JP2010249340A - Heat pump type intermediate temperature air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat pump type intermediate temperature air conditioning system carrying out cooling and heating simultaneous operation by a simple system, requiring only inexpensive facility costs and operation costs, and carrying out comfortable air conditioning. <P>SOLUTION: The heat pump type intermediate temperature air conditioning system is equipped with: a first heat source device 20 carrying out heat exchange of air conditioning heat source water with air via a first air heat source heat pump 21; a first water HP type air conditioner 40 carrying out heat exchange of return air of an air-conditioned space S with the air conditioning heat source water selectively via one or both of an air conditioning first cold temperature water coil 46 and an air conditioning first heat source heat pump 41; and an air type radiation laminar flow unit 1 carrying out induction mixing and distribution diffusion of air of the air-conditioned space S with air-conditioned air supplied from the first water HP type air conditioner 40, discharging the air into the air-conditioned space S like a laminar flow, storing the heat of the induced and mixed air, and carrying out thermal radiation to the air-conditioned space S. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a system that performs air conditioning using medium temperature heat source water.

  There are a radiation type air conditioning system using a radiation panel of a cold / hot water heat source and a forced convection type air conditioning system using a fan coil unit of a cold / hot water heat source.

JP 7-19533 A

  This radiant panel requires less heat energy for air conditioning than the fan coil unit, and the heat source water temperature used by the two differs greatly for reasons such as prevention of panel condensation. Therefore, an air conditioning system that uses both radiation and forced convection is constructed. In this case, many types of equipment such as boilers and cooling towers for adjusting the temperature of the heat source water are necessary, the control mechanism for adjusting the water temperature is complicated, and the equipment cost, operation cost and maintenance cost are increased, and A large installation space is required.

  Moreover, a four-pipe heat source water circuit that allows two types of heat source water to flow at the same time, such as large and medium-sized buildings, hotel rooms, etc. Therefore, high and low temperature operation with only a single heat source device causes waste and waste, further increasing the equipment cost, operation cost and maintenance cost.

  In addition, radiant panels have low air conditioning efficiency due to heat transfer only by heat radiation, and there are many unsuitable areas for air conditioning, such as places with poor heat insulation, places with large heat loads, and places with large amounts of air coming in and out. There is a problem that costs are high because measures are required. Furthermore, forced convection type indoor air conditioners such as a multi-air conditioner and a fan coil unit have a problem that the temperature of cold air or warm air is high and gives a draft feeling, resulting in temperature unevenness.

  In order to solve the above-described problems, the present invention provides a first heat source device that heat-exchanges air-conditioning heat source water with air via a first air heat source heat pump and adjusts the temperature to an intermediate temperature, a first cold / hot water coil for air conditioning, and an air-conditioner. A first water HP type air conditioner that exchanges heat of the return air in the air-conditioned space with the heat source water for air conditioning selectively through one or both of the first water heat source heat pumps, and the first water HP The air in the air-conditioned space is attracted and mixed with the conditioned air supplied from the air conditioner, and is divided and diffused to be discharged into the air-conditioned space in a laminar flow, and the heat of the induced mixed air is stored to store the air-conditioned And a pneumatic radiant laminar flow unit that radiates heat to space.

According to invention of Claims 1-7,
(1) Many types of heat source devices such as boilers and cooling towers need only one type of heat source device, and it is possible to construct a two-pipe type air conditioning system that mixes cooling and heating operations. Reduce CO2 and save space.
(2) Since the temperature of the heat source water may be adjusted to an intermediate temperature, condensation and heat dissipation loss can be prevented, the control mechanism is simplified, and maintenance is facilitated.
(3) Where there is a lot of cooling operation / heating operation, the heat source water can be intermittently operated or stopped by mutual heat recovery of the heat source water, resulting in significant energy saving.
(4) Even if the maximum capacity of the heat source device is exceeded, a heat pump on the air conditioner side and / or the external air conditioner side covers the lack of capacity, and stable air conditioning operation can be performed.
(5) Comfortable air conditioning without drafts or temperature unevenness can be achieved by heat radiation from the induced mixed radiation case and the heat storage radiation shunt and heat transfer of the induced mixed air.

According to the inventions of claims 1, 2, 4, and 5,
(1) When the air conditioning load is small, such as in an intermediate period, the operation of the air conditioning first water heat source heat pump is stopped, and the air conditioning can be performed only by the air conditioning first cold / hot water coil, thereby saving energy.

According to the inventions of claims 2 and 4,
(1) Since the temperature of the heat source water can be adjusted separately for two systems for external conditioning and air conditioning, the water temperature control becomes easy, and air conditioning loads such as when cooling and heating operations coexist in the air conditioning system or during intermediate periods If there is little, only the first heat source device for air conditioning can be intermittently operated or stopped by mutual heat recovery of the heat source water, thereby saving energy.
(2) If two systems for external conditioning and air conditioning are connected and operated with the same heat source water, cooling operation is performed with the air conditioning system, and when heating operation is performed with the external conditioning system, energy is saved by mutual heat recovery of the heat source water.

According to the inventions of claims 2, 3, and 4,
(1) By pre-cooling or heating the outside air or a mixture of outside air and return air with the first cold / hot water coil for external conditioning, the load of the external water conditioning first water heat source heat pump can be reduced, and the humidification efficiency is good. Thus, the temperature and humidity control range of the first water HP-type external air conditioner is expanded.

According to the invention of claim 3,
(1) Since the air-conditioning load can be reduced by the heat recovery effect of the air HP type air conditioner, energy saving is achieved, and the first heat source device for air conditioning can be downsized.

According to the invention of claim 4,
(1) Since the air conditioning load can be reduced by the heat recovery effect of the air HP type air conditioner, energy saving is achieved, and the size of the first heat source device for air conditioning and / or the second heat source device for external conditioning can be reduced.

