JP2011002194A - One-can type composite heat source machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent, in a one-can type composite heat source machine including: a first burner 2and a second burner 2smaller than the first burner, which are provided in parallel in a single can body 1; a first heat exchanger 3and a second heat exchanger 3smaller than the first heat exchanger, which are provided in parallel at an upper part of the can body; and a partition wall 8 dividing the interior of the can body into two combustion chambers 7, 7, wherein the partition wall is formed in a hollow structure having two wall plates 8a and air is let flow in an internal space of the partition wall from an air supply chamber 5 at a lower part of the can body, an air amount supplied to the second heat exchanger from becoming excessive due to blockade of the first heat exchanger and causing defective combustion of the second burner.SOLUTION: A temperature sensor 10 is arranged between the two wall plates 8a of the partition wall 8. A blocking rate of the first heat exchanger 3is estimated based on detected temperature of the temperature sensor 10 in single combustion by the first burner 2alone. In single combustion by the second burner 2alone, rotation speed of a combustion fan 6 is corrected for decrease according to an increase of the blocking rate of the first heat exchanger 3.

Description

  The present invention includes a single can body, a first and second pair of burners provided side by side in the can body, and a first and second pair provided side by side on the top of the can body. The present invention relates to a single can type combined heat source apparatus including a heat exchanger.

  Conventionally, in this type of single can type combined heat source machine, the space between the first and second burners and the first and second heat exchangers in the can is transferred from the first burner to the first heat exchange. A partition wall that divides into a first combustion chamber leading to the furnace and a second combustion chamber leading from the second burner to the second heat exchanger, and burns only one of the burners, for example, the second burner to perform the second heat exchange At the time of single combustion for heating the heat exchanger, it is possible to prevent a problem that the combustion gas of the second burner flows to the first heat exchanger side and the first heat exchanger is heated. Further, an air supply chamber partitioned by a distribution plate is defined at the lower part of the can body, and the first and second combustion air from a single combustion fan is distributed through the distribution holes formed in the distribution plate from the air supply chamber. The fuel is supplied to both the second combustion chambers.

  Here, when the partition wall is provided in the can as described above, the partition wall is heated to a very high temperature by the combustion heat of each of the first and second burners, so ensuring the heat resistance of the partition wall is a problem. Become. Therefore, the partition wall is configured as a hollow structure having two wall plates on the first combustion chamber side and the second combustion chamber side so that the air from the air supply chamber flows in the gap between both wall plates. Is also known (see, for example, Patent Document 1). According to this, the partition wall is cooled by the air from the air supply chamber, and the heat resistance of the partition wall is ensured.

  By the way, when the first burner and the first heat exchanger are for hot water supply, for example, and the second burner and the second heat exchanger are for bath reheating and for heating, from the difference in required heating capacity, The second heat exchanger is formed smaller than the first burner and the first heat exchanger, respectively. In this case, the supply ratio of air to the first combustion chamber is larger than the supply ratio of air to the second combustion chamber. Then, when soot and scale accumulate on the fins of the first heat exchanger, the blockage rate of the first heat exchanger increases, and the amount of air supplied to the first combustion chamber decreases, the supply air to the second combustion chamber The amount is greatly increased, and the second burner has excessive air, resulting in poor combustion. However, conventionally, even if the blockage rate of the first heat exchanger increases, this cannot be detected, and the combustion failure of the second burner cannot be prevented.

JP 2006-78162 A

  In view of the above points, the present invention provides a single can type combined heat source device that detects the blockage rate of a large first heat exchanger and prevents the combustion failure of the second burner. It is said.

  The present invention includes a single can body, a first burner arranged side by side in the can body, a second burner smaller than the first burner, and a first heat provided side by side on the top of the can body. A space between the first heat exchanger and the second heat exchanger smaller than the first heat exchanger, the first and second burners, and the first and second heat exchangers in the can. A partition wall partitioning into a first combustion chamber extending from the first heat exchanger to the first heat exchanger and a second combustion chamber extending from the second burner to the second heat exchanger, and partitioned by a distribution plate at a lower portion of the can body. One can that defines a supply chamber and supplies combustion air from a single combustion fan to both the first and second combustion chambers from the supply chamber through distribution holes formed in the distribution plate The partition wall is configured to have a hollow structure having two wall plates on the first combustion chamber side and the second combustion chamber side, and a space between the two wall plates extends from the air supply chamber. In those flowing air, characterized in that it has improved as follows in order to solve the above problems.

