JP4759672B1 - Heating system - Google Patents

Abstract

【Task】
Provided is a heating device that has high heating capacity, has little heat loss, and is suitable for whole building heating.
[Solution]
The heating device includes a fan coil 30 having a fan and a heat exchanger, a suction device 50, a blowing device 60, and ducts 71 and 72 in the underfloor space. The heat medium warmed by the boiler 39 warms the circulating air, warms the space under the floor, warms the entire floor, and warms the living space. The blow-out device 60 that blows warm air into the underfloor space includes a blow-out housing in which the distance between the upper surface and the lower surface gradually decreases toward the air outlet, and the distance between both side surfaces gradually increases toward the air outlet. The blow-out device 60 blows hot air into a flow path region formed between the floor and the partition member 81, and the guides 85, 85A, and 85B arranged on the partition member 81 smoothly disperse the hot air. With this structure, the hot air blown out from the blowing device 60 generates turbulent flow in a wide area immediately below the floor, greatly increasing the heating capacity and greatly reducing heat loss.
[Selection] FIG.

Description

The present invention relates to a heating device that heats a room by warming a floor.

In recent years, floor heating, which heats a floor by heating, has been widely used because the room temperature is almost uniform and there is no warm air in the room to provide a comfortable living space. Floor heating with hot water pipes and heating wires embedded in the floor is widespread, but the equipment costs are expensive. An underfloor heating apparatus that warms the underfloor with warm air has been proposed as an inexpensive floor heating apparatus for a house that does not have a ventilator under the floor like an externally insulated house or has a ventilator closed in winter.

In the solar-heated heating system described in Patent Document 1, the heat medium heated by the solar heat collector is sent to the fan coil unit, and the heat of the heat medium is released into the underfloor space by the fan coil unit. This released heat is prevented from leaking underground or outdoors by the heat insulating material provided on the foundation, and as sensible heat to the underfloor space and the side plates, foundations, joists and flooring of the foundation facing this underfloor space. Heat is stored. This sensible heat is radiated into the room from the upper surface of the flooring.
In the warm air floor heating device described in Patent Document 2, a hot air passage box is attached in close contact with the back surface of the floor board at the upper part inside the underfloor space to form a double space. A hot air circulation passage that snakes with a partition plate is formed, a heat insulating material is provided on the inner bottom surface of this hot air circulation passage, and a hot air generator that circulates hot water and dissipates heat in the middle of the hot air circulation passage. It is installed.

JP 2001-132986 A JP 2007-127372 A

The solar-powered heating system described in Patent Document 1 has a structure in which warm air generated by the fan coil unit warms the flooring and the heated flooring heats the room. Since it is directly discharged into the underfloor space, the area where the warm air is in direct contact with the floor is relatively small. Therefore, the heating capacity of the solar heating heating system is relatively low.

Next, the reason why the heating capacity of the solar thermal heating system is relatively low will be described in detail. FIG. 18 schematically shows a plan view under the floor of the conventional heating device 160 and the building 10 and the flow of air directly under the floor. FIG. 19 schematically shows a cross section taken along the line AA in FIG. 18 and the flow of warm air in the cross section. In addition, the heating apparatus 160 is a structure which discharge | releases the warm air 41C from the fan coil unit 30 directly to the underfloor space 21 similarly to a solar-heated heating system.
The building 10 in which the heating device 160 is arranged has a structure in which a side wall 12 including a pillar and a wall is constructed on a base portion 11 and a floor 17 is supported by the side wall 12. The underfloor space 21 is a space surrounded by the floor 17, the base portion 11, and the four side walls 12. The foundation 11 is the bottom surface of the underfloor space 21 and is constructed of concrete, ground or the like. The floor 17 is composed of a floor board 16, a joist 15 and a large pull 14. The floor 17 may be composed of only the floor board 16 depending on the structure of the building, the size of the room, or the like, or may be composed of the floor board 16 and the joists 15.
In the case of a building having a direct air passage with outside air such as a ventilation opening in the underfloor space 21, it is preferable to close the ventilation opening in order to reduce heat loss. However, the underfloor space 21 does not need to be a sealed space, and the underfloor space 21 and the living space 22 may be connected by a gap between the floorboard 16 and a gap between the floorboard 16 and the water supply pipe.

The heating device 160 includes a boiler 39 that is a heat source for heating, the fan coil unit 30 disposed in the underfloor space 21, and a heat medium circulation path 38 for circulating a heat medium between the boiler 39 and the fan coil unit 30. And a pump 37 that circulates the heat medium in the heat medium circulation path 38.
The fan coil unit 30 blows air through a fan coil housing 31 that forms an air passage 36 that guides air sucked from the fan coil suction port 34 to the fan coil air outlet 35, and a heat exchanger 33 that is disposed in the air passage 36. It is comprised with the air blower 32 to do. The heat exchanger 33 has a flow path through which the heat medium flows, and performs heat exchange between the air flowing through the air passage 36 and the heat medium flowing through the flow path. The heat medium circulation path 38 is connected to a flow path through which the heat medium of the heat exchanger 33 flows. With this configuration, the heat of the boiler 39 is transferred to the heat exchanger 33 by the heat medium, transmitted to the air flowing through the air passage 36 by the heat exchanger 33, sent to the underfloor space 21 by the blower 32, and warms the floor 17. The warmed floor 17 warms the living space 22.

