JP3865955B2 - Compression heat pump - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a compression heat pump, and more particularly to a compression heat pump having an economizer using a heat exchanger.
[0002]
[Prior art]
As shown in FIG. 11, there has conventionally been an air conditioning system combined with a so-called desiccant air conditioner using a heat pump as a heat source. In the air conditioning system of FIG. 11, a compression heat pump HP using a compressor 260 is used as a heat pump. This air conditioning system regenerates the moisture in the desiccant by desorbing the moisture in the desiccant after passing through the desiccant rotor 103 after the moisture adsorbed after being heated by the path of the processing air A in which the moisture is adsorbed by the desiccant rotor 103. A sensible heat exchanger having a path of regenerated air B, between the treated air adsorbed with moisture and the regenerated air before regenerating the desiccant (desiccant) of the desiccant rotor 103 and before being heated by the heating source 104, an air conditioner having 104, and a compression heat pump HP, and using the high heat source of the compression heat pump HP as a heating source, the regeneration air of the air conditioner is heated by the heater 220 to regenerate the desiccant, and the compression heat pump The processing air of the air conditioner is cooled by the cooler 210 using a low heat source as a cooling heat source.
[0003]
In this air conditioning system, the compressed heat pump HP is configured to simultaneously cool the processing air of the desiccant air conditioner and heat the regeneration air, so that the compressed heat pump HP is treated with the processing air by driving heat applied from the outside to the compressed heat pump HP. In addition, the desiccant can be regenerated with the sum of the heat pumped up from the processing air by the heat pump action and the drive heat of the compression heat pump HP, so that multiple drive energy applied from outside can be used. And a high energy saving effect can be obtained. Further, a heat exchanger 121 between the regenerated air between the sensible heat exchanger 104 and the heater 220 and the regenerated air that has exited the desiccant rotor 103 is provided, further enhancing the energy saving effect.
[0004]
Here, the operation of the compression heat pump HP shown in FIG. 11 will be described with reference to the Mollier diagram of FIG. FIG. 12 is a Mollier diagram of the refrigerant HFC134a. Point a indicates the state of the refrigerant evaporated in the cooler 210 and is in a saturated gas state. Pressure is 4.2 kg / cm ² The temperature is 10 ° C. and the enthalpy is 148.83 kcal / kg. A state where the gas is sucked and compressed by the compressor 260 and a state at the discharge port of the compressor 260 are indicated by a point b. In this state, the pressure is 19.3 kg / cm ² The temperature is 78 ° C., and it is in a superheated gas state. This refrigerant gas is cooled in the heater (condenser when viewed from the refrigerant side) 220 and reaches a point c on the Mollier diagram. This point is the state of saturated gas, and the pressure is 19.3 kg / cm. ² The temperature is 65 ° C. Under this pressure, it is further cooled and condensed and reaches point d. This point is the state of saturated liquid, and the pressure and temperature are the same as point c, and the pressure is 19.3 kg / cm. ² The temperature is 65 ° C. and the enthalpy is 122.97 kcal / kg. This refrigerant liquid is decompressed by the expansion valve 270 and is 4.2 kg / cm, which is a saturation pressure at a temperature of 10 ° C. ² The pressure is reduced to 10 ° C. and reaches a cooler (evaporator as viewed from the refrigerant) 210 as a mixture of refrigerant liquid and gas, where heat is taken from the process air and evaporated to a state of point a on the Mollier diagram The saturated gas is then drawn into the compressor 260 again, and the above cycle is repeated.
[0005]
[Problems to be solved by the invention]
According to the conventional heat pump as described above, the enthalpy difference indicating the cooling effect of the refrigerant per unit weight is the difference between the enthalpy of the saturated gas line at the evaporation pressure of the refrigerant and the enthalpy of the saturated liquid line at the condensation pressure, that is, In Example 12, 148.83-122.97 = 25.86 kcal / kg, which is not necessarily large, so the coefficient of performance COP of the compression heat pump HP has to be lowered.
[0006]
Therefore, an object of the present invention is to provide a heat pump having a high COP.
[0007]
[Means for Solving the Problems]
In order to achieve the above object, a heat pump according to a first aspect of the present invention includes a refrigerant compressor 260 for compressing a refrigerant, and heat from a refrigerant compressed by the refrigerant compressor 260 by a high-temperature fluid, as shown in FIG. A first heat exchanger 220 that condenses the refrigerant under a first pressure; a first throttle 230 that depressurizes the refrigerant condensed in the first heat exchanger 220 to a second pressure; The refrigerant decompressed by the first throttle 230 is evaporated by the heat from the first fluid under the pressure of 2, and after the evaporation, the refrigerant is deprived of heat by the second fluid to condense the refrigerant. The second heat exchanger 300; a second throttle 240 for reducing the refrigerant to a third pressure after condensing in the second heat exchanger 300; and applying heat from the cryogenic fluid under the third pressure Then, the refrigerant depressurized by the second throttle 240 is evaporated. And a third heat exchanger 210 configured to.
[0008]
If comprised in this way, since the 2nd heat exchanger which evaporates and condenses a refrigerant under the 2nd pressure decompressed rather than the 1st pressure is provided, the enthalpy difference per unit quantity of a refrigerant can be enlarged.
[0009]
In addition, as described in claim 2, in the heat pump according to claim 1, the second heat exchanger 300 includes the first section 310 that flows the first fluid; and the second fluid flows. A first fluid flow path 251 through which the refrigerant that exchanges heat with the first fluid passes through the first compartment 310; the second fluid through the second compartment 320; A second fluid flow path 252 for flowing the refrigerant that exchanges heat with the fluid of the first fluid; the refrigerant flows from the first fluid flow path 251 to the second fluid flow path 252; The refrigerant evaporates under the second pressure on the channel-side heat transfer surface of the channel 251, and the refrigerant condenses substantially under the second pressure on the channel-side heat transfer surface of the second fluid channel 252. You may comprise as follows. Here, the condensing pressure at the flow path side heat transfer surface of the second fluid flow path 252 is substantially the second pressure because the refrigerant is between the first flow path and the second flow path. This is because there is a flow and there is a slight flow loss. In practice, the evaporation pressure and the condensation pressure are substantially equal.
