 2b, 2c) for hot water supply and the burner device 5 for heating. The hot water supply liquid distribution line 13 of the unit 1 and the heating liquid distribution line 12 of the combined heat exchanger 1 are connected to the 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 supplying hot water have a pipeline part extending parallel or substantially parallel to the row of flame ports 110 of the burner device 2 (2a, 2b, 2c). 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.

As shown in FIG. 3, 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 supplies water, which is a liquid heat medium introduced from the water supply passage 46 and heated through the hot water supply heat exchanger 4 for latent heat recovery, to the liquid circulation pipe 13 ( After the water is introduced into the main hot water supply heat exchanger) and heated, the heated water is led through the hot water supply passage 47 to the hot water supply destination. 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 bypass servo 21 is controlled by the temperature on the outlet side from the liquid distribution pipe 13 for hot water supply (e.g., 60° C. detected by the thermistor 23 on the heat exchange side), the incoming water temperature, and the hot water supply set in the remote controller 53 . The temperature detected by the hot water supply thermistor 24 is compared with the hot water supply set temperature, and the hot water supply temperature is further controlled to match the hot water supply set temperature.

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 pipes (passages) 59 to 65 and 108, and the pipe 108 transfers the heat medium (for example, water) in the heating circuit 7 to the latent heat recovery heating heat exchanger. It functions as a latent heat heat exchange bypass passage for circulating without passing through 6. 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 .

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 (a high-temperature terminal that circulates at a heat medium temperature of, for example, 80° C.), 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 hot water mat (a low-temperature terminal with a heat medium temperature of 60° C. circulation, for example), and connects the passage inside the device case 80 of the heating liquid circulation passage 8 and the external passage 73. A selectively switching thermal valve 48 is provided to control the supply of heat transfer medium to the heating device 71 .

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 branching hot water supply side temperature variable means (reference numeral 51 in FIG. 3), which will be described later, to determine whether or not the heat medium is introduced into the branch passage 65 and to adjust the amount of introduction. , whether or not the heat medium is introduced into the liquid-water heat exchanger 25 for reheating and the liquid-water heat exchanger 33 for hot water supply/heating thermal connection and the amount of the heat medium introduced 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).

3, 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. are shown respectively.

Although the remote control device is not shown in FIG. 3, 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 provided in many cases, but in this specification they are collectively referred to as a remote control device 53, and in the explanation using FIG. will be explained.

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. 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, the heating circulation pump 9 is driven to circulate the liquid (hot water in this case). , 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.

After passing through the heating liquid circulation line 12 of the composite heat exchanger 1, the liquid then passes through the line 60 as indicated by arrow C, passes through a branch point, and is connected to, for example, the heating liquid circulation line 8. When the high temperature side heating device 70 is operated, as shown by arrow D, it is supplied to the high temperature side heating device, and after passing through the high temperature side heating device 70, it is shown by arrow D'. , and is introduced into the cistern 10 as indicated by the 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 in operation, the thermal valve 76 in the hot side heater 70 is closed and the liquid through line 60 as indicated by arrow D is shown by arrow H. As indicated by arrow G, it passes through a pipeline (latent heat exchange bypass passage) 108 and is introduced into the cistern 10 , and returns to the suction side of the heating circulation pump 9 through a pipeline 64 as indicated by arrow G.

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 (heat medium) branched after passing through the pipe line 60 ) passes through the branch passage 65 as indicated by the arrow E′, and passes through the reheating liquid-water heat exchanger 25 and the hot water supply heating thermal connection liquid-water heat exchanger 33 in order to the pipeline 61 go to the side. By circulating the hot water in the bathtub 75 in the reheating circulation passage 26 while passing the liquid maintained at a high temperature through the reheating liquid-water heat exchanger 25, the bath is properly reheated. The liquid that has passed through the conduit 61 returns to the suction side of the heating circulation pump 9 through the conduit 62, the cistern 10, and the conduit 64, 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 conduit 63 for supplying liquid to a low-temperature side heating device 71 such as a hot water mat. is turned on, the liquid maintained at a low temperature (eg, 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. supplied.

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 of the bathtub 75, there is a control example using a control configuration as shown in FIG. In addition to the examples, appropriate known control methods and appropriate control methods that will be proposed in the future are applied.

The control configuration shown in FIG. 12 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 a 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., the pipe 72 on the outlet side of the heating device 70 and the pipe. It passes through the path 74 and is introduced into the heating heat exchanger 6 (latent heat exchanger) through the pipeline 61 as indicated by the arrow D' in FIG. 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 circulation 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 . Note that the reheating liquid-water heat exchanger 25 can also be called a high-temperature heating device (it is equivalent to a high-temperature heating device in that a high-temperature heating load is generated).

Also, when the high-temperature heating device 70 operates, the combustion control means 52 opens the thermal valve 48 when operating the low-temperature heating device 71 so that the liquid at 60° C. can be normally supplied to the low-temperature heating device 71 . At this time as well, 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 supplied from the main heating heat exchanger 11. A liquid having an appropriate temperature (for example, about 80° C.) is drawn out. This liquid flows as indicated by arrows C and D in FIG. The mixture is supplied to the low-temperature heating device 71 through the line 64 , the heating circulation pump 9 and the line 63 in this order.

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 conduit of the high-temperature heating device 70, so the temperature drops to, for example, about 60° C. The liquid introduced and mixed in the cistern 10 is introduced into the low-temperature heating device 71 through the pipeline 73 as indicated by the arrow in FIG. The temperature of the liquid is lower than if the liquid were introduced directly from the heat exchanger. 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 capacity switching valve (thermal valve) 118 is opened to increase the amount of heat medium sent from the main heating heat exchanger to the cistern 10, and at the same time, the combustion amount of the burner 5 is adjusted. It is sent to line 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 60 .

Even when only the low-temperature heating device 71 is operated, the liquid that has passed through the low-temperature heating device 71 is introduced into the conduit 61 through the conduits 73 and 74 on the outlet side of the low-temperature heating device 71 .