The heating device 160 includes a heating control unit (not shown) that controls the boiler 39, the pump 37, and the blower 32. The heating control unit controls the operation of the boiler 39 and the pump 37 based on a signal generated from a heating switch or the like. When the boiler 39 and the pump 37 are operated, the temperature of the heat medium circulating in the heat medium circulation path 38 increases. The heating control unit has a room temperature lower than a predetermined heating set temperature, and a detection temperature of a heat medium temperature detector (not shown) that detects the temperature of the heat medium near the heat exchanger 33 is higher than a predetermined heat medium setting temperature. If so, the blower 32 is operated. When the blower 32 is operated, the air in the underfloor space 21 is sucked from the fan coil suction port 34, the air is warmed by the heat exchanger 33, and returned to the underfloor space 21 from the fan coil blowout port 35. The heat released by the heat exchanger 33 due to the air circulation warms the air in the underfloor space 21 and the floor 17. The warmed floor 17 warms the living space 22.

Next, the flow of the warm air 41C in the underfloor space 21 and the heat transfer between the floor 17 and the warm air 41C will be described. The hot air 41 </ b> C is a flow of warm air that is generated by the blower 32 and the heat exchanger 33 and circulates through the air passage 36 and the underfloor space 21. It is assumed that the hot air 41 </ b> C has a sufficiently high speed when being blown from the fan coil air outlet 35 and generates turbulent flow in the vicinity of the fan coil inlet 34 and the fan coil air outlet 35. The warm air 41C is composed of a laminar flow 42C and a turbulent flow 43C in the underfloor space 21. The warm air 41C disturbs the temperature distribution in the steady state of the air in the underfloor space 21 (the state in which the temperature of the upper air is higher than the temperature of the lower air), so that natural convection 44C is generated, and the natural convection 44C Heat is transferred to the floor 17. The turbulent flow 43C immediately below the floor 17 greatly increases the heat transfer coefficient between the warm air 41C and the floor 17. The larger the area of the turbulent flow 43C immediately below the floor 17, the greater the amount of heat transfer between the warm air 41C and the floor 17. Although the area where the natural convection 44C comes into contact with the floor is large, the heat transfer coefficient of the natural convection 44C is extremely small, so that the amount of heat transferred from the warm air 41C to the floor via the natural convection 44C is small.

FIG. 18 schematically shows the flow of air immediately below the floor 17 with arrows. Since the air flow is small in the region very close to the floor 17 due to the viscosity of the air, there is a laminar viscous bottom layer. FIG. 18 shows the air flow in a region where turbulent flow exists below the viscous bottom layer. The turbulent flow area 23C is a turbulent flow area generated by the hot air 41C sucked into the fan coil suction port 34, and the turbulent flow area 24C is a turbulent flow area generated by the hot air 41C blown from the fan coil air outlet 35. It is. Laminar flow and natural convection exist in regions other than the turbulent flow regions 23C and 24C, and heat transfer between the hot air 41C and the floor 17 is performed by the laminar flow 42C and natural convection 44C. The laminar flow 42C is mainly a flow due to a gradient of atmospheric pressure, and its velocity rapidly decreases as the distance from the turbulent flow regions 23C and 24C increases. On the other hand, the natural convection 44C is a flow due to the disturbance of the temperature distribution in the steady state, and its velocity gradually decreases as the distance from the turbulent regions 23C and 24C increases.
In the vicinity of the turbulent flow regions 23C and 24C, the speed of the laminar flow 42C is much higher than the speed of the natural convection 44C, so that the heat transfer coefficient by the laminar flow 42C between the hot air 41C and the floor 17 is as follows. Much higher than the heat transfer coefficient due to natural convection 44C between On the other hand, in a place sufficiently away from the turbulent flow areas 23C and 24C, the speed of the laminar flow 42C is smaller than the speed of the natural convection 44C, so the heat transfer coefficient by the laminar flow 42C between the hot air 41C and the floor 17 is It is smaller than the heat transfer coefficient by the natural convection 44C between the hot air 41C and the floor 17.
The laminar flow region 25C is a region in which the heat transfer coefficient by the laminar flow 42C between the hot air 41C and the floor 17 is larger than the heat transfer coefficient by the natural convection 44C between the hot air 41C and the floor 17, and the natural convection region 26C is a region in which the heat transfer coefficient by the natural convection 44C between the hot air 41C and the floor 17 is larger than the heat transfer coefficient by the laminar flow 42C between the hot air 41C and the floor 17.
The average heat transfer coefficient between the hot air 41C and the floor 17 in the turbulent flow regions 23C and 24C is much larger than the average heat transfer coefficient between the hot air 41C and the floor 17 in the laminar flow region 25C. The laminar flow region 25C exists around the turbulent flow region 23C or 24C, and the natural convection region 26C exists outside the laminar flow region 25C. Note that the natural convection 44C exists also in the turbulent flow regions 23C and 24C.

The larger the speed of the hot air 41C at the time of blowing from the fan coil outlet 35, the larger the turbulent flow areas 23C and 24C and the laminar flow area 25C, and the smaller the natural convection area 26C. The shape of the turbulent flow areas 23C and 24C depends on conditions such as the size of the joist 15 and the large pull 14, the direction of the fan coil air outlet 35, the distance between the floor 17 and the fan coil air outlet 35, the temperature and the wind speed of the hot air 41C, etc. It will change greatly. Also, the shape of the laminar flow region 25C varies greatly depending on conditions.
Hereinafter, the shape of the turbulent flow region shown in the figure is a schematic for showing how the shape of the air outlet or the suction port relatively changes the area of the turbulent flow region without changing other conditions. It indicates the shape, not the specific shape.
In the laminar flow region 25C, due to the buoyancy of air, the warm air 41C cooled by the floor 17 descends, the warm hot air 41C rises, cools by the floor 17 and descends. Further, since a force acts in the direction of the fan coil suction port 34 where the atmospheric pressure is low with respect to the air, the direction is gradually changed in the direction of the fan coil suction port 34. That is, in the laminar flow region 25 </ b> C, the hot air 41 </ b> C flows while gradually changing in the direction of the fan coil suction port 34 while being raised or lowered, or repeatedly raised and lowered, and is sucked into the fan coil suction port 34. It is.