According to the invention of claim 5,
(1) Although the heat source water should be intermittently operated or stopped by mutual heat recovery of the heat source water at the time of cooling / heating operation of the air conditioner, outside air treatment that always requires constant air supply is excluded from the water source type If it is done with a conditioner, the heat source device cannot be stopped and is wasteful, but the air HP type external conditioner performs the outside air treatment with the air heat source without using the water heat source, so the heat source device is intermittently operated or stopped. This saves energy and reduces CO2.
(2) Since the air recovery load can be reduced by the heat recovery effect of the air HP type external air conditioner, energy saving can be achieved, and the first heat source device for air conditioning can be downsized.

According to the invention of claim 8,
(1) Although the conventional radiation panel only emits heat from the panel surface, in the present invention, in addition to the heat radiation from the induced mixed radiation case, heat is also transmitted from the heat storage radiation shunt to the air-conditioned space through the opening. Since it radiates, radiation (radiation) energy can be made to reach a long distance at a high ratio. This long-distance radiation action and the wide-range and wide-range heat transfer action that occurs by reducing the temperature difference from the air-conditioned space and releasing it in a laminar flow so that the induced mixed air does not stay near the ceiling, and the air-conditioned Due to the synergistic effect of the circulator action caused by the attraction of space air, the air temperature distribution of the air-conditioned space is made uniform, and high-efficiency and high-performance comfortable air-conditioning without drafts and temperature unevenness can be performed. Therefore, there are few spaces unsuitable for air-conditioning compared with air-conditioning only with heat radiation, and the use range is wide.
(2) The conventional radiant panel uses heat source water for heat radiation, but in the present invention, conditioned air is used as the radiant heat source, so there is no worry of a water leak accident, the equipment can be simplified, and there is no blast power. The circulator effect can be obtained and the operating cost can be reduced.
(3) Since the conditioned air and air in the air-conditioned space are mixed, dew point control is possible, drain treatment equipment for countermeasures against condensation is not required, and costs can be reduced. Cooling capacity or heating capacity per conditioned air volume By reducing the air supply air volume by lowering the air supply temperature (lowering or highering the supply air temperature than usual), the cost can be reduced by reducing the blast power and downsizing the equipment such as ducts.

  FIG. 1 shows a first embodiment of a heat pump type intermediate temperature air conditioning system according to the present invention. This heat pump type intermediate temperature air conditioning system heat-exchanges heat source water for air conditioning with air via a first air heat source heat pump 21. Of the air-conditioned space S with the heat source water for air conditioning selectively through one or both of the first heat source device 20 for adjusting the temperature to the intermediate temperature, the first cold / hot water coil 46 for air conditioning and the first water heat source heat pump 41 for air conditioning. The first water HP type air conditioner 40 that exchanges heat of the return air and supplies the air, and the second heat source device that adjusts the temperature of the heat source water for external adjustment with air through the second air heat source heat pump 81 to an intermediate temperature. 80, the external air conditioning heat source water selectively exchanges one or both of the external conditioning first cold / hot water coil 56 and the external conditioning first water heat source heat pump 51, and heats the mixed air of the outside air and the return air to supply air. 1st water HP type external air conditioner 50 and 1st water The conditioned air supplied from the P-type air conditioner 40 or the first water HP-type external air conditioner 50 attracts and mixes the air in the air-conditioned space S, splits and diffuses it, and releases it to the air-conditioned space S in a laminar flow. Heat source water for air conditioning is circulated between the air-type radiant laminar flow unit 1 that stores the heat of the induced mixed air and radiates heat to the air-conditioned space S, and the first heat source device 20 and the first water HP type air conditioner 40. And a second heat source water circuit 87 that circulates the heat source water for external adjustment between the second heat source device 80 and the first water HP type external conditioner 50. In each figure, the air flow is indicated by a thick black arrow, and the heat source water flow is indicated by a white arrow. Pneumatic radiant laminar flow unit 1 and first water HP type external air conditioner 50, air-conditioned space S and first water HP type external air conditioner 50, air radiant laminar flow unit 1 and first water HP type air conditioner 40, The air-conditioned space S and the first water HP air conditioner 40 are connected to each other via an air passage such as a duct (not shown).

  The first heat source water circuit 27 includes a first water pump 28, a first water heat exchanger 22 of the first heat source device 20, a first water heat exchanger 42 for air conditioning of the first water HP type air conditioner 40, The air source heat source water flows through the first water HP type air conditioner 40 through the piping of the first heat source water circuit 27 and circulates between the first heat source device 20 and the first heat source device 20. The second heat source water circuit 87 includes a second water pump 88, a second water heat exchanger 82 of the second heat source device 80, a first water heat exchanger 52 for external adjustment of the first water HP-type external conditioner 50, and The external conditioning first cold / hot water coil 56 is connected to allow free passage of water, and the external conditioning heat source water flows through the first water HP-type external conditioner 50 through the piping of the second heat source water circuit 87. It circulates between the two heat source devices 80. The heat source water flow rates of the first water HP air conditioner 40 and the first water HP air conditioner 50 are controlled by a valve or the like.

  As shown in FIG. 2, the first heat source device 20 includes a first air heat source heat pump 21 and an air heat exchanger first fan 25 in the casing. The first air heat source heat pump 21 repeats the evaporating, compressing, condensing, and expanding steps in order with respect to the circulating refrigerant, and the refrigerant condensing step absorbs heat in the refrigerant evaporating step with respect to air and heat source water that exchange heat with the circulating refrigerant. The first air heat exchanger 23 and the first water heat exchanger 22 that perform different processes in the circulation refrigerant evaporation process and the condensation process, respectively, and the first compressor that compresses the circulation refrigerant 24, a decompression mechanism such as an expansion valve for expanding the circulating refrigerant, and a switching mechanism such as a valve for switching between the evaporation process and the condensation process of the first air heat exchanger 23 and the first water heat exchanger 22, These are connected by piping so that the refrigerant circulates. The first air heat exchanger 23 exchanges heat between the circulating air such as outside air and the circulating refrigerant, and the circulating refrigerant and the heat source water for air conditioning are heat-exchanged by the first water heat exchanger 22, so that the first heat source device The air conditioning heat source water outlet temperature is controlled by a control means (not shown) so that it falls within a predetermined water temperature range.