A bath set temperature input operation unit 163 shown in FIG. 12 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. It will turn off automatically after keeping warm and water for a long time. 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 hot water temperature in the bathtub detected by the bath thermistor 28 obtained by driving the bathtub hot water circulation pump 27 is lower than the bath set temperature, the burner 5 is combusted and the heating circulation pump 9 is driven as described above. Meanwhile, the reheating liquid flow rate control valve 32 is opened and the bathtub hot water circulation pump 27 is turned on so that the bath set temperature is reached, 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. 5 is a block diagram showing the control configuration of the heat source device of this embodiment. It has means 52 and pump drive control means 55 . The control device 54 includes a remote controller 53, a hot water outlet thermistor 24, a water quantity sensor (flow rate sensor) 19, post-heat exchange water temperature detection means 133, a reheating liquid flow rate control valve 32, gas solenoid valves 14 and 17, a gas proportional Signal connections are made to the valve 18 , the combustion fan 15 , the heating circulation pump 9 , the heating high temperature thermistor 40 , the heating low temperature thermistor 41 , and the heat exchange side thermistor 23 .

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 device 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. The details are as described above.

In this embodiment, in hot water supply only operation, heating only operation, and simultaneous heating operation and hot water supply operation, respectively, It has the structure which switches combustion of the corresponding burner device 2 (2a, 2b, 2c) for hot water supply, and the burner device 5 for heating. That is, the combustion control means 52 controls the opening and closing of the gas on-off valves 17 and 14 corresponding to the plurality of burner devices 2 (2a, 2b, 2c) for supplying hot water and the burner device 5 for heating, respectively. By uniformly controlling the gas supply rate to all the burners 2 and 5 by controlling the valve 18, the hot water supply single operation, the heating single operation, and the simultaneous hot water supply and heating operation are appropriately performed.

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 three burners 107 of the burner device 2a for hot water supply. is. The number of switching stages in Table 1 is the number of switching stages of the burner devices 2 and 5, and is the number of burner stages. In Table 1, as shown in FIG. 2, 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 the 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 increases the combustion surfaces of the three burners 107 of the burner device 2a and the five burners 107 of the burner device 2b, for a total of eight burners. Combustion is performed on the combustion surface of 107 (see switching stage number (2) in Table 1). 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 degree, 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 12 burners 107 of the three burners 107 (see the switching stage number (3) in Table 1). _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 burner device 5 for heating on the lower side of the type 2 pipeline installation portion 112 is burned (see the switching stage number (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 the combustion of the hot water supply burner devices 2a, 2b, 2c and the heating burner device 5 are, for example, when the temperature of water entering the hot water supply circuit 45 is ₁₅ ° C., 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, _The characteristics of the characteristic line d1 in _FIG . 7 are obtained, and as the valve opening amount of the proportional gas valve 18 increases, the characteristics of the characteristic line d2 in _FIG . 7 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.

That is, even during the hot water supply single operation, when the burner device 5 for heating is burned, the liquid circulation pump 9 is driven to circulate the heat medium (hot water) in the heating circuit 7, and the hot water supply heating thermal connection is performed. 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 appropriately opens the reheating liquid flow rate control valve 32, and hot water supply from the heating circuit 7 side via the hot water supply heating thermal connection liquid-water heat exchanger 33 By transferring heat to the circuit 45 side, it is possible to supply hot water with _a high hot water supply capacity in the area sandwiched between the characteristic lines d1 and d2 in _FIG .

In addition, the combustion control means 52, during the heating single operation, when the required combustion capacity required for the heating operation operation is less than the predetermined heating control switching reference capacity (for example, 7.3 kw) The four burners 109 of the burner device 5 for heating on the lower side are on/off controlled (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 to minimize the amount of valve opening.

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

Further, when the heating operation and the hot water supply operation are performed simultaneously, the combustion control means 52 either burns only the heating burner device 5 or burns the heating burner device 5 in accordance with the required hot water supply capacity. Combustion burner determination control for controlling whether to burn the burner device 2 for hot water supply in addition to the device 5; Proportional valve opening control for increasing the opening of the gas proportional valve 18 as the capacity increases and decreasing the opening of the gas proportional valve 18 as the required hot water supply capacity decreases according to a predetermined burner combustion control program. conduct.

In the present embodiment, the hot water supply burner device 2 is formed to have a plurality of hot water supply burner devices 2a, 2b, and 2c. Burner stage number control is also performed to control the number of burner stages, which is the number of combustion burners, of the burner devices 2a, 2b, and 2c for use according to a predetermined burner stage number variable program (the burner combustion control program is a program that also includes the burner stage number variable program). be).

Control according to the variable burner stage number program is control in which the burner stage number is increased as the required hot water supply capacity increases, and the burner stage number is decreased as the required hot water supply capacity decreases. Further, the combustion control means 52 increases the opening degree of the gas proportional valve 18 as the required hot water supply capacity increases, corresponding to the required hot water supply capacity at the same number of burner stages, and increases the opening degree of the gas proportional valve 18 as the required hot water supply capacity decreases. Proportional valve opening control is performed to reduce the opening of the proportional valve 18 .

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 capacity required of the burner device 2 for hot water supply is increased by one step, During the simultaneous operation of hot water supply and heating, burner stage number control shown in Table 2, for example, is performed.

In Table 2, the surfaces indicate the combustion surfaces of the burner devices 2 and 5 for hot water supply and heating. B, C indicates the combustion surface of the burner device 2c for hot water supply, and D indicates the combustion surface of the burner device 5 for heating.

With this control, for example, when the temperature of the heat medium on the exit side of the hot water supply liquid circulation line 13 is 60° C. and the temperature of the heat medium on the exit side of the heating liquid circulation line 12 is 60° C., The relationship between the number of burners fired and the hot water supply capacity (hot water supply number) is as shown by characteristic lines Sa to Sd in FIG. 15, for example. The characteristic line Sa shows the relationship between the number of burners and the capacity when the number of burner stages is 1, the characteristic line Sb is the number of burners of 2, the characteristic line Sc is the number of burners of 3, and the characteristic line Sd is the number of burners of 4. .