[0010]
Further, as described in claim 3 and as shown in FIG. 8, in the heat pump according to claim 1 or 2, between the first throttle 360 and the second heat exchanger 300 d, A gas-liquid separator 350 that separates the refrigerant decompressed to the second pressure into a refrigerant liquid and a refrigerant gas may be provided. In this case, since the gas-liquid separator is provided, By reducing the pressure, it is possible to separate the refrigerant gas generated by part of the refrigerant flashing and the remaining liquid.
[0011]
Further, as described in claim 4, in the heat pump according to claim 2, the refrigerant reduced to the second pressure is provided between the first throttle 360 and the second heat exchanger 300. A gas-liquid separator 350 for separating the refrigerant liquid and the refrigerant gas; and a third fluid channel 252D (FIG. 9) provided in parallel with the second fluid channels 252A to 252C; The refrigerant liquid separated in 360 flows into the first fluid channel 251, and the refrigerant gas separated in the gas-liquid separator 360 bypasses the first fluid channel 251, and the third fluid channel It is configured to flow to 252D.
[0012]
With this configuration, since the refrigerant liquid flows through the first fluid flow path and the refrigerant gas hardly flows, the first fluid can be uniformly cooled, and the refrigerant gas flowing through the second fluid flow path The amount of is also uniform. Further, since the refrigerant gas is caused to flow through the third fluid flow path, heat can be uniformly taken away and condensed by the second fluid, and the third fluid can be uniformly heated.
[0013]
Furthermore, as described in claim 5, in the heat pump according to claim 1, the second heat exchanger 300 includes a first section 310 for flowing the first fluid; and a second section for flowing the second fluid. A first fluid flow path 251 that passes through the first compartment 310 and flows the refrigerant that exchanges heat with the first fluid; and a second fluid that passes through the second compartment 320 A second fluid flow path 252 for flowing the refrigerant for heat exchange; the refrigerant flows from the first fluid flow path 251 to the second fluid flow path 252 and the first fluid flow path 251 The refrigerant evaporates under the second pressure on the flow path side heat transfer surface, and the refrigerant condenses substantially under the second pressure on the flow path side heat transfer surface of the second fluid flow path. The first fluid flow path 251 is provided with a plurality of 251A, 251B, and 251C. The second pressure in the fluid flow path may be configured differently, respectively. The second pressures in the plurality of fluid flow paths are configured to be different from each other, and the plurality of fluid flow paths are arranged in the order of the different second pressure levels. Also good.
[0014]
With this configuration, a plurality of first fluid flow paths are provided, and the evaporation pressure and thus the condensation pressure in the plurality of fluid flow paths are configured to be different from each other. If the two fluids are configured to flow in the forward and reverse directions with respect to the plurality of fluid flow paths, the evaporating pressure is arranged from the higher pressure to the lower pressure along the flow of the first fluid on the high temperature side. The condensing pressure is arranged from the lower pressure to the higher pressure along the flow of the second fluid on the lower temperature side than the first fluid. That is, if the plurality of different second pressures is 2 or more, particularly 3 or more, the pressures are arranged in order of height. Therefore, the first fluid and the second fluid can be substantially counterflowed, and the heat exchange efficiency can be increased.
[0015]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings. In addition, in each figure, the same code | symbol or a similar code | symbol is attached | subjected to the mutually same or equivalent member, and the overlapping description is abbreviate | omitted.
[0016]
FIG. 1 is a flowchart of an air conditioning system including a desiccant air conditioner using a compression heat pump HP1 according to a first embodiment of the present invention, and FIG. 2 is a diagram of a second heat exchanger of the present invention used for the compression heat pump HP1. FIG. 3 is a schematic sectional view showing an example, and FIG. 3 is a refrigerant Mollier diagram of the heat pump HP1.
[0017]
First, with reference to FIG. 2, the structure of a heat exchanger suitable for the heat pump HP1 of the present invention will be described. In the figure, the heat exchanger 300 includes a first partition 310 for flowing the processing air A as the first fluid and a second partition 320 for flowing the outside air B as the second fluid. Are provided adjacent to each other.
[0018]
A plurality of heat exchange tubes as fluid flow paths through which the coolant 250 flows through the first compartment 310, the second compartment 320, and the partition wall 301 are provided substantially horizontally. In this heat exchange tube, the portion penetrating the first compartment is an evaporation section 251 as a first fluid flow path (a plurality of evaporation sections are designated as 251A, 251B, and 251C), and the second compartment is The penetrating portion is a condensing section 252 as a second fluid flow path (a plurality of condensing sections are defined as 252A, 252B, and 252C).
[0019]
In the embodiment shown in FIG. 2, the evaporation section 251 </ b> A and the condensation section 252 </ b> A are configured as a single flow path by a single tube. The same applies to the evaporation sections 251B and C and the condensation sections 252B and C. Therefore, coupled with the fact that the first section 310 and the second section 320 are provided adjacent to each other via the single partition wall 301, the heat exchanger 300 can be formed compact and compact as a whole. .
[0020]
In the embodiment of FIG. 2, the evaporation sections are arranged in the order of 251A, 251B, and 251C from the top in the figure, and the condensation sections are arranged in the order of 252A, 252B, and 252C from the top in the figure.
[0021]
On the other hand, the processing air A as the first fluid is configured to enter the first compartment in the drawing through the duct 109 from above and out from below. Further, the outside air B as the second fluid is configured to enter the second compartment in the drawing through the duct 171 from below and flow out from above.
[0022]
Further, a sprinkling pipe 325 is disposed in the second section, above the heat exchange tube constituting the condensation section 252. Nozzles 327 are attached to the sprinkling pipe 325 at appropriate intervals, and are configured to spray water flowing through the sprinkling pipe 325 to heat exchange tubes constituting the condensing section 252.
[0023]
Further, a vaporizing humidifier 165 is installed at the entrance of the second fluid B in the second section. The vaporizing humidifier 165 is made of a hygroscopic and breathable material such as ceramic paper or nonwoven fabric.