  Since the second heat source device 80 has the same configuration as the first heat source device 20, a description will be given with reference to FIG. The second heat source device 80 includes a second air heat source heat pump 81 and an air heat exchanger second fan 85 in the casing. The first air heat source heat pump 81 repeats the evaporating / compressing / condensing / expanding process sequence for the circulating refrigerant, and the refrigerant condensing process absorbs heat in the refrigerant evaporating process with respect to air and heat source water exchanged with the circulating refrigerant. The second air heat exchanger 83 and the second water heat exchanger 82, which perform heat dissipation in the circulating refrigerant and perform different processes in the circulating refrigerant evaporation process and the condensation process, and the second compressor for compressing the circulating refrigerant, respectively. 84, a decompression mechanism such as an expansion valve for expanding the circulating refrigerant, and a switching mechanism such as a valve for switching between the evaporation process and the condensation process of the second air heat exchanger 83 and the second water heat exchanger 82, These are connected by piping so that the refrigerant circulates. The second air heat exchanger 83 exchanges heat between the ventilating air such as outside air and the circulating refrigerant, and the circulating refrigerant and the external conditioning heat source water are heat-exchanged by the second water heat exchanger 82, whereby the second heat source device. It is controlled by a control means (not shown) so that the 80 external heat source water outlet temperature falls within a predetermined water temperature range.

  The outlet water temperature range of the heat source water for air conditioning and the heat source water for external conditioning is set to a medium temperature of 13 ° C. to 40 ° C., for example, 13 to 18 ° C. during cooling operation and 35 to 40 ° C. during heating operation are appropriate temperatures. Be free. In addition, outside the range of 13 ° C to 40 ° C, the heat insulation treatment of the pipes of the first and second heat source water circuits 27 and 87 is expensive and maintenance is troublesome, and the compression ratio and COP of each heat pump are lowered. To do. The first water heat exchanger 22 and the second water heat exchanger 82 are desirably hermetically sealed, and there is no evaporation loss of the heat source water and the water quality can be maintained and maintenance is easy, but other methods may be used.

  As shown in FIG. 3, the first water HP type air conditioner 40 includes an air conditioning first cold / hot water coil 46, an air conditioning first water heat source heat pump 41, and an air conditioning first air supply fan 45 in a casing. It is equipped with. The first water heat source heat pump 41 for air conditioning repeats the steps of evaporation / compression / condensation / expansion with respect to the circulating refrigerant, and the refrigerant evaporates heat to the air or heat source water that exchanges heat with the circulating refrigerant. Each heat release in the condensing step, the first air heat exchanger 43 for air conditioning and the first water heat exchanger 42 for air conditioning performing the steps of evaporating and condensing the circulating refrigerant, which are different from each other, and the circulating refrigerant The evaporating process and the condensing process of the first compressor 44 for air conditioning to be compressed, a pressure reducing mechanism such as an expansion valve for expanding the circulating refrigerant, the first air heat exchanger 43 for air conditioning and the first water heat exchanger 42 for air conditioning. And a switching mechanism such as a valve for switching, and these are connected by piping so that the refrigerant circulates. The first water HP type air conditioner 40 controls the heat source water flow rate of the first cold / hot water coil 46 for air conditioning by bypassing part or all of the heat source water to the first cold / hot water coil 46 for air conditioning. A control mechanism 49 is provided. In the illustrated example, the air-conditioning flow rate control mechanism 49 is configured by a three-way valve, a bypass flow path, or the like, but the configuration can be freely changed.

  The first water HP type air conditioner 40 has one of the air conditioning first cold / hot water coil 46 and the air conditioning first air heat exchanger 43 or not by control means (not shown) so as to have a preset supply air temperature. In both cases, the return air is cooled or heated so that the cooling operation and the heating operation can be switched, and conditioned air is supplied to the pneumatic radiant laminar flow unit 1. In the first water HP type air conditioner 40, where the air conditioning first water heat source heat pump 41 is often mixed in the cooling / heating operation, the first heat source device is a mutual heat recovery operation by mixing the cold drainage and the warm drainage. The air conditioning can be performed only by circulating the heat source water for air conditioning without operating 20.

  As shown in FIG. 4, the first water HP-type external air conditioner 50 includes an external air conditioning first cold / hot water coil 56, an external air conditioning first water heat source heat pump 51, and an external air conditioning first air supply fan 55. And a first humidifier 57 for external adjustment. The first water heat source heat pump 51 for external adjustment repeats the steps of evaporation, compression, condensation, and expansion with respect to the circulating refrigerant, and the refrigerant absorbs heat in the refrigerant evaporation step with respect to air and heat source water that exchange heat with the circulating refrigerant. Each heat release is performed in the condensing step. The external air conditioning first air heat exchanger 53 and the external air conditioning first water heat exchanger 52 that perform different steps of the circulating refrigerant evaporation step and the condensing step, and the circulating refrigerant A first compressor 54 for external adjustment to be compressed, a decompression mechanism such as an expansion valve for expanding the circulating refrigerant, an evaporation process and a condensation process of the first air heat exchanger 53 for external adjustment and the first water heat exchanger 52 for external adjustment. A switching mechanism such as a valve for switching, and a reheater 58 for refrigerant-air heat exchange using the hot gas from the first compressor 54 for external conditioning as a reheating medium, so that the refrigerant circulates in these. Connected to the pipe. The first water HP type external air conditioner 50 is used for external adjustment to control the heat source water flow rate of the first cold / hot water coil 56 for external adjustment by bypassing part or all of the heat source water to the first cold / hot water coil 56 for external adjustment. A flow rate control mechanism 59 is provided. In the illustrated example, the external adjustment flow control mechanism 59 is configured by a three-way valve, a bypass flow path, or the like, but the configuration can be freely changed.