FIG. 20 is a perspective view of the fan coil casing 31 of the fan coil unit 30. The blower 32 and the heat exchanger 33 are disposed inside the fan coil housing 31. The blower 32 may be composed of one or a plurality of blowers, and the heat exchanger 33 may be composed of one or a plurality of heat exchangers.
The fan coil unit 30 is a device that generates hot air or cold air, and is generally used for heating and cooling. The fan coil unit 30 preferably has a high heating capacity or cooling capacity, is small, and is inexpensive. If the ratio (W / H) of the width W to the height H of the fan coil outlet 35 is increased, the cost performance is lowered due to the necessity of a large number of blowers and the need for a special fan. The ratio of width to height is set relatively small. As a result, since the width W of the fan coil outlet 35 is set to be relatively small, the widths of the turbulent flow regions 23C and 24C are relatively small. The wind speed of the hot air 41C from the fan coil outlet 35 can be adjusted by the rotational speed of the blower 32, and the lengths of the turbulent flow areas 23C and 24C (the length in the direction in which the hot air 41C blows out) are the same as those of the hot air 41C. The greater the wind speed, the greater.
Accordingly, the width of the fan coil outlet 35 is relatively small, and the width of the turbulent flow regions 23C and 24C is relatively small, so that the areas of the turbulent flow regions 23C and 24C are relatively small.
Further, since the warm air 41C is blown directly from the fan coil outlet 35 (without going through the duct) into the underfloor space 21 and directly sucked from the fan coil suction port 34 (without going through the duct), The path of the warm air 41C is short, and the area of the laminar flow region 25C is relatively small.
Therefore, since the heating device 160 has relatively small areas of the turbulent flow regions 23C and 24C and the laminar flow region 25C, the amount of heat transferred from the warm air 41C to the floor 17 is relatively small. That is, the heating capacity of the heating device 160 is relatively low.

Therefore, since the structure of the solar-heated heating system described in Patent Document 1 is the same as the structure of the heating device 160, its heating capacity is relatively low. In addition, although the warm air 41C contacts the base part 11, since the heat insulating material 13 is laid on the base part 11, the heat loss of the heating apparatus 160 is small.

The hot air floor heating device described in Patent Document 2 has low heat loss and high heating capacity, but the hot air passage box has a passage that causes the hot air to meander, and therefore requires airtightness. Since a radiator and a blower are required for each passage box, it is expensive and is not suitable for heating the entire building.

The present invention has been made in view of the above-described problems, and provides a heating apparatus that has high heating capacity, low heat loss, and is suitable for whole building heating.

The heating device of the present invention includes a blowing device having an elongated rectangular outlet in the underfloor space, and blows warm air from the blowing device widely under the floor. The warm air creates a large area of turbulent flow under the floor. Since the heat transfer coefficient between the warm air and the floor is large in the turbulent region, the heating capacity of the heating device of the present invention is high. Furthermore, since the warm air is away from the base, there is little heat loss. Furthermore, since the warm air disturbs the steady-state temperature distribution of the air in the underfloor space, natural convection is generated, and natural convection transfers the heat of the warm air to the entire floor, so the heating device of the present invention is suitable for heating in the entire building. is there.

The heating device of the present invention includes a partition member arranged under the floor, and blows warm air from the outlet between the floor and the partition member. Since a partition member enlarges the area of a turbulent flow area | region, it raises the heating capability of the heating apparatus of this invention. Furthermore, since the warm air which flows into the base part under a partition member is suppressed, the heat loss to the base part of the heating apparatus of this invention is small.

The heating device of the present invention has a high heating capacity and a small heat loss, and is suitable for whole building heating.

The heating apparatus 100 which is 1st embodiment of the heating apparatus of this invention, the top view of the floor under the building 10, and the flow of the air just under a floor are shown typically. FIG. 1 schematically shows a cross section taken along line A-A in FIG. 1 and the flow of hot air in the cross section. The perspective view of the suction apparatus 50 and the blowing apparatus 60 is shown. The perspective view of blowing apparatus 60A is shown. The perspective view of suction device 50B and blowing device 60B is shown. The perspective view of the blowing apparatus 60C is shown. The top view under the floor of the heating apparatus 110 which is 2nd embodiment of the heating apparatus of this invention, and the building 10 is shown typically. The cross section of AA of FIG. 7 is shown typically. The top view under the floor of the heating apparatus 120 which is 3rd embodiment of the heating apparatus of this invention, and the building 10 is shown typically. The cross section of AA of FIG. 9 is shown typically. The perspective view of the partition members 82 and 83 is shown. The top view under the floor of the heating apparatus 130 which is 4th embodiment of the heating apparatus of this invention and the building 10 is shown typically. The cross section of AA of FIG. 12 is shown typically. The top view under the floor of the heating apparatus 140 which is 5th embodiment of the heating apparatus of this invention and the building 10 is shown typically. The cross section of AA of FIG. 14 is shown typically. The top view under the floor of the heating apparatus 150 which is 6th embodiment of the heating apparatus of this invention and the building 10 is shown typically. FIG. 17 schematically shows a cross section taken along line A-A in FIG. 16. The top view under the floor of the conventional heating apparatus 160 and the building 10, and the flow of the air just under a floor are shown typically. FIG. 18 schematically shows a cross section taken along line A-A in FIG. 18 and the flow of hot air in the cross section. The perspective view of the fan coil housing | casing 31 is shown. The top view under the floor of 100 A of heating apparatuses and the building 10 provided with the suction apparatus 50B and the blowing apparatus 60B is shown.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 schematically shows a plan view under the floor of a heating apparatus 100 and a building 10 according to a first embodiment of the heating apparatus of the present invention, and a flow of air directly under the floor. FIG. 2 schematically shows a cross section AA in FIG. 1 and the flow of warm air in the cross section.
The heating device 100 is arranged in the building 10 like the heating device 160. Similarly to the heating device 160, the heating device 100 generates a heat medium between the boiler 39 that is a heat source for heating, the fan coil unit 30 disposed in the underfloor space 21, and the boiler 39 and the fan coil unit 30. A heat medium circulation path 38 for circulation and a pump 37 for circulating the heat medium in the heat medium circulation path 38 are provided. Furthermore, the heating device 100 includes a suction device 50, a duct 71 that connects the suction device 50 and the fan coil suction port 34, a blower device 60, and a duct 72 that connects the blower device 60 and the fan coil blower outlet 35. . That is, the heating device 100 has a configuration in which the ducts 71 and 72, the suction device 50, and the blowing device 60 are added to the heating device 160.
Although the heating apparatus 100 is an example in which the boiler 39 is used as a heat source for heating the heat medium, the exhaust heat of the fuel cell may be used as a heat source for heating. Further, the heat medium may be warmed by the heat of the outside air using a heat pump. Further, the air in the air passage 36 may be directly warmed with an electric heater without using the heat exchanger 33.