For example, as shown by the characteristic line Sa in FIG. 15(a), only the burner device 5 for heating ( The required hot water supply capacity can be obtained even with combustion of four burners), but in the range of Nos. 4.5 to 6.25 (range Rab) where the characteristic line Sa and the characteristic line Sb overlap, Combustion control according to the characteristic line Sb may be combustion of the heating burner device 5 and the hot water supply burner device 2a (seven burners). However, it is one of the important points to improve the thermal efficiency in the combustion apparatus, and in the configuration like the heat source apparatus of the present embodiment, the higher the number of burner stages, the higher the thermal efficiency.

Therefore, for example, when the required hot water supply number is 5 or higher, the number of burner stages is increased by one to switch to combustion control according to the characteristic line Sb, and at the same time, the opening degree of the gas proportional valve 18 is reduced (for example, minimized). ), the burner device 5 for heating (combustion surface D of four burners) and the burner device 2a for hot water supply (combustion surface A of three burners) are burned (a total of seven burner devices are burned). I), combustion control is performed to increase the thermal efficiency. Although the characteristic line Sb is 4.5 or more, as is well known, the control characteristic line is provided with hysteresis (for example, about 0.5) to prevent hunting of the hot water supply burner device 2. Here, when the number of burner stages is increased, the characteristic line Sb is followed when, for example, the required number of hot water supply is No. 5 or higher.

As the required capacity increases, the opening of the proportional gas valve 18 is increased as the required capacity increases. In the same manner as described above, in the region (8.125 to 11) (range Rbc) where the characteristic line Sb and the characteristic line Sc overlap, the combustion control may be similarly performed according to the characteristic line Sb. However, since combustion control according to the characteristic line Sc is also possible, in order to increase the thermal efficiency in the same manner as described above, for example, when the required capacity reaches approximately 8.625, the number of burner stages is increased by one (characteristic line Sc , the combustion surface B of the burner device 2b for hot water supply is also burned to burn a total of 12 burner devices).

Further, in the area (No. 10.875 to No. 18.75) (range Rcd) where the characteristic line Sc and the characteristic line Sd overlap, the combustion control may be performed according to the characteristic line Sc or according to the characteristic line Sd. In order to increase the thermal efficiency in the same manner as described above, for example, when the required capacity reaches about 11.375, the number of burner stages is increased by one (corresponding to the characteristic line Sd, Combustion surfaces A to C of the burner devices 2a to 2c and combustion surface D of the burner device 5 for heating are burned to burn a total of 16 burner devices).

In this way, as the required capacity increases, the control to increase the opening of the gas proportional valve 18 and the control to sequentially increase (increase) the number of burner stages are performed. In the overlapping regions (range Rab, range Rb, range Rcd), the opening degree of the gas proportional valve 18 is reduced as much as possible as a control according to the characteristic line corresponding to the burner stage number one step higher. control is performed.

On the other hand, when the required capacity becomes smaller, the following control is normally performed. That is, as shown by the characteristic line Sd in FIG. 15(b), when the required capacity is No. 24 to about No. 10.875, the heating burner device 5 and the hot water supply burner devices 2a, 2b, and 2c is burned (combustion is performed on the combustion surfaces A, B, C, and D of a total of 16 burner devices), and the opening of the gas proportional valve 18 is decreased as the required capacity decreases, corresponding to the capacity. do. Then, when the required capacity reaches approximately 10.875, the number of burner stages is lowered by one (control according to the characteristic line Sc), and the opening of the gas proportional valve 18 is controlled corresponding to the characteristic line Sc. Then, the combustion surface D of the heating burner device 5 and the combustion surfaces A and B of the hot water supply burner devices 2a and 2b are burned.

When the required capacity becomes smaller, the opening of the gas proportional valve 18 is decreased, and when the required capacity reaches about 8.125, the number of burner stages is lowered by one (control according to the characteristic line Sb). The opening degree of the gas proportional valve 18 is controlled in accordance with the characteristic line Sb to burn the heating burner device 5 and the hot water supply burner device 2a. When the required capacity becomes smaller, the opening of the proportional gas valve 18 is decreased, and when the required capacity reaches about No. 4.5, the number of burner stages is lowered by one (control is performed according to the characteristic line Sa). At the same time, the opening degree of the gas proportional valve 18 is controlled in correspondence with the characteristic line Sa, and only the heating burner device 5b is burned.

That is, as the required performance becomes smaller, the control to decrease the opening of the gas proportional valve 18 and the control to sequentially decrease (lower) the number of burner stages are performed, and the characteristic lines Sa to Sd in FIG. In the overlapping area (range Rab, range Rb, range Rcd), control should be performed according to the characteristic line corresponding to the burner stage number one step higher (that is, the burner stage number should not be reduced to the limit). done.

As described above, in the present embodiment, burner combustion control is performed by controlling the number of stages of the burner and controlling the amount of opening of the gas proportional valve 18 so as to prevent the hot water supply burner device 2 from hunting and to increase the thermal efficiency as much as possible. However, depending on the heat distribution ratio in the two-kind pipe installation portion 112 in which the heating liquid distribution pipe 12 and the hot water supply liquid distribution pipe 13 are in contact with each other in the vertical direction, The hunting phenomenon of the burner device 2 for hot water supply may occur only with burner combustion control.

In other words, in the two-kind pipe arrangement portion 112, the temperature of the heat medium in the liquid circulation pipe 12 for heating is equal to the temperature of the heat medium in the liquid circulation pipe 13 for hot water supply during simultaneous operation of hot water supply and room heating. If it is extremely low compared to , the proportion of the heat absorbed by the heating liquid distribution pipe 12 for the combustion heat amount of the heating burner device 5 increases, and the heat absorption amount decreases on the hot water supply liquid distribution pipe 13 side. As a result, the hot water supply capacity decreases. In other words, when the temperature of the heat medium in the heating liquid circulation pipeline 12 is extremely lower than the temperature of the heat medium in the hot water supply liquid circulation pipeline 13, the heating liquid circulation pipeline 12 The amount of heat absorbed increases, and the amount of heat absorbed on the side of the liquid distribution pipe 13 for hot water supply decreases, so the hot water supply capacity decreases.