  The first water HP type external air conditioner 50 is controlled by a control means (not shown) so that one of the external air conditioning first cold / hot water coil 56 and the external air conditioning first air heat exchanger 53 is set to a preset temperature and humidity. Alternatively, the mixed air of the outside air and the return air is cooled / reheated or heated / humidified, and the conditioned air is supplied to the pneumatic radiant laminar flow unit 1 so that the cooling operation and the heating operation can be switched. The temperature / humidity of the air-conditioned space S is detected by a detector (not shown) and compared with a set value by the control means to control the operation of the first water HP type external air conditioner 50 and the first water HP type air conditioner 40. To do.

  As shown in FIGS. 5 to 11, the pneumatic radiant laminar flow unit 1 is exposed in the air-conditioned space S and the air supply member 11 that is embedded in the ceiling C and sends out conditioned air supplied from the air conditioner. The conditioned air of the air supply member 11 is blown into the induction port 10 on the upper surface while being embedded in the ceiling C, and the air in the air-conditioned space S is attracted and mixed to be air-conditioned from the numerous apertures 9 on the lower surface. An inductive mixed radiation case 16 that emits downward toward the space S, a box-shaped hood 13 that opens downward and flattened vertically, and a maintenance inspection panel 17 are provided. The conditioned air is supplied from the air conditioner and the external air conditioner via an air duct (not shown) such as a duct.

  In the inside of the induction mixing radiation case 16, the induction mixing air is split side by side to be laminar and guided to the air-conditioned space S through the aperture 9, and the heat of the induction mixing air is stored to induce mixing. There is provided a heat storage radiation shunt 2 that conducts heat to the radiation case 16 to radiate heat to the air-conditioned space S and to radiate heat to the air-conditioned space S through the opening 9. The heat storage radiation shunt 2 is in a rectangular shape that is flat vertically, and is brought into contact with at least the bottom surface of the attracting and mixing radiation case 16 so as to be capable of conducting heat.

  The heat storage radiation shunt 2 is made of a material such as aluminum, which is free to store heat and has high heat conduction and heat emissivity, and is provided with a plurality of horizontally long strips of heat transfer plates 8 facing each other at a predetermined pitch and inductively mixed air. Is divided and passes through the gap between the heat transfer plates 8 and 8 in a laminar flow from top to bottom while transferring heat. A plurality of elliptical straight pipes 99 are inserted into each heat transfer plate 8 at intervals from the normal direction so that the elliptical long axis of the elliptical straight pipes 99 is directed in the vertical (gravity) direction. . The elliptical straight pipe 99 can prevent and reinforce deformation of the heat storage radiation shunt 2 such as warping and bending, and is highly safe, and the induced mixed air can be discharged smoothly with low pressure loss.

  The induced mixed air becomes a laminar flow while passing through the gap between the heat transfer plates 8 and 8 by reducing the wind speed while being shunt-diffused by the member resistance of the heat storage and radiation shunt 2 and the induced mixed radiation case 16, and the heat of the induced mixed air Is uniformly transferred to the entire area of the heat storage radiation shunt 2. The opening 9 is formed at a distance from the substantially entire lower surface of the attracting and mixing radiation case 16. In this way, the heat transfer plate 8 can efficiently and reliably transfer the heat of the attracted mixed air to the entire area of the heat storage and radiation shunt 2 to store the heat, and the heat can be uniformly conducted to the attracting and mixed radiation case 16 so that it is always stable. Heat radiation. Furthermore, the induced mixed air can be discharged in a laminar flow by the heat transfer plate 8, and the air-conditioning air temperature distribution can be equalized. In the illustrated example, the opening 9 has a long hole shape, but it may be round or other shapes. In order to maximize the heat radiation effect of the heat storage radiation shunt 2 and the induced mixed radiation case 16 to the air-conditioned space S and the heat transfer effect by the induced mixed air discharge, an opening portion for the entire lower surface of the induced mixed radiation case 16 The total area ratio of the entire 9 is preferably set to 30% or more, but can be changed freely.

  Further, in order to optimally function the diversion diffusion action, laminar flow passage action and heat transfer action of the induced mixed air, the wind speed on the air outlet side is less than half, preferably 20% with respect to the air inlet side of the heat storage radiation shunt 2. The shape, number, pitch, and the like of the heat transfer plate 8 and the apertures 9 are set so as to be reduced to ˜30%. In the illustrated example, the straight pipe 99 has an elliptical shape, but may have a perfect circle shape, or a hole in the heat transfer plate 8 where the straight pipe 99 is not inserted may be omitted. Changes in shape, structure, etc. are free.

  The hood 13 is embedded in the ceiling C with its lower opening 14 exposed to the air-conditioned space S. In the hood 13, a rectangular-shaped attracting and mixing radiation case 16 that is flattened up and down is used for an attraction air path between at least two opposing side surfaces of the peripheral side surface to the entire upper surface and the inner surface of the hood 13. The spacing portion 15 is provided and installed. The attracting and mixing radiation case 16 is configured to be openable / closable or detachable with respect to the hood 13. In the example of the drawing, the spacing portion 15 is provided so as to wrap around the upper surface from both sides in the long side (longitudinal) direction of the attracting mixed radiation case 16, but it also wraps around the top surface from both sides in the short side direction. (All circumferences) Changes are free, such as providing an interval portion on all sides.

  On the lower surface side of the hood 13, a maintenance inspection panel 17 adjacent to one end side of the attracting and mixing radiation case 16 is provided so as to be openable and detachable, and an inspection port 19 is provided on the upper surface side of the hood 13 to cover it. With lid, it can be opened and closed or removed. The air inlet 18 of the air supply member 11 is provided in the vicinity of the inspection port 19. This allows easy maintenance from the panel 17 without removing the entire radiant laminar flow unit 1 from the ceiling C or providing a separate inspection port 19 in the ceiling C, and the air inlet 18 of the air supply member 11 is inspected. Since it is beside the opening 19, construction and maintenance of a conditioned air blowing duct (not shown) can be performed from the panel 17 and the inspection opening 19, and workability is improved. The panel 17 and the inspection port 19 may be omitted.