FIG. 3 (A) shows a perspective view of the suction device 50, and FIG. 3 (B) shows a perspective view of a blowing device 60 which is an embodiment of the first blowing device of the present invention. The suction device 50 includes a suction housing 52 that forms an air passage for guiding air sucked from an elongated, substantially rectangular suction port 53 to the suction housing outlet 51, and parts (not shown) that are connected to the duct 71. The The upper surface of the suction housing 52 is substantially parallel to the floor 17, and the length of the long side substantially parallel to the floor 17 of the suction port 53 is larger than the length of the side substantially parallel to the floor 17 of the suction housing outlet 51. The length of the short side of the mouth 53 is smaller than the length of the side substantially orthogonal to the floor 17 of the suction housing outlet 51. The upper surface and the lower surface of the suction housing 52 are constituted by flat plates, and the distance between the upper surface and the lower surface of the suction housing 52 gradually decreases toward the suction port 53. Both side surfaces of the suction housing 52 are formed of flat plates, and the interval between the both side surfaces of the suction housing 52 gradually increases toward the suction port 53. The structure of the suction device 50 suppresses pressure loss between the suction port 53 and the suction housing outlet 51.
The blow-out device 60 is composed of a blow-out housing 62 that forms an air passage for guiding the air sucked from the blow-out housing inlet 61 to an elongated rectangular outlet 63, a part (not shown) for connecting to the duct 72, and the like. Is done. The upper surface of the blowout housing 62 is substantially parallel to the floor 17, and the length of the long side substantially parallel to the floor 17 of the blowout outlet 63 is larger than the length of the side substantially parallel to the floor 17 of the blowout housing inlet 61. The length of the short side of the outlet 63 is smaller than the length of the side substantially orthogonal to the floor 17 of the blowout housing inlet 61. The upper surface and the lower surface of the blowout housing 62 are constituted by flat plates, and the distance between the upper surface and the lower surface of the blowout housing 62 gradually decreases toward the blowout port 63. Both side surfaces of the blowout housing 62 are formed of flat plates, and the distance between both side surfaces of the blowout housing 62 gradually increases toward the blowout port 63. This structure of the blower device 60 suppresses pressure loss between the blower housing inlet 61 and the blower outlet 63.
The heat exchanger 33 corresponds to the heater of the present invention, the end of the duct 72 on the outlet device 60 side corresponds to the passage outlet of the present invention, and the suction housing 52, the duct 71, the fan coil housing 31, and the duct 72 are connected. What connected is equivalent to the channel | path formation body of this invention, and the blowing apparatus 60 is equivalent to the 1st blowing apparatus of this invention.

The heating apparatus 100 includes a boiler control unit (not shown) that controls the boiler 39 and the pump 37, and a room temperature control unit (not shown) that operates independently of the boiler control unit and controls the blower 32. The boiler control unit controls the operation of the boiler 39 and the pump 37 based on a signal generated from a heating switch or the like. When the boiler 39 and the pump 37 are operated, the temperature of the heat medium circulating in the heat medium circulation path 38 increases. The room temperature control unit is configured such that the room temperature is lower than a predetermined heating temperature, and the detection temperature of a heat medium temperature detector (not shown) that detects the temperature of the heat medium near the heat exchanger 33 is higher than the predetermined heat medium setting temperature. If so, the blower 32 is operated.
Generally, since a boiler control part is a part of boiler, it is difficult to change a boiler control part. Since the room temperature controller operates independently of the boiler controller, there is no need to change the boiler controller. That is, the heating device 100 can control the room temperature by using a commercially available boiler without changing it and adding a room temperature control unit.

The difference in the flow of the warm air 41 of the heating device 100 and the warm air 41C of the heating device 160 will be described with reference to FIGS. The heating device 100 has a configuration in which the suction device 50 and the fan coil unit 30 are connected by a duct 71, and the fan coil unit 30 and the blowing device 60 are connected by a duct 72. Here, the shapes and sizes of both ends of the ducts 71 and 72 are the same. That is, the shape and size of the suction housing outlet 51 and the fan coil suction port 34 are the same, and the shape and size of the fan coil air outlet 35 and the blowing housing inlet 61 are the same.
Since the width of the air outlet 63 is larger than the width of the air outlet housing inlet 61, it is larger than the width of the fan coil air outlet 35. Therefore, the width of the turbulent flow region 24 generated by the hot air 41 blown from the outlet 63 is larger than the width of the turbulent flow region 24C. Moreover, since the height of the blower outlet 63 is smaller than the height of the blower housing inlet 61 and smaller than the height of the fan coil blower outlet 35, the blower outlet 63 can be arranged away from the base part 11 from the fan coil blower outlet 35. Furthermore, the height of the air outlet 63 can be made sufficiently small so that the area of the air outlet 63 can be made smaller than the area of the fan coil air outlet 35. In that case, the wind speed of the warm air 41 blown from the blower outlet 63 is larger than the wind speed of the warm air 41C blown from the fan coil blower outlet 35, and the length of the turbulent flow region 24 is larger than the length of the turbulent flow region 24C. it can.
Therefore, the turbulent flow is achieved by making the width of the outlet 63 larger than the width of the outlet casing inlet 61 and reducing the height of the outlet 63 so that the area of the outlet 63 is smaller than the area of the outlet casing inlet 61. The area of the region 24 can be made larger than the area of the turbulent region 24C.