[0024]
Here, the evaporating pressure in the evaporating section 251 and thus the condensing pressure in the condensing section 252, that is, the second pressure of the present invention, is determined by the temperature of the processing air A and the temperature of the outside air B. Since the heat exchanger 300 shown in FIG. 2 utilizes evaporation heat transfer and condensation heat transfer, the heat transfer rate is very excellent and the heat exchange efficiency is very high. In addition, since the refrigerant flows from the evaporation section 251 toward the condensation section 252, that is, is forced to flow in almost one direction, the refrigerant flows between the processing air as the first fluid and the outside air as the second fluid. High heat exchange efficiency. Here, the heat exchange efficiency φ is a high temperature when the heat exchanger inlet temperature of the high temperature side fluid is TP1, the outlet temperature is TP2, the heat exchanger inlet temperature of the low temperature side fluid is TC1, and the outlet temperature is TC2. When attention is paid to the cooling of the fluid on the side, that is, when the purpose of heat exchange is cooling, φ = (TP1−TP2) / (TP1−TC1), when attention is paid to heating of the low temperature fluid, ie, the purpose of heat exchange Is heated, it is defined as φ = (TC2−TC1) / (TP1−TC1).
[0025]
It is preferable to form a high-performance heat transfer surface by forming spiral grooves such as linear grooves on the inner surface of the barrel of the rifle on the inner surfaces of the heat exchange tubes constituting the evaporation section 251 and the condensation section 252. The refrigerant liquid flowing inside usually flows so as to wet the inner surface. However, if the spiral groove is formed, the boundary layer of the flow is disturbed, so that the heat transfer rate is increased.
[0026]
In addition, although the processing air flows through the first section, it is preferable that fins attached to the outside of the heat exchange tube are processed into a louver shape so as to disturb the fluid flow.
[0027]
Similarly, when the outside air is allowed to flow through the second compartment but water is not sprayed, the fins are preferably configured to disturb the fluid flow. However, when water is sprayed, it is preferable to further apply a corrosion-resistant coating as flat plate fins. This is to prevent corrosive substances that may be mixed in water from being condensed and concentrated by evaporation to corrode the fins or tubes. The fin is preferably made of aluminum or copper.
[0028]
With reference to FIG. 1, the example of the desiccant air conditioner incorporating heat pump HP1 which is the 1st Embodiment of this invention using the heat exchanger 300 shown in FIG. 2 is demonstrated. FIG. 3 is a Mollier diagram illustrating the refrigerant cycle of the heat pump HP1 according to the first embodiment.
[0029]
In this air conditioning system, the humidity of the processing air is lowered by a desiccant (desiccant), and the air conditioning space to which the processing air is supplied is maintained in a comfortable environment.
[0030]
With reference to FIG. 1, the path | route of the process air as a 1st fluid is demonstrated first. In the figure, air RA to be processed by the blower 102 is taken out from the air-conditioned space 101 through a duct 107 which is a suction path. The discharge port of the blower 102 is connected to the processing air side inlet of the desiccant rotor 103 by a duct 108. The processing air side outlet of the desiccant rotor 103 is connected to the inlet of the first section 310 of the heat exchanger 300 described with reference to FIG.
[0031]
The processed air that has been adsorbed and dried by the desiccant rotor 103 reaches the heat exchanger 300 via the duct 109. When the moisture is adsorbed by the desiccant, the processing air is heated by the heat of adsorption and is heated.
[0032]
In the first compartment 310, the process air is cooled by the refrigerant that evaporates in the evaporation section 251. The processing air outlet of the first section 310 is configured to be guided to the processing air cooler 210 by the duct 110. The processing air that has been dried and cooled to a certain degree is further cooled here, becomes processing air SA having an appropriate humidity and an appropriate temperature, and returns to the conditioned space 101 via the duct 111.
[0033]
Next, the path of the outside air as the second fluid on the second section 320 side of the heat exchanger 300 will be described. A duct 171 for introducing outside air from the outdoor OA is connected to the entrance of the second section 320. The outside air introduced by the duct 171 is humidified by the vaporizing humidifier 165, deprived of sensible heat, and lowered in temperature. When the outside air that has fallen in temperature passes through the second compartment 320, it takes heat away from the refrigerant in the condensing section 252 and condenses it.
[0034]
In addition, water is sprayed to the heat exchange tube 252 through a sprinkling pipe 325, and the temperature of the outside air is also lowered by this, and it is condensed by the sensible heat of the outside air and the evaporation heat of the sprayed water. The refrigerant in section 252 condenses.
[0035]
A duct 172 is connected to the outside air outlet of the second section, and a blower 160 is provided in the middle of the duct 172. The outside air used for condensing the refrigerant passes through the duct 172. , Exhausted to the outdoors as exhaust EX.
[0036]
Next, the refrigerant path of the heat pump HP1 will be described. In the figure, the refrigerant gas compressed by the refrigerant compressor 260 is guided to the regenerative air heater 220 via the refrigerant gas pipe 201 connected to the discharge port of the compressor. The refrigerant gas compressed by the compressor 260 is heated by the compression heat, and the regeneration air (described later) is heated by this heat. The refrigerant gas itself deprives of heat and condenses.
[0037]
The refrigerant outlet of the heater 220 is connected to the inlet of the evaporation section 251 of the heat exchanger 300 by the refrigerant path 202, and a throttle 230 is provided in the vicinity of the inlet of the evaporation section 251 in the refrigerant path 202. .
[0038]
The liquid refrigerant exiting the heater (cooler or condenser as viewed from the refrigerant side) 220 is depressurized by the throttle 230, expands, and part of the liquid refrigerant evaporates (flashes). The refrigerant in which the liquid and gas are mixed reaches the evaporation section 251, where the liquid refrigerant flows and evaporates so as to wet the inner wall of the tube of the evaporation section, thereby cooling the processing air flowing through the first section.
[0039]
Since the evaporating section 251 and the condensing section 252 are a series of tubes, that is, configured as an integral flow path, the evaporated refrigerant gas (and the refrigerant liquid that has not evaporated) flows into the condensing section 252. The heat is taken away and condensed by the outside air and the sprayed water flowing through the second compartment.