  A line-shaped induction port 10 for blowing conditioned air of the air supply member 11 is formed along the center line L between the two opposing side surfaces that form the interval portion 15 on the upper surface of the induction mixing radiation case 16, A line-shaped air outlet 12 that blows out conditioned air along the induction port 10 is formed in the longitudinal direction of the air supply member 11. The inner space of the air supply member 11 is provided with a rectifying mechanism G that reduces the diameter from the windward side in the long side direction of the air outlet 12 toward the leeward side and adjusts the air direction in the air supply member 11. In the illustrated example, the inside of the air supply member 11 is partitioned by the inclined plate 11a to reduce the inner space, but the diameter of the air supply member 11 itself may be reduced or may be reduced by other methods. Further, a partition plate 7 a that guides conditioned air in the longitudinal direction of the air supply member 11 is provided directly below the air inlet 18. The partition plate 7a is narrower than the inner width of the air supply member 11 so that a part of the conditioned air flows from both sides to the bottom. Note that the partition plate 7a may be omitted by configuring the air outlet 12 not to be positioned below the air inlet 18, and the air supply member 11 is formed in a funnel-shaped cross section with the upper portion narrowed and the lower portion narrowed. However, changes in shape, structure, etc. are free.

  In this way, the attracted mixed air is sent down along the center line L of the attracted mixed radiation case 16 and discharged to the air-conditioned space S through the heat storage radiation shunt 2 so that the attracted mixed air is unevenly distributed throughout the heat storage radiation shunt 2. In addition, it is possible to surely diffuse and diffuse without a bypass, to flow in a laminar flow, and to conduct heat uniformly throughout the radiation cover 7, so that the effective air conditioning range per unit is wide and the air conditioning efficiency can be improved. Moreover, since it is flat at the top and bottom, the pneumatic radiant laminar flow unit 1 can be easily installed in a narrow ceiling. Further, only one air outlet 12 of the air supply member 11 is required, the structure can be simplified and the manufacture is easy. And since the diameter of the internal space of the air supply member 11 is reduced from the windward side in the long side direction of the air outlet 12 toward the leeward side, the wind speed can be made uniform throughout the long side direction of the air outlet 12 and variations are caused. Does not occur. Therefore, there is no attraction unevenness, the circulator effect is high, the attraction air can be mixed evenly, there is no temperature unevenness of the air discharged from the attraction mixing radiation case, and stable comfortable air conditioning can be performed.

  The rectifying mechanism G is formed by providing a plurality of small wall strips 7 extending in a direction intersecting with the airflow direction of the conditioned air at intervals. When there is no rectifying mechanism G, conditioned air flows obliquely downward, but the wind direction can be adjusted directly below by the resistance of the rectifying mechanism G. The width and height of the small wall strip 7 can be freely changed. However, if the small wall strip 7 is too low, the direction of the wind cannot be adjusted. If it is too high, the conditioned air is small as indicated by the thick dotted arrow in FIG. A portion where there is no air flow is intermittently generated in the space between the dotted thick arrow and the solid thick arrow without being able to reach the lee of the wall strip 7. In order to prevent the air current from being interrupted and to eliminate temperature unevenness, the height of the small wall strip 7 is preferably set to 10 to 30% of the maximum cross-sectional area of the internal space of the air supply member 11.

  As shown in FIG. 10, the blower width adjusting mechanism A capable of changing the blown air speed by adjusting the gap width HA on the short side of the line-shaped air outlet 12, and the short-side side of the line-shaped induction port 10. An induction width adjusting mechanism B is provided that can adjust the induction wind speed by adjusting the gap width HB. The blowout width adjusting mechanism A includes a blower outlet width adjusting member 3 that increases or decreases the gap width HA on the short side of the blower outlet 12, and fixing means 4 that attaches the blower outlet width adjusting member 3 detachably or slidably. The attracting width adjusting mechanism B includes an attracting port width adjusting member 5 that increases or decreases the gap width HB on the short side of the attracting port 10 and a fixing unit 6 that attaches the attracting port width adjusting member 5 detachably or slidably. The fixing means 4 and 6 are formed of a known screwed member such as a screw indicated by a dashed line. In the illustrated example, the blower outlet width adjusting member 3 and the attraction opening width adjusting member 5 are configured using a pair of bent pieces, but the shape, structure, and the like can be freely changed. Taking an example of the induced air mixing ratio optimum for air conditioning, the conditioned air blowing air volume: the induced air volume is about 6: 4, but the setting change is free. In this way, the blown air speed and / or the induced air speed can be arbitrarily changed, the optimum air mixing ratio for air conditioning can be selected, and the air conditioning efficiency can be further improved. It should be noted that one or both of the blowout width adjusting mechanism A and the attraction width adjusting mechanism B may be omitted.

  As shown in FIG. 9, when the conditioned air is blown out from the air-feeding member 11 and enters the induction mixing radiation case 16 as indicated by a solid thick arrow, the gap between the air outlet 12 and the air inlet 10 becomes negative pressure. Then, the air in the air-conditioned space S is attracted through the spacing portion 15 as indicated by a short dotted thick arrow, and is shunted and diffused while being mixed in the induced mixing radiation case 16 as indicated by a long thick dotted arrow. It is discharged into the space S in a laminar flow. By repeating these steps, air is circulated and stirred between the air-conditioned space S and the pneumatic radiant laminar flow unit 1. During cooling, air conditioning is performed using induced mixed air and cold heat radiation that are lower in temperature than the air-conditioned space, and during heating, air conditioning is performed using induced mixed air and heat radiation that is higher in temperature than the air-conditioned space. The conditioned air is set so that the absolute humidity becomes lower than the dew point temperature of the air-conditioned space when it is attracted and mixed, for example, in order to prevent dew condensation and increase the efficiency of air conditioning.

  In the first embodiment of FIG. 1, it is also free to supply conditioned air by exchanging only the outside air with the first water HP-type external conditioner 50. Further, in the illustrated example, the system is configured as an outside air processing and circulation air conditioning system, but the second heat source device 80, the first water HP type external conditioner 50, and the second heat source water circuit 87 are omitted, and only the circulation air conditioning is performed. The system can be configured freely.