  That is, according to the present invention, a temperature sensor is disposed between both wall plates of the partition wall, and the blockage rate of the first heat exchanger is estimated based on the temperature detected by the temperature sensor during single combustion of only the first burner. 1 estimating means, and fan correcting means for reducing and correcting the rotational speed of the combustion fan in accordance with an increase in the blockage rate of the first heat exchanger estimated by the first estimating means during single combustion of only the second burner. It is characterized by that.

  Here, when one of the first heat exchanger and the second heat exchanger becomes obstructed, it is drawn by the air flow or the exhaust flow that flows through the other heat exchanger, Combustion gas in one combustion chamber corresponding to the exchanger flows toward the partition wall side. Therefore, if a temperature sensor is arranged between two wall plates constituting the partition wall as in the present invention, the temperature detected by the temperature sensor rises as the blockage rate of one heat exchanger increases. In addition, at the time of simultaneous combustion of the first burner and the second burner, even if the temperature detected by the temperature sensor rises, it is impossible to determine which of the first heat exchanger and the second heat exchanger has become blocked. However, at the time of single combustion of only the first burner, the blockage rate of the first heat exchanger can be estimated based on the temperature detected by the temperature sensor. In the present invention, during the single combustion of only the second burner, the rotational speed of the combustion fan is corrected to decrease according to the increase in the blocking rate of the first heat exchanger. Even if the ratio of the air flowing into the chamber increases, the air is not excessively supplied to the second combustion chamber, and the combustion failure of the second burner can be prevented.

  In the present invention, the second correction means for estimating the blockage rate of the second heat exchanger based on the temperature detected by the temperature sensor during the single combustion of only the second burner is provided. At the time of single combustion of only the burner, the rotational speed of the combustion fan is corrected to decrease according to the increase in the blockage rate of the first heat exchanger, and the increase in the blockage rate of the second heat exchanger estimated by the second estimation means It is desirable to be configured to compensate for increase accordingly. According to this, the decrease in the amount of air supplied to the second combustion chamber due to the blockage of the second heat exchanger can be compensated by the increase in the rotational speed of the combustion fan, and the combustion state of the second burner can be maintained well.

  Further, in the present invention, the fan control means corrects the rotation speed of the combustion fan according to the increase in the blockage rate of the first heat exchanger estimated by the first estimation means when the first burner alone is burned alone. At the same time, it is desirable that the correction is made so as to decrease in accordance with the increase in the blockage rate of the second heat exchanger estimated by the second estimation means. According to this, even if the blockage of the first heat exchanger or the blockage of the second heat exchanger occurs, the combustion state of the first burner can be maintained well.

  In the embodiment to be described later, STEP 8 in FIG. 3 corresponds to the first estimation means, and STEP 2 in FIG. 3 corresponds to the second estimation means, which corresponds to the fan control means. Are STEP 5 to 7 and STEP 11 to 13 in FIG.

The cutting front view showing the 1 can type compound heat source machine of the embodiment of the present invention. FIG. 2 is a cut side view taken along line II-II in FIG. 1. The flowchart which shows the content of the fan correction | amendment control performed with the 1 can type compound heat source machine of embodiment. (A) The graph which shows the relationship between the blockage rate of a 1st heat exchanger, and the detection temperature of a temperature sensor, (b) The graph which shows the relationship between the blockage rate of a 2nd heat exchanger, and the detection temperature of a temperature sensor. (A) The graph which shows the relationship between the obstruction | occlusion rate of a 1st heat exchanger, and a fan correction coefficient, (b) The graph which shows the relationship between the obstruction | occlusion rate of a 2nd heat exchanger, and a fan correction coefficient.

FIG. 1 shows a single can type combined heat source machine having a hot water supply function and a bath reheating function. With the composite heat source machine, and a second burner 2 ₂ for the first burner 2 ₁ and bath hot water supply provided side by side in the lateral direction in a single can body 1, transverse to the top of the can body 1 Tile and a second heat exchanger 3 ₂ for the first heat exchanger 3 ₁ the bath hot water supply provided in the.