[0040]
The outlet side of the condensing section 252 is connected to the cooler 210 by the refrigerant liquid pipe 203. A throttle 240 is provided in the middle of the refrigerant pipe 203. The attachment position of the throttle 240 may be anywhere from immediately after the condensing section 252 to the entrance of the cooler 210, but is preferably as close as possible to the entrance of the cooler 210. This is because the refrigerant after the restriction 240 is considerably lower than the atmospheric temperature, so that the cold insulation of the pipe becomes thick. The refrigerant liquid condensed in the condensing section 252 is depressurized by the restriction 240 and expanded to lower the temperature, enter the cooler 210 and evaporate, and cool the processing air with the heat of evaporation. As the diaphragms 230 and 240, for example, an orifice, a capillary tube, an expansion valve or the like is used.
[0041]
The refrigerant evaporated and gasified by the cooler (evaporator as viewed from the refrigerant side) 210 is led to the suction side of the refrigerant compressor 260 and the above cycle is repeated.
[0042]
Next, the path of regenerating air for regenerating the desiccant will be described. The outside air taken in from outside by the outside air duct 124 is sent to the sensible heat exchanger 121. The sensible heat exchanger is a rotor-shaped heat exchanger, in which a large-volume rotor filled with a heat storage body rotates in a housing divided into two sections, and is taken into one section from the outside. The fresh outside air is configured to flow a fluid that exchanges heat with the outside air in the other compartment.
[0043]
The outside air heated to a certain degree by the sensible heat exchanger 121 reaches the heater 220 through the duct 126, and the outside air heated by the refrigerant gas and further heated here passes through the duct 127 as the regenerative air as the desiccant rotor 103. Introduced on the playback side.
[0044]
Regenerated air that has regenerated the desiccant by the desiccant rotor 103 is guided to the sensible heat exchanger 121 through ducts 128 and 129 that connect the desiccant rotor and the other section of the sensible heat exchanger 121. A blower 140 is provided between the duct 128 and the duct 129, and is used to take in outside air and to flow a regeneration air path.
[0045]
Regenerated air that has exchanged heat with the outside air (heated outside air) in the sensible heat exchanger 121 passes through the duct 130 and is discharged as the exhaust EX.
[0046]
With reference to FIG. 3, the effect | action of heat pump HP1 which is embodiment of this invention in the air conditioning system of FIG. 1 is demonstrated. FIG. 3 is a Mollier diagram when the refrigerant HFC134a is used. In this diagram, the horizontal axis is enthalpy and the vertical axis is pressure.
[0047]
In the figure, point a is the state of the refrigerant outlet of the cooler 210 of FIG. 1 and is in the state of saturated gas. Pressure is 4.2 kg / cm ² The temperature is 10 ° C. and the enthalpy is 148.83 kcal / kg. A state where the gas is sucked and compressed by the compressor 260 and a state at the discharge port of the compressor 260 are indicated by a point b. In this state, the pressure is 19.3 kg / cm ² The temperature is 78 ° C., and it is in a superheated gas state.
[0048]
This refrigerant gas is cooled in the heater (condenser when viewed from the refrigerant side) 220 and reaches a point c on the Mollier diagram. This point is the state of saturated gas, and the pressure is 19.3 kg / cm. ² The temperature is 65 ° C. Under this pressure, it is further cooled and condensed and reaches point d. This point is the state of saturated liquid, and the pressure and temperature are the same as point c, and the pressure is 19.3 kg / cm. ² The temperature is 65 ° C. and the enthalpy is 122.97 kcal / kg.
[0049]
The refrigerant liquid is decompressed by the throttle 230 and flows into the evaporation section 251 of the heat exchanger 300. On the Mollier diagram, it is indicated by a point e. The temperature will be about 30 ° C. The pressure is the second pressure of the present invention, and in the present example, 4.2 kg / cm. ² And 19.3 kg / cm ² And a saturation pressure corresponding to 30 ° C. Here, a part of the liquid is evaporated and the liquid and the gas are mixed. In the evaporation section 251, the refrigerant liquid evaporates under the second pressure, and reaches the point f between the saturated liquid line and the saturated gas line at the same pressure. Here, the liquid has almost evaporated. At point e, the ratio of refrigerant liquid to gas is the inverse ratio of the difference between the enthalpy at the point where the saturated pressure line at 30 ° C. cuts the saturated liquid line and the saturated gas line and the enthalpy at point d. As is apparent from the diagram, liquid is more in weight ratio. However, since gas is overwhelmingly larger in volume ratio, in the evaporating section, the liquid is mixed with a large amount of gas, and the liquid evaporates while being wetted on the inner surface of the tube of the evaporating section.
[0050]
The gas phase refrigerant indicated by the point f or the refrigerant in the mixed state of the gas phase and the liquid phase flows into the condensation section 252. In the condensing section 252, the refrigerant is deprived of heat by the outside air flowing through the second compartment and / or the sprayed water and reaches the point g. This point is on the saturated liquid line in the Mollier diagram. The temperature is 30 ° C. and the enthalpy is 109.99 kcal / kg.
[0051]
The refrigerant liquid at the point g is 4.2 kg / cm, which is a restriction 240 and a saturation pressure of 10 ° C. ² The pressure is reduced to 10 ° C. and reaches a cooler (evaporator as viewed from the refrigerant) 210 as a mixture of refrigerant liquid and gas, where heat is taken from the process air and evaporated to a state of point a on the Mollier diagram The saturated gas is then drawn into the compressor 260 again, and the above cycle is repeated.
[0052]
As described above, in the heat exchanger 300, the refrigerant changes in state from the point e to the point f in the evaporation section 251, and changes in the state from the point f to the point g in the condensation section 252. Heat transfer rate is very high because of heat and condensation heat transfer.
[0053]
Further, as the compression heat pump including the compressor 260, the heater (refrigerant condenser) 220, the throttles 230 and 240, and the cooler (refrigerant evaporator) 210, when the heat exchanger 300 is not provided, the heater (condenser) is provided. ) Since the refrigerant in the state of point d at 220 is returned to the cooler (evaporator) 210 via the throttle, the enthalpy difference that can be used by the cooler (evaporator) is 148.83-122.97 = 25.86 kcal / In the case of the heat pump HP1 according to the embodiment of the present invention in which the heat exchanger 300 is provided, 148.83 to 109.99 = 38.84 kcal / kg, and compression is performed for the same cooling load. The amount of gas circulating to the machine, and thus the required power, can be reduced by 33%. That is, even if the compressor 260 is a single-stage type, it can have the same action as an economizer in which flash gas is sucked into an intermediate stage in a multi-stage type (for example, a two-stage type).