  FIG. 12 shows a first embodiment in which an air HP type air conditioner 60 is provided in which heat is recovered from the air in the air-conditioned space S by the air-conditioning air heat source heat pump 61 and heat is exchanged to supply the return air. This is two examples. As shown in FIG. 13, the air HP air conditioner 60 includes an air conditioning air heat source heat pump 61, an air conditioning supply fan 65, an air conditioning exhaust fan 66, and an air conditioning humidifier 67 in a casing. I have. The air heat source heat pump 61 for air conditioning repeats the steps of evaporation, compression, condensation, and expansion with respect to the circulating refrigerant, and absorbs heat in the refrigerant evaporation step and releases heat to the air that exchanges heat with the circulating refrigerant in the refrigerant condensation step. The air-conditioning supply-side air heat exchanger 62 and the air-conditioning exhaust-side air heat exchanger 63 that perform the steps of evaporating and condensing the circulating refrigerant, which are different from each other, and the air-conditioning compression for compressing the circulating refrigerant , A decompression mechanism such as an expansion valve for expanding the circulating refrigerant, and a switching mechanism such as a valve for switching between the evaporation process and the condensation process of the air-conditioning supply-side air heat exchanger 62 and the air-conditioning exhaust-side air heat exchanger 63 And a reheater 68 for refrigerant-air heat exchange using hot gas from the air conditioning compressor 64 as a reheating medium, and these are connected by piping so that the refrigerant circulates.

  The air-type radiant laminar unit 1, the air HP type air conditioner 60, and the air-conditioned space S are connected to each other via an air passage such as a duct (not shown). The air HP type air conditioner 60 is exhausted to the outside or the like while recovering heat from the air in the air-conditioned space S by the air-conditioning exhaust side air heat exchanger 63, and is not shown so as to have a preset temperature and humidity. With this control means, the return air is cooled / reheated or heated / humidified by the air supply air heat exchanger 62 for air conditioning, and the conditioned air is supplied to the pneumatic radiant laminar flow unit 1 so that the cooling operation and the heating operation can be switched. I care. The temperature and humidity of the air-conditioned space S are detected by a detector (not shown), compared with a set value by the control means, and the operation of the air HP air conditioner 60 is controlled. Since other configurations are the same, description thereof is omitted. In the second embodiment, the first heat source device 20, the first water HP air conditioner 40, and the first heat source water circuit 27 may be configured to be omitted.

  FIG. 14 is a third example in which an air HP type external conditioner 70 is provided in place of the first water HP type external conditioner 50 in the first example. As shown in FIG. 15, the air HP type external air conditioner 70 includes an external air heat source heat pump 71, an external air supply fan 75, an external air exhaust fan 76, and an external air humidifier 77 inside the casing. It has. The external conditioning air heat source heat pump 71 repeats the steps of evaporation / compression / condensation / expansion with respect to the circulating refrigerant, and the heat exchanged with the circulating refrigerant is performed in the refrigerant evaporation step, and the heat is dissipated in the refrigerant condensation step. An external adjustment supply-side air heat exchanger 72 and an external adjustment exhaust-side air heat exchanger 73 that perform different processes of evaporation and condensation of the circulating refrigerant and an external adjustment compression that compresses the circulating refrigerant. , A decompression mechanism such as an expansion valve that expands the circulating refrigerant, and a switching mechanism such as a valve that switches between the evaporation process and the condensation process of the external adjustment air supply side air heat exchanger 72 and the external adjustment exhaust side air heat exchanger 73 And a reheater 78 for refrigerant-air heat exchange using hot gas from the external compressor 74 as a reheating medium, and these are connected by piping so that the refrigerant circulates.

  The air-type radiant laminar flow unit 1, the air HP-type external air conditioner 70, and the air-conditioned space S are connected to each other via an air passage such as a duct (not shown). The air HP-type external air conditioner 70 is exhausted to the outside or the like while recovering heat from the air in the air-conditioned space S by the external air-conditioning exhaust air heat exchanger 73, and at the same time, is set to a preset temperature and humidity. By the omitted control means, the outside air is cooled / reheated or heated / humidified by the external air supply side air heat exchanger 72 so that the cooling operation and the heating operation can be switched to supply conditioned air to the pneumatic radiant laminar flow unit 1. I care. The temperature and humidity of the air-conditioned space S are detected by a detector (not shown), compared with a set value by the control means, and the operation of the air HP type external air conditioner 70 is controlled. Since other configurations are the same, description thereof is omitted. Since the air HP type external conditioner 70 performs the outside air treatment with the heat energy of the air without using the heat source water, it is not necessary to operate the first heat source device 20 wastefully. For example, in the place where the cooling and heating operations of the first water HP type air conditioner 40 are mixed, the heat source operation is performed without mixing the first heat source device 20 without the first heat source device 20 being operated. Air conditioning can be achieved only by circulation.

  FIG. 16 shows a second water HP type air conditioner 90 that exchanges heat of the return air with the air source heat source water via the air conditioning second water source heat pump 91 and supplies the air, and the first water HP type air conditioner shown in FIG. The machine 40 has the same configuration as that of the first cold / hot water coil 46 for air conditioning and the flow rate control mechanism 49 for air conditioning. The second water HP air conditioner 90 includes a second water heat source heat pump 91 for air conditioning and a second air supply fan 95 for air conditioning in a casing. The second water heat source heat pump 91 for air conditioning includes a second air heat exchanger 93 for air conditioning and a second water heat exchanger 92 for air conditioning that perform different steps of the evaporation and condensation steps of the circulating refrigerant, and the circulating refrigerant. The evaporation step and the condensation step of the second compressor 94 for air conditioning to be compressed, the pressure reducing mechanism such as an expansion valve for expanding the circulating refrigerant, the second air heat exchanger 93 for air conditioning and the second water heat exchanger 92 for air conditioning. And a switching mechanism such as a valve for switching, and these are connected by piping so that the refrigerant circulates.