In the lower part of the can body 1, an air supply chamber 5 partitioned by a distribution plate 4 with respect to the space in the can body 1 is defined. A single combustion fan 6 driven by a fan motor 6 a is connected to the supply chamber 5. Then, air from the combustion fan 6 enters the first and second combustion chambers 7 ₁ and 7 _{2, which} will be described later, in the can 1 through a number of distribution holes 4 a formed in the distribution plate 4 from the air supply chamber 5. It is supplied as secondary air for combustion.

Each of the first and second burners 2 ₁ and 2 ₂ is configured by arranging a plurality of unit burners 2a that are long in the front-rear direction (in the direction orthogonal to the plane of FIG. 1) as the depth direction of the can body 1 in the horizontal direction. Has been. As shown in FIG. 2, each unit burner 2a includes a lower mixing tube portion 2b extending in the front-rear direction. And the front part of the distribution plate 4 is bent upward, the rising part 5a is formed in the front part of the air supply chamber 5, and the inflow end of each mixing pipe part 2b is made to face this rising part 5a. The front surface of the rising portion 5a of the air supply chamber 5 is closed by a gas manifold 2c, and a gas nozzle 2d facing the mixing tube portion 2b of each unit burner 2a is provided in the gas manifold 2c. The fuel gas is supplied from each gas nozzle 2d to the mixing pipe portion 2b of each unit burner 2a, and the primary combustion air is supplied to the mixing pipe portion 2b from the rising portion 5a.

Each of the first and second heat exchangers 3 ₁ , 3 ₂ includes a heat absorbing fin 3 a that is stacked in a large number in the front-rear direction, and a meandering heat absorbing tube 3 b that passes through the heat absorbing fin 3 a. The Although not shown, an upstream water supply pipe and a downstream hot water outlet pipe are connected to the heat absorption pipe 3b of the first heat exchanger 31, and a _first hot water tap is opened at the downstream end of the hot water outlet pipe. when passed through the exchanger 3 _1, is ignited first burner 2 _1, the hot water set temperature from hot water tap is tapped. The second heat absorbing tube 3b of the heat exchanger 3 _2, although not shown, bathtub via the return forward pipe line is connected, via a water through the second heat exchanger 3 ₂ in the bathtub when circulating Te and ignited in the second burner 2 _2, bath reheating is carried out.

Since the direction of reheating bath than hot water supply less demand heating capacity, the second burner 2 ₂ smaller than a second heat exchanger 3 ₂ are each first burner 2 ₁ and the first heat exchanger 3 ₁ It has become.

Further, in the can 1, a space between the first and _second burners 2 ₁ and 2 ₂ and the first and second heat exchangers 3 ₁ and 3 ₂ is provided as a first burner 2 _1. and a first combustion chamber ₇₁ leading to the first heat exchanger 3 _1, and the partition wall 8 is provided for partitioning the second burner 2 ₂ second combustion chamber 7 ₂ reaching the second heat exchanger 3 ₂ Yes. Therefore, the first combustion gas of the burner 2 ₁ is led to the first heat exchanger 3 ₁ through the first combustion chamber _71, the combustion gas of the second burner 2 ₂ through the second combustion chamber 7 _Paragraph 2 is guided to the heat exchanger _{3 2.} Combustion gas heat exchange with the first and second of each heat exchanger 3 _1, 3 _2, flows to a common exhaust hood 9 positioned above the two heat exchangers 3 _1, 3 _2, formed in the exhaust hood 9 From the exhaust port 9a.

Partition wall 8 is constructed in a hollow structure having first combustion chamber ₇₁ side and the second combustion chamber 7 ₂ side of the two wall panels 8a, the 8a. The lateral width of the gap between the wall plates 8a, 8a is widened at the lower part of the partition wall 8, and the gap is communicated with the air supply chamber 5 through the communication hole 4b formed in the distribution plate 4. Therefore, the air from the air supply chamber 5 flows into the space between the wall plates 8a and 8a, and the partition wall 8 is cooled by this air, so that the heat resistance of the partition wall 8 is ensured.