[0054]
Next, with reference to FIG. 4, the example of the desiccant air conditioner incorporating heat pump HP2 which is the 2nd Embodiment of this invention is demonstrated. Except that water is used as the second fluid flowing through the second compartment of the heat exchanger 300b, the configuration and operation are the same as those of the first embodiment. In the figure, the cooling water cooled to about 32 ° C. in the summer in the cooling tower 470 is led to the suction port of the cooling water pump 460 through the cooling water pipe 471 connected to the bottom of the cooling tower 470. Then, it is sent to the second section of the heat exchanger 300b through the cooling water pipe 472 connected to the discharge port.
[0055]
In the second section of the heat exchanger 300b, a baffle plate provided so as to be orthogonal to the heat exchange tube is applied, and the cooling water flows outside the heat exchange tube perpendicular to the tube. A cooling water pipe 473 is connected to the cooling water outlet of the second section, and the cooling water whose temperature has been raised by the heat exchanger 300b is returned to the cooling tower. Thus, in the first embodiment of FIG. 1, the refrigerant is condensed in the condensing section by the outside air, whereas in the second embodiment, the refrigerant is condensed in the condensing section by the cooling water. ing. The refrigerant cycle of the heat pump HP2 is the same as that in FIG.
[0056]
Next, an example of a desiccant air conditioner incorporating a heat pump HP3 according to a third embodiment of the present invention will be described with reference to FIG. A heat exchanger 300c as shown in FIG. 6 is used for the heat pump HP3. The heat exchanger 300c has basically the same structure as the heat exchanger 300 of FIG. 2 except that the watering pipe 325, the nozzle 327, and the vaporizing humidifier 165 for spraying water are not provided.
[0057]
In FIG. 5, the path of the processing air as the first fluid is the same as in FIG. In the heat exchanger 300c for the heat pump HP3 shown in FIG. 5, a restriction such as an orifice is inserted between the header 235 and the evaporation section 251. In the diaphragm, 230A, 230B, and 230C are allocated to the plurality of evaporation sections 251A, 251B, and 251C, respectively. Further, condensing sections 252A, 252B, and 252C corresponding to the respective parts are assigned with diaphragms 240A, 240B, and 240C, respectively, between the headers 245.
[0058]
In such a structure, the processing air A flows orthogonally to the heat exchange tube so as to contact the evaporation sections in the order of 251A, 251B, and 251C in the first section, and performs heat exchange with the refrigerant. The outside air B whose inlet temperature is lower than the processing air flows orthogonally to the heat exchange tube so as to contact the condensing sections in the order of 252C, 252B, and 252A in the second compartment. In such a case, the evaporating pressure (temperature) or the condensing pressure (temperature) of the refrigerant is determined for each section grouped by the throttle, but in the order of 251A, 251B, and 251C in the evaporating section, it decreases from high to low. In the condensing section, the order increases from low to high in the order of 252C, 252B and 252A. If attention is paid to the flow of the processing air A and the outside air B, since it is a so-called counter flow, a remarkably high heat exchange efficiency φ, for example, a heat exchange efficiency φ of 80% or more can be realized.
[0059]
Here, in each of the plurality of evaporation sections 251A, 251B, and 251C, the respective evaporation pressures, which are the second pressures of the present invention, are different as a result of providing independent throttles 230A, 230B, and 230C at the entrances of the respective evaporation sections. A value can be taken and the process air is flowed through the first compartment to contact the evaporation sections 251A, 251B, 251C in this order, and the process air is deprived of sensible heat, resulting in a temperature drop from the inlet to the outlet. To do. As a result, the evaporation pressure in the evaporation sections 251A, 251B, and 251C decreases in this order, and the evaporation temperatures are arranged in order.
[0060]
Exactly the condensing temperature ranges from low to high in the order of sections 252C, 252B, 252A, but like the evaporation section, each condensing section is provided with an independent restriction 240A, 240B, 240C resulting in an independent condensing pressure or The condensation pressure can be arranged in this order as a result of allowing the outside air to flow in contact with the condensation sections 252C, 252B, 252A in this order from the entrance to the exit of the second compartment. Become. Therefore, when attention is paid to the processing air A and the outside air B, as described above, a so-called counterflow type heat exchanger is formed, and high heat exchange efficiency can be achieved.
[0061]
In FIG. 6, the first compartment and the second compartment are provided adjacent to each other via a partition plate 301, and the evaporation section and the condensation section are formed by an integral continuous heat exchange tube. As another form (not shown), a heat exchanger in which the first section and the second section are separated and the first flow path and the second flow path are also separated may be used. In other words, the evaporating sections 251A, 251B, and 251C are connected to the condensing sections 252A, 252B, and 252C through appropriate headers and connecting pipes, respectively. Also in this case, the performance as a basic heat exchanger is not different from the case of FIG.
[0062]
In the embodiment of FIG. 5, the outside air as the second fluid is used as desiccant regeneration air. In the drawing, a duct 124 for introducing outside air from the outdoor OA is connected to the entrance of the second section 320. The outside air introduced by the duct 124 is introduced into the second compartment 320 and, when passing through it, takes heat from the refrigerant in the condensing section 252 and condenses it. Here, the condensing section 252 includes sections 252C, 252B, and 252A, and the condensing temperatures are arranged from low to high in this order. Thus, outside air will exit the second compartment 320 after contacting the hottest condensation section 252A. The outlet of the second compartment is connected to the heater 220 by a duct 126, and the outside air heated to some extent in the second compartment 320 is introduced into the heater 220, where it is further heated and heated as regenerated air. The desiccant rotor 103 is reached via a duct 127 connecting the vessel 220 and the desiccant rotor 103.
[0063]
In this way, the regeneration air introduced into the desiccant rotor 103 is exhausted from the desiccant rotor 103 through ducts 128 and 129 that communicate with the outside air after heating and regeneration of the desiccant. A blower 140 is provided between the duct 128 and the duct 129, and is used to take in outside air and to flow a regeneration air path.