Since the width of the suction port 53 is larger than the width of the suction housing outlet 51, it is larger than the width of the fan coil suction port 34. Therefore, the width of the turbulent flow region 23 generated by the hot air 41 sucked into the suction port 53 is larger than the width of the turbulent flow region 23C. Further, since the height of the suction port 53 is smaller than the height of the suction housing outlet 51 and smaller than the height of the fan coil suction port 34, the suction port 53 can be arranged away from the base portion 11 from the fan coil suction port 34. Further, the height of the suction port 53 can be made sufficiently small so that the area of the suction port 53 can be made smaller than the area of the fan coil suction port 34. In that case, the speed of the warm air 41 sucked into the suction port 53 is larger than the speed of the warm air 41C sucked into the fan coil suction port 34, and the length of the turbulent flow region 23 can be made larger than the length of the turbulent flow region 23C. .
Therefore, the turbulent flow is achieved by making the width of the suction port 53 larger than the width of the suction housing outlet 51 and reducing the height of the suction port 53 so that the area of the suction port 53 is smaller than the area of the suction housing outlet 51. The area of the region 23 can be made larger than the area of the turbulent region 23C.
Since the distance between the suction port 53 and the air outlet 63 is larger than the distance between the fan coil air inlet 34 and the fan coil air outlet 35, the area of the laminar flow region 25 is larger than the area of the laminar flow region 25C.
Therefore, the areas of the turbulent flow regions 23 and 24 and the laminar flow region 25 of the heating device 100 are larger than the areas of the turbulent flow regions 23C and 24C and the laminar flow region 25C of the heating device 160, respectively. Is higher than the heating capacity of the heating device 160.

FIG. 4 shows a perspective view of a blowing device 60 </ b> A having a structure in which a nozzle 65 is connected to a blowing port 63 of the blowing device 60. The nozzle 65 forms a passage that guides the air flowing from the nozzle inlet 64 to the nozzle outlet 66. The nozzle inlet 64 is connected to the outlet 63. The nozzle 65 includes a nozzle upper surface, a nozzle lower surface, and both nozzle side surfaces. The nozzle upper surface and the nozzle lower surface are substantially parallel to each other, and the distance between the nozzle side surfaces gradually increases toward the nozzle outlet 66.
The nozzle 65 has a nozzle upper surface and a nozzle lower surface that are substantially parallel to each other and is arranged in a direction in which the air flow is blown out. Therefore, the length of the turbulent flow region generated by the hot air blown from the nozzle blowout port 66 is increased. The width of the turbulent flow region generated by the hot air blown from the nozzle outlet 66 is slightly larger than the width of the turbulent flow region 24. That is, the area of the turbulent flow region generated by the warm air blown from the nozzle outlet 66 is larger than the area of the turbulent flow region 24. Therefore, the heating capacity of the heating device provided with the blowing device 60 </ b> A is higher than that of the heating device provided with the blowing device 60.

5A and 5B are perspective views of a suction device 50B and a blowing device 60B that is a first embodiment of the second blowing device provided in the heating device of the present invention. FIG. 21 shows a plan view of the heating device 100A including the suction device 50B and the blowing device 60B and the floor under the building 10. The configuration of the heating device 100A includes a suction device 50B instead of the suction device 50, a blower device 60B instead of the blower device 60, a duct 71A instead of the duct 71, and a duct 72A instead of the duct 72. The operation of the heating device 100 </ b> A is the same as the operation of the heating device 100.
The suction device 50B is composed of a suction housing 62B having a rectangular parallelepiped structure and parts (not shown) for connecting to a duct or the like, and is arranged so that the upper surface thereof is substantially parallel to the floor 17. The shape of the suction port 53B for sucking warm air from the underfloor space 21 is an elongated rectangular shape, and the shape of the suction housing inlet 51B connected to a substantially rectangular duct, fan coil or the like is substantially rectangular.
The blow-out device 60B includes a blow-out housing 62B having a rectangular parallelepiped structure and parts (not shown) for connecting to a duct or the like, and is arranged so that the upper surface thereof is substantially parallel to the floor 17. The shape of the air outlet 63B that blows warm air into the underfloor space 21 is an elongated, substantially rectangular shape, and the shape of the air outlet housing inlet 61B that is connected to a substantially rectangular duct, fan coil, or the like is substantially rectangular.
The length of the long side substantially parallel to the floor 17 of the outlet 63B is more than twice the length of the side substantially parallel to the floor 17 of the outlet casing inlet 61B, and the length of the short side of the outlet 63B is the outlet. It is one half or less of the length of the side substantially orthogonal to the floor 17 of the housing entrance 61B.
The end of the duct 72A on the blowing device 60B side corresponds to the passage outlet of the present invention, and the connection of the suction housing 52B, the duct 71A, the fan coil housing 31, and the duct 72A corresponds to the passage forming body of the present invention. The blowing device 60B corresponds to the second blowing device of the present invention.