Thus, the ratio of heat absorption by the liquid distribution pipe 12 for heating and the ratio of heat absorption by the liquid distribution pipe 13 for hot water supply (distribution ratio) are determined by the temperature difference between the two. In the configuration of the composite heat exchanger 1 applied to the embodiment, this is particularly noticeable because the ratio of the liquid circulation pipes 12 of the heat exchanger for heating is large in the two-kind pipe installation portion 112 .

For example, as shown by characteristic lines a to d in FIG. and the hot water supply scale indicating the hot water supply capacity. In this embodiment, the combustion control means 52 performs combustion control (combustion of the burner devices 2, 5) corresponding to such a characteristic line. control, which controls the amount of opening of the gas proportional valve 18 and the opening/closing control of the gas on-off valve 17).

In FIG. 10 and FIG. 11, which will be described later, the characteristic lines a to d all show the characteristic lines when the temperature on the exit side from the liquid distribution pipe 13 for supplying hot water is 60.degree. Further, regarding the temperature on the heating side, the characteristic line a indicates the case where the temperature (heat medium temperature detected by the heating high-temperature thermistor 40) coming out of the liquid distribution pipe 12 for heating is 60°C. Characteristic line b indicates a case where the temperature of the heat medium is 55° C., characteristic line c indicates a case of 50° C., and characteristic line d indicates a case of 45° C., respectively.

Further, the opening degree of the gas proportional valve 18 and the rotational speed of the combustion fan 15 are, for example, substantially proportional, and the minimum hot water supply number is No. 2.5. Characteristic lines below No. 2.5 are imaginary lines (although they do not actually exist, extension lines of characteristic lines b to d in the first row are indicated by thin lines).

In this embodiment, combustion control of the burner device 2 (2a, 2b, 2c) for hot water supply and the burner device 5 for heating is made to correspond to characteristic lines for control such as characteristic lines a to d in FIG. However, between the third and fourth burner stages and between the second and third burner stages, hunting occurs on any of the characteristic lines a to d. A wrap margin for prevention is formed.

That is, the characteristic line d is the lowest among the characteristic lines a to d when the temperature of the heat medium on the outlet side of the liquid distribution pipe 12 for heating is 45° C., but is between the second and third burner stages. Since a lap allowance for preventing hunting is formed at , when the control is performed at the second stage of the burner stage number according to the characteristic line d, the required hot water supply number increases, and the gas proportional valve 18 When the degree of opening (gas pressure at this degree of opening) reaches end A in the figure, the burner is controlled to move to A' at the third stage of the burner stage, and conversely, the required hot water supply number becomes smaller. When the opening degree of the gas proportional valve 18 reaches the B end at the third burner stage, it is controlled to move to B' at the second burner stage.

In this way, between the second and third burner stages on the characteristic line d, a hunting prevention wrap allowance is provided between AB' and A'-B (that is, the burner stage number 3 A region where the hot water supply capacity overlaps between the second stage and the second stage is provided, and hunting is prevented. A hysteresis that would occur when the line falls to the eye cannot be formed, and a region in which the second stage and the first stage of the characteristic line d overlap is not formed. Therefore, since hunting of the hot water supply burner device 2a cannot be prevented in this state, the movement between the first and second burner stages is repeated.

This relationship is shown by the relationship between the number of burners and the hot water supply capacity (hot water supply number). In FIG. is shown by the characteristic lines Sa' to Sd' in the case of . As can be seen from the characteristic line Sa' and the characteristic line Sb', when only the heating burner device 5 is burned (characteristic line Sa'), and when the hot water supply burner device 2a is used in addition to the heating burner device 5, When burned (characteristic line Sb'), there is a difference in the hot water supply capacity, and there is no overlap portion (lap allowance) between the characteristic line Sa' and the characteristic line Sb' like the portion within the dashed line A frame, and the hot water supply There is concern about the occurrence of hunting in the burner device 2a.

On the other hand, in this embodiment, the hunting of the burner device 2 for hot water supply is prevented by the following configuration in which the hot water supply side temperature variable means 51 for branching is provided. That is, in the present embodiment, the branching hot water supply side temperature variable means 51 burns only the heating burner device 5 during simultaneous heating and hot water supply operation in which the heating operation and the hot water supply operation are performed at the same time. When heating the portion 112, by opening the reheating liquid flow rate control valve 32 without operating the reheating circulation pump 27, the liquid is heated in the heating liquid circulation line 12 forming the main heating heat exchanger. It functions as heat medium circulation path control means for circulating the heat medium through the liquid-water heat exchanger 33 for hot water supply and heating thermal connection.

With this function, the heat of the heat medium heated in the heating liquid distribution pipe 12 can be applied to the hot water supply circuit 45 side through the hot water supply heating thermal connection liquid-water heat exchanger 33. The hot water supply capacity can be improved when only the burner device 5 is burned. That is, with the above configuration, the amount of heat directly heated by the hot water supply heat exchanger from the heating burner device 5 and the heat medium heated by the heating burner device 5 in the main heating heat exchanger The amount of heat applied (indirectly heated) to the hot water supply circuit 45 side is added to increase the heating capacity of the hot water supply side, and hunting of the hot water supply burner device 2 can be suppressed.

This point will be described with reference to FIG. 10. In the two-kind pipe installation section 112, during simultaneous operation of hot water supply and heating, the temperature of the heat medium in the heating liquid distribution pipe 12 is higher than that of the hot water supply liquid distribution. When the temperature of the heat medium in the pipeline 13 changes from a high state to a low state, that is, when the heat consumption in the heating devices 70 and 71 increases, for example, the characteristic line a changes from the state of the characteristic line a. In the state of d, the proportion of heat absorbed by the heating liquid distribution pipe 12 in the amount of combustion heat of the heating burner device 5 increases. As a result, the amount of heat absorbed to the liquid distribution pipe 13 side for supplying hot water is reduced, so that the ability to supply hot water is reduced.