Incidentally, that soot or scale is deposited on the first heat exchanger 3 ₁ and the second heat absorbing fins 3a of the heat exchanger 3 _2, resulting in obstruction of the first heat exchanger 3 ₁ and the second heat exchanger 3 ₂ is there. The normal because the larger feed rate of air to the first combustion chamber 7 ₁ than the feed rate of air to the second combustion chamber 7 _2, the first combustion at the first closing of the heat exchanger 3 ₁ When the supply amount of air to the chamber ₇₁ is reduced, not only produce the first burner 3 ₁ of incomplete combustion due to insufficient air, the supply air amount to the second combustion chamber 7 ₂ greatly increases, the second burner 2 ₂ occurs poor combustion with air excess. When the second heat exchanger 3 ₂ is closed, the second supply air amount to the combustion chamber 7 ₂ decreases, ₂ second burner 2 is generated poor combustion with insufficient air.

Here, the first heat exchanger 3 ₁ and the second heat exchanger 3 ₂ and one heat exchanger is closed slightly, while the two heat exchangers 3 _1, 3 ₂ common exhaust hood 9 above The combustion gas in one combustion chamber corresponding to one heat exchanger is biased toward the partition wall 8 by being drawn by the exhaust flow flowing through the heat exchanger. Even if the burner corresponding to the other heat exchanger is not burned, the combustion gas in one combustion chamber is drawn by the air flow flowing from the air supply chamber 5 to the exhaust hood 9 via the other heat exchanger. Flows unevenly toward the partition wall 8 side. Therefore, the temperature of the partition wall 8 rises.

Therefore, in this embodiment, both wallboard 8a of the partition wall 8, a temperature sensor 10 between 8a arranged, the first heat exchanger 3 ₁ and the second heat exchanger on the basis of the detected temperature T of the temperature sensor 10 32 The blockage rate of ₂ can be detected.

  The temperature sensor 10 has a pipe-like shape having a temperature sensing part 10a incorporating a temperature sensing element such as a thermistor at the tip. The temperature sensor 10 is inserted into the partition wall 8 from the front side of the can 1 as shown in FIG. Is inserted. And the fixed part 10b of the tail end side of the temperature sensor 10 is being fixed to the front surface of the can 1 in the state which located the temperature sensitive part 10a in the center part of the partition wall 8 in the front-back direction.

Incidentally, both wallboard 8a of the temperature sensor 10 is a partition wall 8, when in contact with the 8a, when one alone causes only a burned burner combustion of the first burner 2 ₁ and the second burner 2 _2, the burner Even if the temperature of one combustion chamber side wall plate 8a becomes high due to the blockage of one of the corresponding heat exchangers, the temperature sensor 10 from this wall plate 8a to the other combustion chamber side wall plate 8a passes through the temperature sensor 10. As a result, the detection temperature rise of the temperature sensor 10 is suppressed and the detection accuracy of the blockage rate of the heat exchanger is deteriorated. Therefore, in the present embodiment, the both wall plates 8a and 8a are formed with the bulging portion 8b bulging outward in the lateral direction so as to be positioned at the insertion portion of the temperature sensor 10, and the temperature sensor 10 is formed on the both wall plates 8a. , 8a.

A detection signal of the temperature sensor 10 is input to a controller 11 that controls both the first and second burners 2 ₁ and 2 ₂ and the combustion fan 6. Here, the detection temperature T of the temperature sensor 10, in response to the first heat exchanger 3 ₁ the closure rate CL1 changes as shown in FIG. 4 (a), according to the second closing rate CL2 of the heat exchanger 3 ₂ Changes as shown in FIG. Therefore, the controller 11 estimates the detected temperature first heat exchanger on the basis of T 3 ₁ and the second heat exchanger 3 _{and second} occlusion rate CL1, CL2 of the temperature sensor 10, the combustion fan 6 in accordance with the estimation result The fan correction control is executed to correct the rotation speed. Hereinafter, the fan correction control will be described with reference to FIG.

Fans correction control, first, a bath islanding operation of the operating state of the multifunction heat source device in STEP1 burning only the second burner 2 _2, the single hot water supply run and first to burn only the first burner 2 ₁ second both burners It is discriminated whether the hot water supply or the bath is operated at the same time to burn 2 ₁ and 2 ₂ simultaneously.