  FIG. 17 shows a second water HP type external air conditioner 30 that supplies air by heat-exchanging only the outside air or a mixture of outside air and return air with the outside conditioning heat source water via the outside water conditioning second water source heat pump 31. Thus, the first water HP type external air conditioner 50 of FIG. 4 has the same configuration as that in which the external adjustment first cold / hot water coil 56 and the external adjustment flow control mechanism 59 are omitted. The second water HP type external air conditioner 30 includes an external air conditioning second water heat source heat pump 31, an external air conditioning second air supply fan 35, and an external air conditioning second humidifier 36 in the casing. The second water heat source heat pump 31 for external conditioning is a second air heat exchanger 33 for external conditioning and a second water heat exchanger 32 for external conditioning that perform the steps of evaporation and condensation of the circulating refrigerant, which are different from each other, and the circulating refrigerant. The evaporation step and the condensation step of the second compressor 34 for external adjustment to be compressed, the pressure reducing mechanism such as an expansion valve for expanding the circulating refrigerant, the second air heat exchanger 33 for external adjustment and the second water heat exchanger 32 for external adjustment. A switching mechanism such as a valve for switching, and a reheater 37 for refrigerant-air heat exchange using hot gas from the second compressor for external conditioning 34 as a reheating medium, so that the refrigerant circulates therethrough. Connected to the pipe.

  Although not shown, the second water HP air conditioner 90 is provided instead of the first water HP air conditioner 40 or the second water HP is replaced with the first water HP air conditioner 50 in each of the embodiments. It is also free to configure the system by providing the HP type external air conditioner 30. Furthermore, the first heat source device 20, the second heat source device 80, the pneumatic radiant laminar flow unit 1, the first water HP air conditioner 40, the second water HP air conditioner 90, the first water HP air conditioner 50, The number of the second water HP-type external air conditioner 30, the air HP-type air conditioner 60, and the number of the air HP-type external air conditioners 70 can be increased or decreased. Alternatively, in the first embodiment of FIG. 1 and the second embodiment of FIG. 12, the first heat source water circuit 27 and the second heat source water circuit 87 are connected to each other, and the same heat source water is supplied to the first heat source device 20 and the second heat source device 20. It is also possible to adjust the temperature in both the heat source device 80, only one, or omit one and only the other, and in the air-conditioned space that cools even in winter, cooling operation with an air conditioner, heating operation with an external air conditioner Then, energy is saved by mutual heat recovery of the heat source water. The first and second heat source water circuits 27 and 87 can be freely changed to various methods such as a direct return method, a reverse return method, and a combination of these methods. Furthermore, each of the heat pumps 21, 81, 41, 91, 51, 31 is preferably an electric drive type, and by using it at midnight power, the operation cost can be greatly reduced and CO2 can be reduced. Other driving methods may be used.

1 is an overall simplified explanatory diagram of a first embodiment of the present invention. It is a simplified explanatory view of a heat source device. It is a simplified explanatory view of the 1st water HP type air conditioner. It is a simple explanatory view of the 1st water HP type external air conditioner. It is the perspective view seen from the bottom face side of a pneumatic radiation laminar flow unit. It is a top view of a pneumatic radiation laminar flow unit. It is the top view which fractured | ruptured a part of upper surface of the induction mixing radiation case. It is side surface sectional drawing of an air supply member and an attraction | suction mixing radiation case. It is the whole sectional view seen from the E direction of FIG. It is principal part sectional drawing of an air supply member and the attraction | suction mixing radiation case seen from the F direction of FIG. It is the perspective view which fractured | ruptured a part of upper surface of an air supply member. It is the whole simplified explanatory drawing of 2nd Example of this invention. It is a simplified explanatory view of an air HP type air conditioner. It is the whole simplified explanatory drawing of 3rd Example of this invention. It is a simplified explanatory view of an air HP type external air conditioner. It is a simplified explanatory view of the 2nd water HP type air conditioner. It is a simple explanatory view of the 2nd water HP type external air conditioner.

DESCRIPTION OF SYMBOLS 1 Pneumatic radiation laminar flow unit 2 Heat storage radiation diverter 9 Opening part 10 Induction port 11 Air supply member 16 Induction mixing radiation case 20 1st heat source apparatus 21 1st air heat source heat pump 30 2nd water HP type external conditioner 31 Outside Second water heat source heat pump for conditioning 40 First water HP type air conditioner 41 First water heat source heat pump for air conditioning 46 First cold / hot water coil for air conditioning 50 First water HP type air conditioner 51 First water heat source heat pump for external conditioning 56 For external conditioning First hot / cold water coil 60 Air HP air conditioner 61 Air heat source heat pump for air conditioning 70 Air HP external air conditioner 71 Air conditioning heat source heat pump for external air conditioning 80 Second heat source device 81 Second air heat source heat pump 90 Second water HP air conditioner 91 2nd water heat source heat pump for air conditioning C Ceiling S Air-conditioned space

Claims (8)