[0064]
Next, the refrigerant path will be described. In the figure, the refrigerant gas compressed by the refrigerant compressor 260 is led to a regenerative air heater (condenser as viewed from the refrigerant) 220 via a refrigerant gas pipe 201 connected to the discharge port of the compressor. The refrigerant gas compressed by the compressor 260 is heated by the compression heat, and the regeneration air is heated by this heat. The refrigerant gas itself deprives of heat and condenses.
[0065]
A refrigerant pipe 202 is connected to the refrigerant outlet of the heater 220, and further reaches the header 235, where it is divided into a plurality of (three in FIG. 5) refrigerant systems, each having a different throttle 230A, 230B. , 230C. The diaphragms 230A, 230B, and 230C are connected to the evaporation sections 251A, 251B, and 251C shown in FIG. 6, respectively. Accordingly, each of the evaporation sections 251A, 251B, and 251C is configured to be able to evaporate at different evaporation pressures and thus at different evaporation temperatures. The apertures 230A, 230B, and 230C are provided in the vicinity of the entrances of the evaporation sections 251A, 251B, and 251C. An orifice, an expansion valve, a capillary tube or the like is used as the throttle.
[0066]
The liquid refrigerant exiting the heater (refrigerant condenser) 220 is depressurized by the throttles 230A, 230B, and 230C, and expands to partially evaporate (flash). The refrigerant in which the liquid and gas are mixed reaches each of the evaporation sections 251A, 251B, and 251C, where the liquid refrigerant flows and evaporates so as to wet the inner wall of the tube of the evaporation section, and flows through the first compartment. Cool down.
[0067]
Since each evaporation section 251A, 251B, 251C and each condensation section 252A, 252B, 252C are a series of tubes, the evaporated refrigerant gas (and the refrigerant liquid that has not evaporated) is transferred to the condensation sections 252A, 252B, 252C. It flows in and is deprived of heat and condensed by outside air flowing through the second compartment.
[0068]
On the outlet side of each condensing section 252A, 252B, 252C, throttles 240A, 240B, 240C are provided, respectively. A header 245 is provided at the end, and a refrigerant pipe 203 is connected to the header 245 so that the liquid refrigerant is guided to the cooler 210.
[0069]
In such a configuration, the refrigerant liquid condensed in the condensing sections 252A, 252B, and 252C is decompressed and expanded by the restrictors 240A, 240B, and 240C to lower the temperature, and merges at the header 245 and then enters the cooler 210. Evaporate and cool the process air with the heat of evaporation.
[0070]
The refrigerant evaporated and gasified by the cooler (refrigerant evaporator) 210 is guided to the suction side of the refrigerant compressor 260, and the above cycle is repeated.
[0071]
With reference to FIG. 7, the refrigerant | coolant flow and effect | action of heat pump HP3 which are 3rd Embodiment in the air conditioner of FIG. 5 are demonstrated. FIG. 7 is a Mollier diagram when the refrigerant HFC134a similar to that in FIG. 3 is used.
[0072]
In the figure, point a is the state of the refrigerant outlet of the cooler 210 of FIG. 7, which is a saturated gas state. Pressure is 4.2 kg / cm ² The temperature is 10 ° C. and the enthalpy is 148.83 kcal / kg. A state where the gas is sucked and compressed by the compressor 260 and a state at the discharge port of the compressor 260 are indicated by a point b. In this state, the pressure is 19.3 kg / cm ² The temperature is 78 ° C.
[0073]
The refrigerant gas is cooled in the heater (refrigerant condenser) 220 and reaches a point c on the Mollier diagram. This point is the state of saturated gas, and the pressure is 19.3 kg / cm. ² The temperature is 65 ° C. Under this pressure, it is further cooled and condensed and reaches point d. This point is the state of saturated liquid, and the pressure and temperature are the same as point c, and the pressure is 19.3 kg / cm. ² The temperature is 65 ° C. and the enthalpy is 122.97 kcal / kg.
[0074]
Of the refrigerant liquid, the state of the refrigerant reduced in pressure by the diaphragm 230A and flowing into the evaporation section 251A is indicated by a point e1 on the Mollier diagram. The temperature will be about 43 ° C. The pressure is one of different second pressures of the present invention, and is a saturation pressure corresponding to a temperature of 43 ° C. Similarly, the state of the refrigerant reduced in pressure by the throttle 230B and flowing into the evaporation section 251B is indicated by a point e2 on the Mollier diagram, the temperature is 40 ° C., and the pressure is a second pressure different from that of the present invention. Another one is a saturation pressure corresponding to a temperature of 40 ° C. Similarly, the state of the refrigerant depressurized by the throttle 230C and flowing into the evaporation section 251C is indicated by a point e3 on the Mollier diagram, the temperature is 37 ° C., and the pressure is the second pressure different from the present invention. Another one is a saturation pressure corresponding to a temperature of 37 ° C.
[0075]
At any of the points e1, e2, and e3, the refrigerant is in a state where a part of the liquid is evaporated and the liquid and the gas are mixed. In each evaporating section, the refrigerant liquid evaporates under the second pressure and reaches intermediate points f1, f2, and f3 between the saturated liquid line and the saturated gas line at each pressure, respectively.
[0076]
The refrigerant in this state flows into each condensing section 252A, 252B, 252C. In each condensing section, the refrigerant is deprived of heat by the outside air flowing through the second compartment and reaches points g1, g2, and g3, respectively. These points are on the saturated liquid line in the Mollier diagram. The temperatures are 43 ° C., 40 ° C., and 37 ° C., respectively. These refrigerant liquids reach the points j1, j2, and j3 through the throttles, respectively. The pressure at these points is 4.2 kg / cm at a saturation pressure of 10 ° C. ² It is.
[0077]
Here, the refrigerant is in a state where liquid and gas are mixed. These refrigerants merge into one header 245, and the enthalpy here is an average value obtained by weighting the points g1, g2, and g3 with the flow rates of the corresponding refrigerants. In this example, about 113.51 is obtained. It is. The reason why the enthalpy is higher than that in the case of FIG. 3 in spite of the three stages is that water is not sprayed in the second section.