Therefore, the combustion control means 52 controls the opening amount of the gas proportional valve 18 so as not to cause the drop in the hot water supply capacity, but there are cases where the drop in the hot water supply capacity cannot be prevented. For example, when the hot water supply number is No. 3 during simultaneous operation, the valve opening amount of the gas proportional valve 18 is, for example, 12%, but when the amount of heat consumed by the heating devices 70 and 71 increases and becomes the state of the characteristic line b (the state where the temperature of the liquid flowing through the heating liquid circulation line 12 is 55° C.), the gas proportional valve The valve opening amount of 18 is, for example, 39%.

When the amount of heat consumed by the heating devices 70 and 71 further increases and the state of the characteristic line c (the state where the temperature of the liquid flowing through the heating liquid flow line 12 is 50° C.) is reached, the valve opening amount of the gas proportional valve 18 is For example, it is 66%, but when the amount of heat consumption in the heating devices 70 and 71 further increases and the state of the characteristic line d (the temperature of the liquid flowing out of the heating liquid distribution pipe 12 is 50° C.), the gas proportionality The opening amount of the valve 18 exceeds the upper limit of 90%, for example, and the amount of heat supplied cannot be increased sufficiently, resulting in a drop in hot water supply capacity.

Therefore, if the amount of heat consumed by the heating devices 70 and 71 is reduced, the drop in hot water supply capacity can be prevented. As a method of reducing heat consumption in the heating devices 70 and 71, for example, there is a method of opening the liquid flow control valve 32 for reheating. By doing this, the heat medium flows into the branch passage (pipe line) 65 branched from the pipe line 60, and the total amount of heat sent to the heating device 70 (flow rate is reduced) is reduced. consumption can be reduced. As a result, the return temperature from the heating device 70 is lower than before the reheating liquid flow control valve 32 is opened. On the other hand, the temperature of the heat medium coming out of the liquid-water heat exchanger 33 for hot water supply/heating thermal connection is also low (when only the heating device 71 is in operation, only this heat medium is generated).

As a result, the heat medium passing through the heating liquid distribution pipe 12 absorbs a large amount of the combustion heat of the heating burner device, but the temperature of the system drops, so the heat medium is sent to the heating device 70 and the heating device 71. As the temperature of the heat medium drops, the amount of heat consumed (the amount of heat released) in the heating devices 70 and 71 can be reduced, and a drop in the hot water supply capacity can be prevented. Opening the reheating liquid flow rate control valve 32 while the bathtub hot water circulation pump 27 is stopped has the effect of reducing the amount of heat consumed by the heating devices 70 and 71, and the above-mentioned hot water supply and heating thermal connection liquid- The hot water supply capacity can be increased by the double effect of absorbing and recovering the heat on the heating circuit 7 side in the water heat exchanger 33 to the hot water supply side.

For example, characteristic line Sa' and characteristic line Sb' in FIG. is 45° C., the branch corresponding hot water supply side temperature variable means 51 transfers the heat medium through the heating liquid distribution pipe 12 forming the main heating heat exchanger to the hot water supply heating thermal connection liquid-water heat An example of the relationship between the number of combustion burners and the number of hot water supply grades in the first and second stages of the burner stage is shown when the hot water is circulated through the exchanger 33 (characteristic lines Sc' and Sd' are also An example of the relationship between the number of combustion burners and the number of hot water supply when the temperature on the outlet side of the liquid distribution pipe 13 for heating is 60° C. and the temperature of the heat medium on the outlet side of the liquid distribution pipe 12 for heating is 45° C. ). As is clear from the comparison of the characteristic lines Sa' and Sb', the first burner stage (combustion only in the heating burner device 5) and the second burner stage (burner device 5 for heating and the burner device for hot water supply) 2a) can be formed, and the problem of hunting of the hot water supply burner device 2 (2a) can be prevented.

By the way, the amount of heat (output) supplied to the hot water supply side during simultaneous operation in which the heating operation and the hot water supply operation are performed at the same time is directly absorbed by the liquid distribution pipe 13 for hot water supply in the two-kind pipe installation part 112. Heat and in the two-kind pipe installation portion 112, once the heat is absorbed by the liquid distribution pipe 12 for heating, it is transferred to the hot water supply side via the hot water supply heating thermal connection liquid-water heat exchanger 33. It is the sum of the heat received and the heat recovered by the hot water supply heat exchanger 4 for recovering latent heat as needed. In this embodiment, the hot water supply heat exchanger 4 for latent heat recovery is provided to form the heat source device, but the hot water supply heat exchanger 4 for latent heat recovery may not be provided.

Then, in the two-kind pipe arrangement portion 112, once the liquid distribution pipe 12 for heating absorbs heat, heat is transmitted to the hot water supply side via the hot water supply heating thermal connection liquid-water heat exchanger 33 ( The heat (the latter) obtained by directly absorbing the heat in the hot water supply liquid distribution pipe 13 in the two-kind pipe installation portion 112 is more efficient than the former). Therefore, in the heat source device 1, even if the amount of heat (output) supplied to the hot water supply circuit 45 side is the same, it is better to increase the ratio of the latter and decrease the ratio of the former. The amount of heat (input) supplied to the heat source device 1 via the devices 2 and 5 can be reduced (the heat utilization efficiency of the energy supplied through the gas pipe 16 can be improved).

Therefore, in this embodiment, in consideration of the thermal efficiency of the heat source device, the heat is transferred to the hot water supply side via the hot water supply/heating thermal connection liquid-water heat exchanger 33 to obtain a lap allowance for the hot water supply capacity control. The reheating liquid flow rate control valve is used so that the wrap allowance can be appropriately formed by the heat transmitted to the hot water supply side through the hot water supply and heating thermal connection liquid-water heat exchanger 33, not the main control. The degree of opening of 32 is moderated so that the lap margin is moderately formed. That is, if the opening of the reheating liquid flow control valve 32 is large, the amount of heat transmitted to the hot water supply side via the hot water supply heating thermal connection liquid-water heat exchanger 33 becomes large, and the lap charge of the hot water supply capacity control is reduced. Although it can be large, the degree of opening of the reheating liquid flow rate control valve 32 is set to an appropriate (just right) degree of opening in consideration of the thermal efficiency of the heat source device.