During bath islanding operation, in STEP2, estimates the detected temperature T the second heat exchanger _{3 and second} closure rate CL2 based on the temperature sensor 10, also at the time of single hot water supply run, in STEP 8, the detection temperature T of the temperature sensor 10 based estimating a first heat exchanger _{3 1} the closure rate CL1. This estimation is performed by retrieving the blocking rates CL1 and CL2 corresponding to the detected temperature T from the data table as shown in FIG. 4A or 4B stored in the controller 11. Incidentally, either at the time of simultaneous operation of the water heater and bath, even if the detected temperature T of the temperature sensor 10 is increased, resulting in any clogging of the heat exchanger and the first heat exchanger 3 ₁ and the second heat exchanger 3 ₂ Indistinguishable. Therefore, the blockage rate of the heat exchanger is not estimated based on the temperature T detected by the temperature sensor 10 during simultaneous operation.

If during bath isolated operation for estimating a second heat exchanger _{3 and second} occlusion rate CL2 in STEP2, the process proceeds to STEP3, exceeds a predetermined judgment value the blockage rate CL2 is the upper limit of the combustible range YCL2 (e.g., 90%) It is determined whether or not. If CL2> YCL2, stops the second burner _{2 2} combustion proceeds in STEP4, an error message is displayed.

Proceeds to STEP5 If CL2 ≦ YCL2, searches the data table shown in FIG. 5 (b), determining the enhancement factor I2 corresponding to the second closing rate CL2 of the heat exchanger _{3 2.} Next, proceeding to STEP 6, the data table shown in FIG. 5A is searched, and a decrease correction coefficient D 2 corresponding to the blockage rate CL ₁ of the first heat exchanger 31 estimated in STEP 8 during the previous hot water supply independent operation is obtained. Ask. The maximum time increase correction factor I2 is gradually increased from with 1.0 to increase the second heat exchanger _{3 and second} occlusion rate CL2, occlusion rate CL2 becomes the determination value YCL2 (e.g., 1.05) become. Further, reduction correction coefficient D2, the minimum when it is judged value YCL1 gradually decreases from with 1.0 to increase the first heat exchanger _{3 1} the closure rate CL1, occlusion rate CL1 will be described later (for example, 0. 95).

Thereafter, the process proceeds to STEP7, calculates the rotational speed NF by multiplying the increase correction coefficient I2 in reference rotational speed YNF2 defined a decrease correction coefficient D2 in response to the second combustion amount of burners 2 _2, with the rotation speed NF The combustion fan 6 is rotated. According to this, the rotational speed NF combustion fan 6, with decreasing corrected in accordance with the increase in the first heat exchanger 3 ₁ the closure rate CL1, according to the increase of the second heat exchanger 3 _{and second} occlusion rate CL2 Increase correction. Therefore, the combustion air excess or deficiency in supply without can maintain second combustion state of the burner 2 ₂ satisfactorily in the second combustion chamber 7 _2.

When estimating the occlusion rate CL1 of single hot water supply run first heat exchanger in STEP8 at _{3 1,} the process proceeds to STEP 9, exceeds a predetermined judgment value the blockage rate CL1 is the upper limit of the combustible range YCL1 (e.g., 90%) It is determined whether or not. If CL1> YCL1, stops the first combustion burner _{2 2} proceeds to STEP 10, an error message is displayed.

Proceeds to STEP11 if CL1 ≦ YCL1, searches the data table shown in FIG. 5 (a), obtaining the increase correction factor I1 corresponding to the first heat exchanger _{3 1} the closure rate CL1. Then, the process proceeds to STEP 12, and searches the data table shown in FIG. 5 (b), a decrease correction coefficient D1 corresponding to the second closing rate CL2 of the heat exchanger _{3 2} estimated in STEP2 in the preceding bath islanding Ask. The maximum time increase correction factor I1 is gradually increased from with 1.0 to increase the first heat exchanger _{3 1} the closure rate CL1, occlusion rate CL1 becomes the determination value YCL1 (e.g., 1.05) become. Further, reduction correction coefficient D1 is gradually decreased from with 1.0 to increase the second heat exchanger _{3 and second} occlusion rate CL2, minimum when the closure rate CL2 becomes the determination value YCL2 (e.g., 0.98) become.