  A first heat source device (20) for heat-adjusting the air-conditioning heat source water with air via the first air heat source heat pump (21) to adjust the temperature to an intermediate temperature, a first air-conditioning cold / hot water coil (46), and an air-conditioning first 1st water HP type air conditioner (40) which heat-exchanges the return air of the to-be-conditioned space (S) with the heat source water for air conditioning through one or both of one water heat source heat pump (41) and supplies it ) And the conditioned air supplied from the first water HP type air conditioner (40), the air in the air-conditioned space (S) is attracted and mixed to be shunted and diffused to form a laminar flow in the air-conditioned space (S) And a pneumatic radiant laminar flow unit (1) that stores the heat of the induced mixed air and radiates heat to the air-conditioned space (S).   A first heat source device (20) for heat-adjusting the air-conditioning heat source water with air via the first air heat source heat pump (21) to adjust the temperature to an intermediate temperature, a first air-conditioning cold / hot water coil (46), and an air-conditioning first 1st water HP type air conditioner (40) which heat-exchanges the return air of the to-be-conditioned space (S) with the heat source water for air conditioning through one or both of one water heat source heat pump (41) and supplies it ), A second heat source device (80) for heat-exchanging the heat source water for external adjustment with air via the second air heat source heat pump (81) and adjusting the temperature to an intermediate temperature, and a first cold / hot water coil for external adjustment (56) Of the first water HP type that supplies heat by exchanging only outside air or a mixture of outside air and return air with the outside conditioning heat source water selectively through one or both of the outside water conditioning first water heat source heat pumps (51). External air conditioner (50) and the first water HP air conditioner (40) or the first water HP air conditioner The air in the air-conditioned space (S) is attracted and mixed with the conditioned air supplied from (50), and diffused and diffused to be discharged into the air-conditioned space (S) in a laminar flow, and the heat of the induced mixed air is An air-type radiant laminar flow unit (1) that stores heat and radiates heat to the air-conditioned space (S).   A second heat source device (80) for adjusting the temperature to an intermediate temperature by heat-exchanging the heat source water for external adjustment with air via the second air heat source heat pump (81), a first cold / hot water coil (56) for external adjustment, 1st water HP type external air conditioner which heat-exchanges only the external air or the mixture of external air and return air with the external heat source water selectively through one or both of the 1 water heat source heat pump (51) (50), an air HP type air conditioner (60) for exchanging heat from the air in the air-conditioned space (S) by the air-conditioning air heat source heat pump (61) and supplying air by heat exchange, 1 The air in the air-conditioned space (S) is attracted and mixed by conditioned air supplied from the water HP-type external air conditioner (50) or the air HP-type air conditioner (60), and divided and diffused to form a laminar flow. The air to be conditioned is discharged to the air conditioned space (S) and the heat of the attracted mixed air is stored. Heat pump medium temperature air conditioning system, characterized in that a pneumatic radiation laminar flow unit (1), equipped with the) to heat radiation.   A first heat source device (20) for heat-adjusting the air-conditioning heat source water with air via the first air heat source heat pump (21) to adjust the temperature to an intermediate temperature, a first air-conditioning cold / hot water coil (46), and an air-conditioning first 1st water HP type air conditioner (40) which heat-exchanges the return air of the to-be-conditioned space (S) with the heat source water for air conditioning through one or both of one water heat source heat pump (41) and supplies it ), A second heat source device (80) for heat-exchanging the heat source water for external adjustment with air via the second air heat source heat pump (81) and adjusting the temperature to an intermediate temperature, and a first cold / hot water coil for external adjustment (56) Of the first water HP type that supplies heat by exchanging only outside air or a mixture of outside air and return air with the outside conditioning heat source water selectively through one or both of the outside water conditioning first water heat source heat pumps (51). The air-conditioned space (S) by the air conditioner (50) and the air heat source heat pump (61) for air conditioning. An air HP type air conditioner (60) that exchanges heat and supplies the return air while recovering heat from the air, and the first water HP type air conditioner (40) or the first water HP type external air conditioner ( 50) or conditioned air supplied from the air HP type air conditioner (60), the air in the air-conditioned space (S) is attracted and mixed, divided and diffused, and released into the air-conditioned space (S) in a laminar flow And a pneumatic radiant laminar flow unit (1) for storing heat of the attracted mixed air and radiating heat to the air-conditioned space (S).   A first heat source device (20) for heat-adjusting the air-conditioning heat source water with air via the first air heat source heat pump (21) to adjust the temperature to an intermediate temperature, a first air-conditioning cold / hot water coil (46), and an air-conditioning first 1st water HP type air conditioner (40) which heat-exchanges the return air of the to-be-conditioned space (S) with the heat source water for air conditioning through one or both of one water heat source heat pump (41) and supplies it ), And an air HP type external air conditioner (70) for exchanging heat and supplying air while recovering heat from the air in the air-conditioned space (S) with an air conditioning heat source heat pump (71), and the first The conditioned air supplied from the water HP air conditioner (40) or the air HP external air conditioner (70) attracts and mixes the air in the air-conditioned space (S) and splits and diffuses it to form a laminar flow. The air-conditioned space (S) is discharged into the air-conditioned space (S) and stores the heat of the attracted mixed air. Heat pump medium temperature conditioning system characterized by comprising a pneumatic radiation laminar flow unit for thermal radiation (1), the.   Instead of the first water HP air conditioner (40), a second water HP air conditioner that supplies the air by heat exchange of the return air with the heat source water for air conditioning via the second water heat source heat pump (91) for air conditioning. The heat pump type intermediate temperature air-conditioning system according to claim 1, 2, 4 or 5, comprising (90).   Instead of the first water HP-type external air conditioner (50), the external air conditioning heat source water exchanges only the outside air or the mixed air of the outside air and the return air via the second water heat source heat pump (31) for outside air supply. The heat pump type intermediate temperature air conditioning system according to claim 2, 3 or 4, further comprising a second water HP type external air conditioner (30).   The air-type radiant laminar flow unit (1) is embedded in the ceiling (C) and is exposed to an air supply member (11) that sends out conditioned air supplied from an air conditioner and an air-conditioned space (S). It is embedded in the ceiling (C) and conditioned air of the air supply member (11) is blown into the induction port (10) on the upper surface, so that the air in the air-conditioned space (S) is attracted and mixed. An induction mixing radiation case (16) that discharges downward from a large number of apertures (9) toward the air-conditioned space (S), and the attraction mixing radiation case (16) includes the attraction mixing radiation case (16). The air is split side by side to form a laminar flow and is guided to the air-conditioned space (S) through the opening (9) and the heat of the induced mixed air is stored to store the induced mixed radiation case (16 ) To conduct heat to the air-conditioned space (S) and The heat pump type intermediate temperature air conditioning system according to claim 1, 2, 3, 4, 5, 6 or 7, further comprising a heat storage radiation diverter (2) for radiating heat to the air-conditioned space (S) through the hole (9). .

Images