FIG. 11 shows an example of a burner combustion control program different from that of this embodiment. In some cases, there may not be an area with the same hot water supply number between the first stage and the first stage. In this case, as in the present embodiment, only the burner combustion control by the combustion control means 52 results in hunting of the hot water supply burner device 2a. 51 functions as the heat medium circulation path control means to circulate the heat medium heated through the heating liquid circulation pipe 12 through the hot water supply and heating thermal connection liquid-water heat exchanger 33. , a similar effect can be obtained.

In addition, when hot water supply and heating are simultaneously operated, the hot water supply temperature is preferentially controlled, and the heating return temperature (heat medium temperature detected by the heating low temperature thermistor 41) is monitored to perform burner combustion control. (because the temperature on the heating side does not control the temperature, and the temperature is the same), it is not certain what degree the heating return temperature (heat medium temperature detected by the heating low temperature thermistor 41) will be. The detected temperature of the high temperature thermistor 40 is also uncertain. Therefore, in FIGS. 10 and 11, four characteristic lines a to d are shown as control characteristic lines. There is an infinite relationship between the degree of opening and the hot water supply number indicating the hot water supply capacity, and it always changes according to the heating return temperature, and control may be performed in accordance with this relationship.

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. Further, the branching hot water supply side temperature variable means 51 operates the reheating circulation pump 27 when reheating the hot water in the bathtub, and opens the reheating liquid flow control valve 32 to open the reheating liquid flow control valve after reheating is completed. 32 is also controlled.

The branch-compatible hot water supply side temperature variable means 51 passes the liquid that has passed through the main heating heat exchanger to the branch passage 65 side without operating the reheating circulation pump 27 when increasing the temperature of the water flowing through the hot water supply circuit 45 side. The reheating liquid flow rate control valve 32 is controlled so as to increase the liquid flow rate. On the other hand, when it is not necessary to increase 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 11 is not passed to the branch passage 65 side, or reheating is performed so as to reduce the heat medium flow rate. 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, for example, adjustment of the opening amount of the reheating liquid flow control valve 32 for increasing the temperature of the water flowing through the hot water supply circuit 45 side, etc. It controls the opening and closing of the heating liquid flow rate control valve 32 and the valve opening amount.

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 Calculated by the formula

Then, the branching hot water supply side temperature varying means 51 adjusts {(heat amount obtained by the heating circuit from the heating burner device 5) - (estimated by the heat exchange capacity estimating means). The opening amount of the reheating liquid flow rate control valve 32 is controlled so as to maintain the heat exchange capacity) ≥ 3,500 (Kcal/h). Here, (amount of heat obtained by the heating circuit from the burner device 5 for heating) = (amount of heat generated by combustion of the burner device 5 for heating) - (radiation loss) - (circulation of liquid for hot water supply from the burner device 5 for heating is the amount of heat directly absorbed by the pipeline 12).

Although the setting reference value is not particularly limited, in the present embodiment, the value is determined so that the bathroom heater connected to the heating circuit can perform the heating operation. In other words, by adjusting the branching hot water supply side temperature variable means 51, the amount of heat left in the heating circuit out of the amount of heat obtained from the burner device 5 for heating = "heating capacity" should not fall below 3,500 (Kcal/h). As a result, a large amount of the capacity of the heating side is supplied to the hot water supply side, so that the amount of heat supplied to the bathroom heater is not sufficiently performed on the heating circuit side, and cold air is blown from the bathroom heater. Since the heater will stop, the setting reference value is set as described above.

In addition, if the hot water supply capacity cannot be sufficiently increased by adjusting the branching hot water supply side temperature variable means 51 described above and the hot water temperature is expected to drop, the assumed hot water supply liquid distribution pipe line Calculated based on the temperature on the output side from 13 (estimated hot water temperature after the drop that will be detected by the heat exchange output side thermistor 23), the incoming water temperature, and the set hot water supply temperature set in the remote control device 53. Based on the bypass ratio of the bypass servo 21 calculated and the controllable bypass ratio of the bypass servo 21, when the bypass ratio of the bypass servo 21 calculated is within the controllable bypass ratio range, the set reference value After leaving heat in the heating circuit, the bypass ratio of the bypass servo 21 is adjusted.

If the calculated bypass ratio of the bypass servo 21 is not a controllable bypass ratio, the water volume servo 20 adjusts the flow rate until the calculated bypass ratio of the bypass servo 21 becomes a controllable bypass ratio (flow rate is reduced), the bypass ratio may be adjusted after the amount of heat is left in the heating circuit based on the set reference value.

In addition, when the hot water in the bathtub is reheated when the heat medium (hot water) of the heating circuit 7 is flowed to the branch passage 65 side, 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.

When the hot water supply capacity is replenished and the opening of the gas proportional valve 18 is less than the upper limit of 90%, the rotation speed of the reheating circulation pump 27 is lowered to operate the bath tub 75 in a limited manner. heat quantity to the hot water), and even if heat quantity is given to the hot water in the bathtub 75, the heat quantity given from the heating circuit 7 side to the hot water supply circuit 45 side via the hot water supply heating thermal connection liquid-water heat exchanger 33 can be maintained. As the reheating liquid flow rate control valve 32 is increased and the temperature of the heat medium passing through the heating liquid distribution pipe is lowered, the proportional gas valve 18 is opened and the bathtub 75 is opened. You may make it replenish the part which gave heat quantity to hot water.

FIG. 8 shows a diagram of a partial area including parts different from those of the first embodiment in the system configuration of the second embodiment of the heat source device according to the present invention. The second embodiment has substantially the same structure as the first embodiment. 1 is different from that shown in FIG.

In the example shown in FIG. 8, in the hot water supply and heating thermal connection liquid-water heat exchanger 33, by driving the circulation pump 9 for heating, 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 7 side can be transferred to the hot water supply circuit 45 side (the hot water supply side can absorb the heat on the heating side). .