Since the width of the turbulent flow area is approximately proportional to the width of the hot air, the width of the turbulent flow area 24D generated by the hot air blown from the blower outlet 63B is blown from the hot air blowout outlet having the same size as the blowout housing inlet 61B. It is approximately twice or more larger than the width of the turbulent region where the generated warm air is generated. Moreover, the area of the blower outlet 63B can be made smaller than the area of the blower casing inlet 61B, and the speed of the warm air at the blower outlet 63B can be made larger than the speed of the hot air at the blower casing inlet 61B. The length of the region 24D can be made larger than the length of the turbulent flow region generated by the hot air blown from the hot air blowout port having the same size as the blowout housing inlet 61B. That is, the blowing device 60B makes it possible to make the area of the turbulent flow region 24D larger than the area of the turbulent flow region generated by the hot air blown from the hot air blowing port having the same size as the blowing housing inlet 61B.
Therefore, the heating capability of the heating device provided with the blowing device 60B can be made larger than the heating capability of the heating device not provided with the blowing device 60B. Furthermore, since the blower outlet 63B can be separated from the base part 11 from the hot air outlet having the same size as the blower casing inlet 61B, heat loss can be reduced.

FIG. 6 shows a perspective view of a blowing device 60C that is a second embodiment of the second blowing device provided in the heating device of the present invention. The blowing device 60 </ b> C includes a blowing housing 62 </ b> C having a rectangular parallelepiped structure and parts (not shown) for connecting to a duct and the like, and is arranged so that the upper surface is substantially parallel to the floor 17. The heating device provided with the blow-out device 60C is the same as the heating device 100A except for the shape of the air passage, and a description thereof will be omitted.
The shape of the air outlet 63C that blows warm air into the underfloor space 21 is an elongated and substantially rectangular shape, and the shape of the air outlet housing inlet 61C that is connected to a substantially circular duct or the like is substantially circular. The length of the long side substantially parallel to the floor 17 of the outlet 63C is at least twice the diameter of the outlet casing inlet 61C, and the length of the short side of the outlet 63C is a third of the diameter of the outlet casing inlet 61C. Or less.

Since the width of the turbulent flow area is substantially proportional to the width of the hot air, the width of the turbulent flow area generated by the hot air blown from the outlet 63C is blown from the hot air outlet having the same size as the outlet casing inlet 61C. It is approximately twice or more larger than the width of the turbulent flow region generated by hot air. Further, the area of the outlet 63C can be made smaller than the area of the outlet casing inlet 61C, and the speed of the warm air at the outlet 63C can be made larger than the speed of the hot air at the outlet casing 61C. The length of the turbulent flow region generated by the hot air blown out from 63C may be made larger than the length of the turbulent flow region generated by the hot air blown out from the hot air blowout port having the same size as the blowing housing inlet 61C. Is possible. In other words, the blower device 60C has a turbulent flow area generated by the hot air blown from the hot air blowout outlet having the same size as the blowout housing inlet 61C in the area of the turbulent flow area generated by the hot air blown from the blowout outlet 63C. It is possible to make it larger than the area.
Therefore, the heating capability of the heating device provided with the blowing device 60C can be made larger than the heating capability of the heating device not provided with the blowing device 60C. Furthermore, since the air outlet 63C can be separated from the base portion 11 from the hot air outlet having the same size as the air outlet 61C, heat loss can be reduced.

FIG. 7 schematically shows a plan view of the heating apparatus 110 according to the second embodiment of the present invention and the floor under the building 10. FIG. 8 schematically shows a cross section taken along line AA of FIG.
The heating device 110 is obtained by adding a partition member 81 to the heating device 100. The partition member 81 is a flat plate, and is arranged below the air outlet 63 so as to form an air flow path between the partition 17 and the floor 17. The channel region 28 is a region between the floor 17 and the partition member 81, and the side surface of the channel region 28 is open.
The warm air blown from the outlet 63 to the flow channel region 28 is restricted from flowing downward by the partition member 81, and flows from the side surface of the flow channel region 28 to the outside of the flow channel region 28. The warm air that has flowed to the outside of the flow path region 28 flows while gradually changing the flow direction toward the suction device 50 having a low atmospheric pressure, and is sucked into the suction device 50. The partition member 81 strengthens the turbulent flow in the flow channel region 28 and enlarges the region of the turbulent flow. That is, the partition member 81 makes the area of the turbulent flow region 24 </ b> A larger than the area of the turbulent flow region 24 of the heating device 100. Further, the areas of the turbulent flow region 23A and the laminar flow region 25A of the heating device 110 are substantially equal to the areas of the turbulent flow region 23 and the laminar flow region 25 of the heating device 100. Therefore, the heating capability of the heating device 110 is higher than the heating capability of the heating device 100. That is, the partition member 81 has the effect of increasing the heating capacity.
Further, since the warm air blown out from the outlet 63 is prevented from flowing downward by the partition member 81, the contact between the warm air and the base portion 11 is suppressed.
When the shape of the partition member 81 is substantially the same as the shape of the turbulent flow region 24A, since the turbulent flow generated outside the flow channel region 28 is weak, the warm air does not contact the base portion 11 and heat loss does not occur. Therefore, the partition member 81 reduces the heat loss of the heating device 110 and eliminates the need for a heat insulating material on the base portion 11. The shape of the partition member 81 is preferably substantially the same as the shape of the turbulent flow region 24A.
The connected suction housing 52, duct 71, fan coil housing 31, duct 72, and blowing housing 62 correspond to the passage forming body of the present invention, and the air outlet 63 corresponds to the passage outlet of the present invention.