Thereafter, the process proceeds to STEP 13, and calculates the rotation speed NF by multiplying the increase correction coefficient I1 to the reference rotational speed YNF1 defined a decrease correction coefficient D1 in response to the first burner _{2 first} combustion amount in the rotational speed NF The combustion fan 6 is rotated. According to this, the rotational speed NF combustion fan 6, with increasing corrected in accordance with the increase in the first heat exchanger 3 ₁ the closure rate CL1, according to the increase of the second heat exchanger 3 _{and second} occlusion rate CL2 Decrease correction. Therefore, the combustion air excess or deficiency in supply without can maintain a first combustion state of the burner 2 ₁ satisfactorily in the first combustion chamber 7 _1.

During simultaneous operation of the water heater and bath, in STEP 14, it is determined whether or not the second closing rate CL2 of the heat exchanger _{3 2} estimated in STEP2 in the preceding bath isolated operation exceeds the determination value YCL2, also, in STEP15 , whether exceeds a predetermined preliminary determination value first heat exchanger _{3 1} the closure rate CL1 estimated in STEP8 in the previous single hot water supply run is set smaller than the determination value YCL1 YCL1a (e.g., 70%) Is determined. Then, CL2> when a YCL2 a is when and CL1> YCL1a, an error display stops the second burner _{2 2} combustion proceeds to STEP 16. Next, the first heat exchanger _{3 1} the closure rate CL1 is determined whether or not exceeds the determination value YCL1 in STEP 17, CL1> if YCL1, stops the first burner _{2 2} combustion proceeds to STEP18 And error display.

Incidentally, at the time of simultaneous operation, so that the hot water temperature is maintained at the set temperature, in relation to control with priority hot-water supply side, the rotational speed NF of the combustion fan 6 to an increase in the first heat exchanger 3 ₁ the closure rate CL1 Accordingly, it is not possible to correct the decrease. Therefore, CL1> becomes a YCL1a, the combustion state of the second burner _{2 2} with air excess is degraded. Therefore, CL1> when a YCL1a is stopped combustion of the second burners _{2 2.}

When it is determined that CL1 ≦ YCL1 In STEP17, together determine the enhancement factor I1 corresponding to the first closing rate CL1 of the heat exchanger _{3 1} STEP 19, the second heat exchanger _{3 and second} occlusion rate CL2 in STEP20 A corresponding decrease correction coefficient D1 is obtained. Then, the process proceeds to STEP 21, and calculates the rotation speed NF by multiplying the increase correction coefficient I1 to the reference rotational speed YNF1 defined a decrease correction coefficient D1 in response to the first burner _{3 first} combustion amount in the rotational speed NF The combustion fan 6 is rotated.

If the fan rotational speed NF is excessively corrected to increase or decrease, the detected temperature T of the temperature sensor 10 changes due to a change in the amount of air supplied to the internal space of the partition wall 8, and the first and second heats. The blocking rates CL1 and CL2 of the exchangers 3 ₁ and 3 ₂ cannot be accurately estimated. Therefore, the fan rotational speed NF is corrected to increase or decrease within a range of, for example, ± 5% of the specified rotational speeds YNF1 and YNF2.

Further, the detected temperature T of the temperature sensor 10 is also changed by the combustion amount of the first burner 2 ₁ and the second burner 2 _2. Therefore, when the combustion amount of the first burner 2 ₁ and the second burner 2 ₂ each predetermined amount, closure of the detected temperature T first heat exchanger based on the 3 ₁ and the second heat exchanger 3 _{and second} temperature sensor 10 The rates CL1 and CL2 are estimated. Incidentally, the first burner _{2 1} and the second burner _{2 2} of the first heat exchanger while gradually changing the combustion amount unit _{3 1} and second heat exchanger ₃ and _second occlusion rate CL1, CL2 between the detected temperature T examine the relationship stores data tables for each combustion amount to the controller 11, first burner 2 ₁ and the first heat exchanger 3 ₁ and the second heat from the data table corresponding to the second combustion amount of burners 2 ₂ it is also possible to estimate the occlusion rate CL1, CL2 of the exchanger _{3 2.}