FIG. 9 shows the system configuration of a heat source device according to a third embodiment of the present invention, and the third embodiment will be described below. In the description of the third embodiment, the same reference numerals are given to the parts with the same names as those of the first and second embodiments, and redundant description thereof will be omitted or simplified.

In the third embodiment, as shown in FIG. 9, the hot water supply system 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 and second embodiments A liquid-water heat exchanger 33 for heating thermal connection is provided on the outlet side of the hot water supply liquid circulation pipe 13 (main hot water supply heat exchanger) forming the composite heat exchanger 1 .

Further, in the third embodiment, as in the second embodiment, the liquid-water heat exchanger 33 for hot water supply and heating thermal connection is formed by opposed heat exchangers. That is, in the third 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 distribution 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 is introduced from the hot water supply heat exchanger 4 for latent heat recovery into the hot water supply and heating thermal connection liquid-water heat exchanger 33. The water flowing in 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 water and the heat medium from the liquid distribution pipe 12 flow in opposite directions to each other. It consists of an opposed heat exchanger.

The third embodiment can also achieve substantially the same effects as those of the first and second embodiments.

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, the heat source device of the present invention is configured as shown in FIGS. It is possible to omit the latent heat recovery heat exchanger provided in each of the above embodiments.

In addition, 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 detecting means for detecting the incoming water temperature of the hot water supply. good too.

Furthermore, the liquid-water heat exchanger 33 for hot water supply and heating thermal connection is not necessarily provided in the branch passage 65, and the heat medium heated through the main heating heat exchanger and the main hot water supply heat are not necessarily provided in the branch passage 65. It may be provided in such a manner as to thermally connect the heat medium passing through either the inlet-side passage or the outlet-side passage of the exchanger.

Furthermore, in each of the above-described embodiments, the branching hot water supply side temperature variable means 51 burns only the heating burner device 5 during simultaneous heating and hot water supply operation in which the heating operation and the hot water supply operation are performed at the same time. When the installation portion 112 is heated, by opening the reheating liquid flow control valve 32, the heat medium heated in the heating liquid distribution pipe 12 forming the main heating heat exchanger is used for hot water supply and heating. Although the liquid is circulated through the connecting liquid-water heat exchanger 33, the following control may be performed.

In other words, the branching hot water supply side temperature varying means 51 burns only the heating burner device 5 and heats the two-kind pipe installation portion 112 during the simultaneous heating and hot water supply operation in which the heating operation and the hot water supply operation are performed at the same time. and when it is determined that hunting of the hot water supply burner device 2 occurs due to the low temperature of the heat medium in the heating liquid circulation line 12, the reheating liquid flow rate control valve 32 By opening, the heat medium heated in the heating liquid circulation line 12 forming the main heating heat exchanger is circulated through the hot water supply heating thermal connection liquid-water heat exchanger 33. may

Further, for example, the heat distribution ratio in the two-kind pipe installation portion 112 may be forcibly changed by changing the rotation speed of the heating circulation pump 9 (reducing the rotation speed). That is, when the flow rate of the heating liquid distribution pipe line 12 of the second type pipe line installation portion 112 decreases, the temperature of the heat medium rises to a large extent, making it difficult for the heat medium to absorb heat. Instead, the hot water supply liquid distribution pipe 13 absorbs a large amount of heat, and the heat distribution ratio changes. Therefore, such control may be performed.

For example, in the fourth row of FIG. 10, the characteristic lines a to d are less affected by the heating temperature (each characteristic line is dense), but the first row is more affected by the heating temperature (each characteristic line is rough). Since the heat absorption in the hot water supply circuit 45 is absorbed in the second-class pipeline installation part 112 in all stages in the first stage, the heat absorption in the first-stage pipeline installation part 111 increases in the second stage and later. , the effect of heat absorption in the heating liquid distribution pipe 12 is relatively small. Therefore, by reducing the rotational speed of the heating circulation pump 9, the amount of heat absorbed by the heating liquid distribution pipe 12 in the second type pipe installation portion 112 is reduced, and the influence on the amount of heat absorbed on the hot water supply side is reduced. Each characteristic line of the tier changes from coarse to dense, the dashed frame D in FIG. 10 can be eliminated, and a lap allowance for hunting prevention is formed.

Further, for example, as shown by the dashed lines in FIGS. 3 and 9, a bypass electromagnetic provided in a bypass pipe 120 that bypasses between a pipe 60 as a passage on the going side and a pipe 61 as a passage on the return side. By opening the valve 121 to reduce the amount of heat medium sent to the heating device 70, the amount of heat consumed by the heating device 70 may be reduced, and the wrap allowance for hunting prevention may be formed. Furthermore, by closing the low-temperature capacity switching valve (thermal valve) 118 that is opened when the heating device 71 is in operation and lowering the temperature of the heat medium sent to the low-temperature heating device 71, the amount of heat consumed by the heating device 71 is may be reduced to form a lap allowance for hunting prevention.

Furthermore, in the case of the configuration having a plurality of hot water supply burner devices 2 as in each of the above embodiments, if, for example, the temperature of the heat medium in the liquid circulation pipe 12 for heating decreases, the hot water supply burner In the burner stage variable program for switching the stage number of the device 2, if there is no region where the hot water supply capacity (hot water supply scale) is the same in the vertically adjacent stage numbers, the hot water supply capacity is changed in the vertically adjacent stage numbers. The heat medium circulation path control means circulates the heat medium heated through the main heating heat exchanger through the hot water supply heating thermal connection liquid-water heat exchanger 33 so that the same area is formed. By transmitting the heat of the heat medium circulating in the heating circuit 7 to the hot water supply circuit 45 side, the occurrence of hunting when the hot water supply capacity is switched can be suppressed.

Furthermore, the heat source device of the present invention may have other functions such as a heat collecting function for collecting solar heat, and a configuration such as a hot water storage tank.

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.

Furthermore, in each of the above embodiments, the temperature of the liquid flowing out of the hot water supply pipe 13 is set at 60° C., but this temperature is not limited to a fixed value of 60° C., for example, and may be variable according to the set temperature of the hot water supply. I don't mind.