FIG. 9 schematically shows a plan view of the heating device 120 according to the third embodiment of the heating device of the present invention and the floor under the building 10. FIG. 10 schematically shows a cross section taken along line AA of FIG.
The heating device 120 is obtained by adding partition members 82 and 83 to the heating device 160. FIG. 11A shows a perspective view of the partition member 82. The partition member 82 includes a bottom plate 82A and inclined plates 82B, 82C, and 82D that are inclined. The partition member 82 is disposed such that the bottom plate 82A is positioned below the fan coil suction port 34.
The channel region 29 is a region between the floor 17 and the partition member 82, and the side surface of the channel region 29 is open. The air in the flow path region 29 flows in the direction of the fan coil suction port 34, generates a turbulent flow, and is sucked into the fan coil suction port 34. Air outside the flow channel region 29 passes through the side surface of the flow channel region 29 and is sucked into the fan coil suction port 34. The side surface of the flow channel region 29 is a gap between the floor 17 and the end of the partition member 82. When the total area of all the side surfaces is sufficiently small, the speed of the hot air passing through the side surface of the flow channel region 29 is large. Turbulence is generated near the side surface of the region 29. That is, the partition member 82 strengthens the turbulent flow in the flow path region 29, expands the region where the turbulent flow is generated, and makes the area of the turbulent flow region 23B larger than the area of the turbulent flow region 23C of the heating device 160. . Further, the partition member 82 suppresses contact between the warm air and the base portion 11.

FIG. 11B shows a perspective view of the partition member 83. The partition member 83 includes a bottom plate 83A and inclined plates 83B, 83C, and 83D that are inclined. The partition member 83 is disposed such that the bottom plate 83A is positioned below the fan coil blower outlet 35.
The channel region 28A is a region between the floor 17 and the partition member 83, and the side surface of the channel region 28A is open. The warm air blown out from the fan coil blower outlet 35 to the flow channel region 28A is changed by the partition member 83 in the direction of the floor 17, flows through the side surface of the flow channel region 28A, and flows outside the flow channel region 28A. The side surface of the flow channel region 28A is a gap between the floor 17 and the end of the partition member 83. When the total area of all the side surfaces is sufficiently small, the speed of the hot air passing through the side surface of the flow channel region 28A is large. Turbulence is generated near the side surface of the region 28A. That is, the partition member 83 strengthens the turbulent flow in the flow path region 28A, expands the region where the turbulent flow is generated, and makes the area of the turbulent flow region 24B larger than the area of the turbulent flow region 24C of the heating device 160. . Further, the partition member 83 suppresses contact between the warm air and the base portion 11.
Therefore, the heating device 120 has a higher heating capacity than the heating device 160.
The fan coil suction port 34, the fan coil blowout port 35, and the fan coil housing 31 correspond to the suction port, the passage outlet, and the passage formation body of the present invention, respectively. The material of the partition members 81, 82, 83 may be metal, wood, or other materials.

FIG. 12 schematically shows a plan view of the heating apparatus 130 according to the fourth embodiment of the present invention and the floor under the building 10. FIG. 13 schematically shows a cross section taken along line AA of FIG.
The heating device 130 is obtained by adding a flow path upper surface member 84 to the heating device 110. The flow path upper surface member 84 is a flat plate, has substantially the same shape and size as the partition member 81, and is disposed in parallel with the floor 17 between the floor 17 and the outlet 63. The channel region 28B is a region between the channel upper surface member 84 and the partition member 81, and the side surface of the channel region 28B is open. The warm air is blown out from the outlet 63 to the flow path region 28B.
In the heating device 110, the warm air blown from the outlet 63 flows through the flow path region 28, but the upper surface of the flow path region 28 is composed of the large pull 14, the joists 15, and the floor board 16, and has warm and undulated hot air. The flow of is suppressed. On the other hand, in the heating device 130, the warm air blown from the outlet 63 flows through the flow channel region 28B, and the upper surface of the flow channel region 28B is the flow channel upper surface member 84, which is a flat surface. The speed of the warm air is higher than that of the heating device 110. Therefore, the area of the turbulent region (not shown) of the heating device 130 is larger than the area of the turbulent region 24A of the heating device 110.

Since no air flow path is required between the floor 17 and the flow path upper surface member 84, the flow path upper surface member 84 may be attached in close contact with the large pull 14. In order to warm the floor 17 on the channel upper surface member 84 with warm air, the channel upper surface member 84 is preferably a highly heat conductive metal plate or metal foil. When a member having low thermal conductivity such as wood is used as the flow path upper surface member 84, the warm air flowing through the flow path region 28B by opening a plurality of holes through which air flows in the flow path upper surface member 84 and the floor 17 It is preferable to increase the heat transfer coefficient.
The flow path upper surface member 84 does not directly contact the hot air blown from the blower outlet 63 with the floor plate 16, and avoids the unevenness of the floor 17 to flow the hot air at a high speed, thereby increasing the area of the heated floor 17. The temperature of the floor 17 is made more uniform. Therefore, the heating device 130 including the flow path upper surface member 84 can blow out hot air having a temperature higher than that of the heating device 110 at a higher speed, and the heating device 130 is suitable for a building that requires large-capacity heating. .

FIG. 14 is a plan view schematically showing a heating device 140 according to the fifth embodiment of the heating device of the present invention and the floor under the building 10. FIG. 15 schematically shows a cross section taken along line AA of FIG.
The heating device 140 is obtained by adding guides 85, 85A, and 85B to the heating device 110. The channel region 28C is a region between the floor 17 and the partition member 81, and the side surface of the channel region 28C is open. The guides 85, 85A, and 85B are partition members so that warm air blown from the outlet 63 flows smoothly in the flow channel region 28C and flows out of the flow channel region 28C from the side surface of the flow channel region 28C. 81. Since the guides 85, 85A, and 85B increase the speed of the warm air, the area of the turbulent flow area is increased and the heating capacity is increased.
The guide 85 arranged along the side wall 12 suppresses contact between the warm air and the side wall 12. In addition, it is also possible to arrange | position a guide so that warm air may be flowed along the side wall with large heat dissipation, and the indoor temperature may be made more uniform. Further, a guide made of a curved member is preferable because it increases the speed of hot air. The material of the guides 85, 85A and 85B may be metal, wood or other materials.