As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to this. For example, in the above embodiment, the fan rotation speed NF at the time or simultaneous operation hot water supply operation, increasing the correction coefficient I1 corresponding to the occlusion rate CL1 reference rotation number YNF1 to the first heat exchanger 3 _1, the second heat exchanger vessel 3 is calculated by multiplying the _second closure rate CL2 reduction correction coefficient D1 in accordance with it, even if the clogging of the second heat exchanger 3 _2, amount of air supplied to the first combustion chamber 7 ₁ Does not increase so much. Therefore, the fan rotation speed NF during hot water supply operation or simultaneous operation may be calculated by multiplying the reference rotation speed YNF1 by only the increase correction coefficient I1.

Further, the above-described embodiment, the first burner 2 ₁ and the first heat exchanger 3 ₁ for hot water, the second burner 2 ₂ and 1 can type composite heat source machine and the second heat exchanger 3 ₂ and a bath While the invention is obtained by applying the second burner 2 ₂ and the second heat exchanger 3 ₂ other than bath applications, for example, and for heating, and further, the first burner 2 ₁ and the first heat exchanger 3 ₁ even one can type composite heat source machine according to those other than the hot water supply application, and the second burner 2 ₂ and the second heat exchanger 3 ₂ respectively first than the burner 2 ₁ and the first heat exchanger 3 ₁ The present invention can be similarly applied as long as it is small.

DESCRIPTION OF SYMBOLS 1 ... Can body, 2 ₁ ... 1st burner, 2 ₂ ... 2nd burner, 3 ₁ ... 1st heat exchanger, 3 ₂ ... 2nd heat exchanger, 4 ... Distribution board, 4a ... Distribution hole, 5 ... Supply Air chamber, 6 ... combustion fan, 7 ₁ ... first combustion chamber, 7 ₂ ... second combustion chamber, 8 ... partition wall, 8a ... wall plate, 10 ... temperature sensor, 11 ... controller.

Claims (3)

A single can body, a first burner arranged side by side in the can body and a second burner smaller than the first burner, a first heat exchanger arranged side by side on the top of the can body and the first The space between the first heat exchanger and the second heat exchanger, which is smaller than the first heat exchanger, and the first and second burners in the can and the first and second heat exchangers, is transferred from the first burner to the first heat A partition wall partitioning into a first combustion chamber leading to the exchanger and a second combustion chamber leading from the second burner to the second heat exchanger, and an air supply chamber partitioned by a distribution plate at a lower portion of the can body A single-can type combined heat source that is configured to supply combustion air from a single combustion fan to both the first and second combustion chambers through distribution holes formed in the distribution plate from the supply chamber. The partition wall has a hollow structure having two wall plates on the first combustion chamber side and the second combustion chamber side, and allows air from the air supply chamber to flow into the space between both wall plates. In things,
A temperature sensor is arranged between both wall plates of the partition wall,
First estimating means for estimating a blocking rate of the first heat exchanger based on a temperature detected by a temperature sensor during single combustion of only the first burner;
Fan correction means for reducing and correcting the rotational speed of the combustion fan in accordance with an increase in the blockage rate of the first heat exchanger estimated by the first estimation means during single combustion of only the second burner. 1 can type combined heat source machine.   Based on the temperature detected by the temperature sensor during single combustion of the second burner alone, the second heat exchanger is provided with second estimating means for estimating the blockage rate of the second heat exchanger, and the fan correction means includes only the second burner. During the single combustion, the rotational speed of the combustion fan is corrected to decrease according to the increase in the blockage rate of the first heat exchanger, and according to the increase in the blockage rate of the second heat exchanger estimated by the second estimation means. The single-can type combined heat source apparatus according to claim 1, wherein the one-can type combined heat source apparatus is configured to compensate for the increase.   3. The single can type combined heat source apparatus according to claim 2, wherein the fan control means estimates the rotation speed of the combustion fan by the first estimation means when the first burner alone is burned alone. It is configured to perform an increase correction according to an increase in the blockage rate of the heat exchanger and to perform a decrease correction according to an increase in the blockage rate of the second heat exchanger estimated by the second estimation means. One can type combined heat source machine.

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