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.

1 heat source device 2, 2a, 2b, 2c burner device for hot water supply 4 heat exchanger for hot water supply for latent heat recovery 5 burner device for heating 6 heat exchanger for latent heat recovery for heating 7 heating circuit 8 liquid circulation passage for heating 9 Heating circulation pump 14, 17 Gas solenoid valve 15 Combustion fan 18 Gas proportional valve 24 Hot water supply thermistor 25 Bath heat exchanger 32 Liquid flow control valve for reheating 33 Liquid-water heat exchanger for hot water supply and 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 54 Control means 55 Pump drive control means 111 First-class pipeline installation section 112 Second-class pipeline installation section

Claims (7)

A hot water supply heat exchanger, a hot water supply circuit having a function of heating water as a 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 liquid heat medium through the heating heat exchanger a heating circuit comprising a heating circulation pump that circulates the 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. The hot water heat exchanger has a main hot water heat exchanger for recovering sensible heat of the combustion gas of the burner device by a liquid flow conduit forming the hot water heat exchanger, and the heating heat exchanger A hot water supply liquid forming the main hot water supply heat exchanger, having a main heating heat exchanger for recovering sensible heat of the combustion gas of the burner device through a liquid flow conduit forming the heating heat exchanger. A first-class pipeline installation portion in which only a circulation pipeline is arranged, and a liquid circulation pipeline of the main hot water supply heat exchanger are vertically sandwiched by the liquid circulation pipeline of the main heating heat exchanger. The hot water supply heat exchanger and the heating heat exchanger form a composite heat exchanger, and the lower portion of the composite heat exchanger has a two-kind pipe arrangement portion arranged in contact with each other. A burner device for hot water supply and a burner device for heating are separately arranged on the side. A gas on-off valve for supplying and shutting off the fuel gas to the burner device corresponding to each of the hot water supply burner device and the heating burner device. is provided, and a gas proportional valve that uniformly varies the gas supply ratio to both burner devices is provided. Combustion burner determination control for controlling whether to burn only the heating burner device or to burn the hot water supply burner device in addition to the heating burner device, and the combustion burner determined by the combustion burner determination control. In combustion, corresponding to the required hot water supply capacity, the opening of the gas proportional valve is increased as the required hot water supply capacity increases, and the opening of the gas proportional valve is decreased as the required hot water supply capacity decreases. combustion control means for performing temperature control according to a predetermined burner combustion control program; Thermally connecting the passage with the heat transfer medium passing through one of the exit passages A liquid-water heat exchanger for hot water supply and heating thermal connection is provided, and when the heating and hot water supply are simultaneously operated, only the heating burner device is burned to heat the two-kind pipe installation portion. A heat source apparatus comprising heat medium circulation path control means for circulating a heat medium for circulating a heating circuit through the liquid-water heat exchanger for hot water supply and heating thermal connection. The heat medium circulation path control means controls the heat medium for circulating in the heating circuit when heating only the heating burner device during the simultaneous operation of heating and hot water supply to heat the two-kind pipe installation portion. When, instead of circulating through a heating thermal connection liquid-water heat exchanger, only the heating burner device is burned during the simultaneous operation of the heating and hot water supply to heat the two-kind pipe installation part When it is determined that hunting of the hot water supply burner device occurs due to the low temperature of the heat medium, the heat medium circulating in the heating circuit is circulated through the liquid-water heat exchanger for hot water supply/heating thermal connection. 2. The heat source device according to claim 1, wherein the heat source device is configured to The heat medium circulation path control means controls the hot water supply/heating thermal connection liquid-water heat exchange so that the amount of heat exchanged by the hot water supply/heating thermal connection liquid/water heat exchanger becomes a predetermined set heat exchange amount. 3. The heat source device according to claim 1, wherein the flow rate of the heat medium passing through the vessel is controlled. On the outlet side of the main heat exchanger for heating, an outgoing passage is formed for circulating the liquid that has passed through the main heat exchanger for heating toward the heating device. to the main heating heat exchanger side is formed, and the tip end of the branched passage branched from the going-side passage is connected to the return-side passage, and the hot water supply is connected to the branched passage 4. The heat source device according to claim 1, 2 or 3, further comprising a liquid-water heat exchanger for heating thermal connection. The hot water supply burner device includes a plurality of burner devices, and is provided with gas on-off valves for supplying and shutting off the fuel gas to the burner device corresponding to the plurality of burner devices and the heating burner device, respectively. , a gas proportional valve for uniformly varying the ratio of gas supply to all the burner devices is provided, and the number of burner stages, which is the number of combustion burners among the plurality of hot water supply burner devices, is set in correspondence with the required hot water supply capacity. is increased according to a predetermined burner stage number variable program as the required hot water supply capacity increases, and the burner stage number is decreased as the required hot water supply capacity decreases, and the required hot water supply is made to correspond to the required hot water supply capacity. combustion control means for performing proportional valve opening control for increasing the opening of the gas proportional valve as the capacity increases and decreasing the opening of the gas proportional valve as the required hot water supply capacity decreases; The control means burns only the heating burner device when the requested hot water supply capacity is less than a predetermined set capacity during simultaneous operation in which the heating operation and the hot water supply operation are performed simultaneously, and when the required hot water supply capacity exceeds the set capacity, the heating burner device. 5. The heat source apparatus according to any one of claims 1 to 4, wherein the hot water supply burner device burns in accordance with the burner stage number variable program in addition to the combustion of . If there is no region in which the hot water supply capacity is the same in the burner stage number variable program, the heat medium circulation path control means circulates the heat medium in the heating circuit so that the same area is formed. 6. The heat source device according to claim 5, wherein the heat medium is circulated through a liquid-water heat exchanger for hot water supply and heating thermal connection, and the heat of the heat medium circulating in the heating circuit is transmitted to the hot water supply circuit side. A latent heat recovery heat exchanger for recovering latent heat of combustion gas of the burner device is connected to at least one of the main hot water supply heat exchanger and the main heating heat exchanger. The heat source device according to any one of claims 1 to 6.

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