[0078]
This refrigerant takes heat from the processing air in the cooler (refrigerant evaporator) 210, evaporates to become a saturated gas in the state of point a on the Mollier diagram, is again sucked into the compressor 260, and the above cycle is repeated. .
[0079]
As described above, in the heat exchanger 300c, the refrigerant evaporates in each evaporating section and condenses in each condensing section. Since it is evaporative heat transfer and condensing heat transfer, the heat transfer rate is very high. . Moreover, in the first section, the process air cooled from the high temperature to the low temperature as it flows from the top to the bottom in the figure is cooled at the temperatures arranged in order of 43 ° C., 40 ° C., and 37 ° C., respectively. Compared with the case of cooling at one temperature, for example, 40 ° C., the heat exchange efficiency can be increased. The condensing section is similar. That is, in the second section, the outside air (regeneration air) heated from the low temperature to the high temperature as it flows from the bottom to the top in the figure is heated at the temperatures arranged in order of 37 ° C., 40 ° C., and 43 ° C., respectively. Therefore, the heat exchange efficiency can be increased as compared with the case of heating at one temperature, for example, 40 ° C.
[0080]
Further, as the compression heat pump HP3 including the compressor 260, the heater (refrigerant condenser) 220, the throttle and the cooler (refrigerant evaporator) 210, when the heat exchanger 300c is not provided, the heater (condenser) 220 is provided. Since the refrigerant in the state of point d is returned to the cooler (evaporator) 210 through the throttle, the enthalpy difference that can be used in the cooler (evaporator) is only 25.86 kcal / kg. In the case of the embodiment of the present invention provided with the vessel 300b, 148.83-113.51 = 35.32 kcal / kg, and the amount of gas circulating to the compressor with respect to the same cooling load, and thus the required power, is 27. % Can also be reduced. That is, even if the compressor 260 is a single-stage type, it is possible to provide the same operation as in the case of having a plurality of types of economizers that suck flash gas into the intermediate stage. It is the same as the form.
[0081]
With reference to FIG. 8, the example of the desiccant air conditioner incorporating heat pump HP4 which is the 4th Embodiment of this invention is demonstrated. FIG. 9 is a heat exchanger 300d suitable for use in the heat pump HP4, and FIG. 10 is a Mollier diagram for explaining the refrigerant cycle of the heat pump HP4 according to the fourth embodiment.
[0082]
The processing air path and the regeneration air path are the same as those in the air conditioner of the embodiment of FIG.
[0083]
Here, the refrigerant path of the heat pump HP4 will be described. In the figure, the refrigerant gas compressed by the refrigerant compressor 260 is guided to the regenerative air heater 220 via the refrigerant gas pipe 201 connected to the discharge port of the compressor. The refrigerant gas compressed by the compressor 260 is heated by the compression heat, and the regeneration air (described later) is heated by this heat. The refrigerant gas itself deprives of heat and condenses.
[0084]
The refrigerant outlet of the heater 220 is connected to the inlets of the evaporation sections 251A, B, and C of the heat exchanger 300d by the refrigerant path 202. A throttle 360 such as an expansion valve is provided in the middle of the refrigerant path 202. A gas-liquid separator 350 is provided between the throttle 360 and the evaporation sections 251A, B, and C. The configuration of the heat exchanger 300d will be described in detail later with reference to FIG.
[0085]
The liquid refrigerant exiting the heater (cooler or condenser as viewed from the refrigerant side) 220 is decompressed by an expansion valve 360 as a first throttle, and expands to partially evaporate (flash). The refrigerant mixed with the liquid and gas is separated into the refrigerant liquid and the refrigerant gas by the gas-liquid separator 350, the refrigerant liquid reaches the evaporation sections 251A, B, and C, and the refrigerant evaporates in the tube of the evaporation section. Then, the processing air flowing through the first compartment is cooled.
[0086]
Since the evaporating section 251 and the condensing section 252 are a series of tubes, that is, configured as an integral flow path, the evaporated refrigerant gas (and the refrigerant liquid that has not evaporated) flows into the condensing section 252. The heat is taken away and condensed by the outside air and the sprayed water flowing through the second compartment.
[0087]
The outlet side of the condensing section 252 is connected to the expansion valve 270 as the second throttle by the refrigerant liquid pipe 203 and further to the cooler 210 by the refrigerant pipe 204. The refrigerant liquid condensed in the condensing section 252 is decompressed and expanded by the restriction 270 to lower the temperature, enters the cooler 210 and evaporates, and cools the processing air with the heat of evaporation. The restrictors 360 and 270 may be expansion valves, for example, orifices and capillary tubes.
[0088]
The refrigerant evaporated and gasified by the cooler (evaporator as viewed from the refrigerant side) 210 is led to the suction side of the refrigerant compressor 260 and the above cycle is repeated.
[0089]
The gas-liquid separator 350 includes a container into which a mixture of gas and liquid flows, and a baffle plate 355 disposed in the container so as to face the inlet of the gas-liquid mixture. The gas-liquid mixture collides with the baffle plate 355 and the liquid is separated from the gas. The gas flows out from the gas outlet provided alongside the gas-liquid mixture inlet of the container and is connected to the gas outlet. The refrigerant flows through the refrigerant pipe 340 to the heat exchanger 300d. The refrigerant liquid flows out from a liquid outlet provided in the vertical direction below the container of the gas-liquid separator. Refrigerant pipes 450A, 450B, and 450C are connected to the liquid outlet and communicate with the evaporation sections 251A, B, and C, respectively.
[0090]
With reference to FIG. 9, the structure of the heat exchanger 300d as a 2nd heat exchanger suitable for using for the heat pump of 4th Embodiment is demonstrated. In the figure, in the heat exchanger 300d, a first partition 310 that flows the processing air A that is the first fluid and a second partition 320 that flows the outside air B that is the second fluid are one partition wall 301. It is the same as that of the heat exchanger shown in FIG.
[0091]
The arrangement of the evaporation sections 251A, B and C, the arrangement of the condensation sections 252A, B and C, the watering pipe 325, the vaporizing humidifier 165, the processing air paths 109 and 110, and the outside air path 171 are also shown in FIG. It is the same.