FIG. 16 schematically shows a plan view of the heating apparatus 150 according to the sixth embodiment of the present invention and the floor under the building 10. FIG. 17 schematically shows a cross section taken along line AA of FIG.
The heating device 150 is obtained by adding guides 86, 86A, and 86B to the heating device 130. The channel region 28D is a region between the channel upper surface member 84 and the partition member 81, and the side surface of the channel region 28D is open.
The guides 86, 86A, and 86B are partition members so that the warm air blown from the outlet 63 flows smoothly in the flow channel region 28D and flows out of the flow channel region 28D from the side surface of the flow channel region 28D. 81 and the flow path upper surface member 84. Since the guides 86, 86A and 86B increase the speed of the hot air, the area of the turbulent flow area is increased and the heating capacity is increased.
The guide 86 disposed along the side wall 12 suppresses contact between the warm air and the side wall 12. In addition, it is also possible to arrange | position a guide so that warm air may be flowed along the side wall with large heat dissipation, and the indoor temperature may be made more uniform. Further, a guide made of a curved member is preferable because it increases the speed of hot air. The material of the guides 86, 86A and 86B may be metal, wood or other materials.

As mentioned above, although embodiment of the heating apparatus of this invention was described, this invention is not limited to these. For example, in the heating device 100, the duct 72 or 71 may be branched and a plurality of blowing devices or suction devices may be arranged.

10 Buildings, 11 Foundations, 12 Side Walls, 13 Thermal Insulation, 14 Large Pulls, 15 joists, 16 Floorboards, 17 Floors
21 underfloor space, 22 living space, 23 24 turbulent flow region, 25 laminar flow region, 26 natural convection region, 28 29 flow channel region 30 fan coil, 31 fan coil housing, 32 blower, 33 heat exchanger, 34 fan coil Suction port, 35 Fan coil outlet, 36 Air passage, 37 Pump, 38 Heat medium circulation path, 39 Boiler 41 Hot air, 42 Laminar flow, 43 Turbulence, 44 Natural convection 50 Suction device, 51 Suction housing outlet, 52 Suction housing, 53 Suction port 60 Blowout device, 61 Blowout housing inlet, 62 Blowout housing, 63 Blowout port, 64 Nozzle inlet, 65 Nozzle, 66 Nozzle blowout port 71 72 Duct 81-83 Partition member, 84 Flow path upper surface Member, 85 86 guide 100-160 heating device

Claims (6)

A passage forming body that forms air passages for guiding air sucked from a suction port arranged in a subfloor space under the floor of a building to a substantially rectangular passage outlet having one side substantially parallel to the floor;
A blower that blows air from the suction port toward the passage outlet;
A heater for heating air in the passage-forming body;
A first blower device including a blowout housing that forms an air passage that guides air flowing from a blowout housing inlet connected to the passage outlet to a blowout port that blows air into the underfloor space;
The air outlet has an elongated rectangular shape whose long side is substantially parallel to the floor,
The blowout housing forms an air passage on the upper surface, the lower surface and both side surfaces,
The length of the long side is larger than the length of the one side,
The length of the short side of the outlet is smaller than the length of the side orthogonal to the one side,
The distance between the upper surface and the lower surface gradually decreases toward the air outlet,
The heating apparatus according to claim 1, wherein a distance between the side surfaces gradually increases toward the outlet. A nozzle that further forms an air passage that guides air that has flowed from a nozzle inlet connected to the air outlet to an elongated, substantially rectangular nozzle air outlet that blows air into the underfloor space;
The nozzle forms an air passage on the nozzle upper surface, the nozzle lower surface, and both nozzle side surfaces,
The heating apparatus according to claim 1, wherein the nozzle upper surface and the nozzle lower surface are substantially parallel to each other. A passage forming body that forms air passages for guiding air sucked from a suction port disposed in an underfloor space under the floor of a building to a substantially rectangular or substantially circular passage outlet having one side substantially parallel to the floor; ,
A blower that blows air from the suction port toward the passage outlet;
A heater for heating air in the passage-forming body;
A second blow-out device including a blow-out case that forms a passage for air that guides air flowing from a blow-out case inlet connected to the passage outlet to a blow-out port that blows air into the underfloor space;
The air outlet has an elongated rectangular shape whose long side is substantially parallel to the floor,
When the passage exit is substantially rectangular,
The length of the long side of the air outlet is at least twice the length of the one side,
The length of the short side of the outlet is less than or equal to one half of the length of the side orthogonal to the one side,
When the passage exit is substantially circular,
The length of the long side of the outlet is at least twice the diameter of the passage outlet,
The length of the short side of the said blower outlet is 1/3 or less of the diameter of the said channel | path exit, The heating apparatus characterized by the above-mentioned. A partition member arranged to form an air flow path between the floor and the floor under the floor of the building;
A passage forming body that guides air sucked from a suction port arranged in the underfloor space to a passage outlet and forms an air passage so as to blow out between the floor and the partition member from the passage outlet;
A blower that blows air from the suction port toward the passage outlet;
A heating apparatus comprising a heater for heating air in the passage forming body. A channel upper surface member arranged directly under the floor of the building;
A partition member disposed below the flow path upper surface member so as to form an air flow path with the flow path upper surface member;
A passage that forms air passages so that air sucked from a suction port disposed in the underfloor space under the floor is guided to a passage outlet and is blown out from the passage outlet between the flow path upper surface member and the partition member. A formed body;
A blower that blows air from the suction port toward the passage outlet;
A heating apparatus comprising a heater for heating air in the passage forming body. 6. The guide according to claim 4, further comprising one or a plurality of guides disposed on the partition member so as to guide a flow direction of the air blown out from the passage outlet in a predetermined direction. Heating device.

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