[0092]
Headers 450A, B, and C are connected to the evaporation sections 251A, B, and C, and refrigerant pipes 430A, 430B, and 430C are connected to the headers 450A, B, and C, respectively. Each of the evaporation sections 251A, B, and C is configured to include one or more, typically a plurality (six in the example of FIG. 9) heat exchange tubes, and the plurality of heat exchange tubes. Are summarized in each header 450A, B, C.
[0093]
The refrigerant gas pipe 340 passes through the first section 310 of the heat exchanger 300d through the tube 341. The tube 341 passes through the partition wall 301 and is disposed through the second section 320. In the example of FIG. 9, two tubes 341 are arranged in parallel, and each of the tubes 341 is constituted by three passes through the second section 320. Here, as in the condensation sections 252A, B, and C, the portion in the second section 320 of the tube 341 has a structure in which fins are attached to the outside of the tube to promote heat exchange. This portion is called a condensation section 252D. The condensing section 252D is disposed between the condensing section 252C and the vaporizing humidifier 165 on the upstream side of the outside air flow of the condensing section 252C. In the condensing section 252D, the refrigerant gas is deprived of heat by the outside air that is the second fluid and condenses. Note that the condensing section 252D may be disposed on the downstream side of the outside of the condensing section 252A.
[0094]
Since the tube 341 hardly contributes to heat exchange in the first section, it effectively bypasses the first section 310. Thus, the first compartment 310 may actually be bypassed structurally, i.e., through the exterior of the first compartment 310 and connected to the condensing section 252D in the second compartment.
[0095]
Headers 455A, B, and C are provided on the refrigerant liquid outlet sides of the condensing sections 252A, B, and C, respectively, and the condensing sections 252A, B, and C each configured by a plurality of tubes are collected. The piping from each header is further combined into one header 370 (FIG. 8), and the header 370 is connected to the expansion valve 270 by the refrigerant piping 203 as described above. The refrigerant liquid from the condensing section 252D is guided by the refrigerant pipe 345 connected to the condensing section 252D, and joins the path 203 on the downstream side of the header 370. Note that the pipe 345 may be connected to the header 370.
[0096]
With reference to the Mollier diagram of FIG. 10, the effect | action of heat pump HP4 which is embodiment of this invention in the air conditioning system of FIG. 8 is demonstrated. FIG. 10 is a Mollier diagram when the refrigerant HFC134a is used. In this diagram, the horizontal axis is enthalpy and the vertical axis is pressure.
[0097]
In the figure, point a is the same as point B, point c, and point d in the Mollier diagram of FIG. The refrigerant liquid at the point d is decompressed by the throttle 360 and flows into the gas-liquid separator 350. Here, the separated refrigerant gas passes through the pipe 340 as a gas in the state of the intersection h between the isobaric line of saturated pressure corresponding to 40 ° C. and the saturated gas line, which is the second pressure of the present invention. It flows into tube 341 and into condensing section 252D. Here, the outside air (outside air cooled with water from the vaporizing humidifier and sprinkling pipe) takes heat and condenses, reaches the saturated liquid line, and is typically supercooled, and exceeds the saturated liquid line. The point i of the cooling liquid phase is reached.
[0098]
The liquid separated by the gas-liquid separator 350 is a liquid at a point g on the saturated liquid line. The liquid at the point i and the liquid at the point g are mixed by the header 370 and depressurized by the expansion valve 270, and the pressure is 4.2 kg / cm. ² Then, it becomes a refrigerant (a mixture of gas and liquid) having a temperature of 10 ° C.
[0099]
As described above, in the present embodiment, there is almost no gas phase component contained in the refrigerant guided to the heat exchange tubes (heat transfer tubes) constituting the evaporation sections 251A, B, and C of the second heat exchanger. Therefore, the amount of refrigerant guided to the evaporation sections 251A, B, C is uniform, so that the cooling of the first fluid by evaporation in the evaporation sections 251A, B, C is uniform, and the condensation sections 252A, B, C The amount of refrigerant condensed in the heat transfer tube is occupied by the refrigerant evaporated at 251A, B, and C in the evaporation section. When the gas phase is included, the heat is not uniform, especially in the condensing section containing a large amount of the gas phase. However, such a problem does not occur if only the liquid layer is used.
[0100]
In this way, the amount of heat transferred by the heat pipe action of each heat transfer pipe (phase change of the refrigerant, particularly heat transfer action due to evaporation and condensation) is made uniform between the heat transfer pipes. Uniform heat transfer is possible, and the inconvenience that air as the first fluid and the second fluid passes without being involved in heat transfer can be prevented. Therefore, in the dehumidifying air-conditioning apparatus according to the embodiment, the heat exchange efficiency between the processing air as the first fluid and the cooling medium (outside air) or the regeneration air as the second fluid is improved and the operation reliability is improved. Can be planned.
[0101]
Hereinafter, examples of the present invention will be described using specific numerical values. As calculation conditions, the heat transfer amount is 2 USRt, the evaporation temperature is 10 ° C., the economizer temperature is 40 ° C., the condensation temperature is 65 ° C., the refrigerant is HFC134a, and the pipe diameter is 12 mm. Further, the inner diameter of the heat transfer tube is 8.3 mm, and the number of heat transfer tubes is 40 (in the case of a three-stage arrangement as shown in FIG. 9, for example, 13, 14, 13, 13 are arranged in a staggered arrangement in each stage). . Here, when the enthalpy of each point is read and calculated with reference to the Mollier diagram of FIG. / S.
[0102]
Comparative example:
The gas-liquid two-phase refrigerant after being expanded by the expansion valve is branched into a large number of heat transfer tubes configured in one path of the heat exchanger using a distributor. In the second heat exchanger, the number of branches is large because the heat transfer tubes must be arranged in one path.
[0103]
Dryness immediately after the expansion valve: (122.97-113.51) /39.42=0.242 (39.42 is the enthalpy difference between point h and point g in FIG. 10)
Specific volume of the two-phase mixed refrigerant immediately after the expansion valve: 0.00087261 × (1−0.242) + 0.020032 × 0.242) = 0.551m ^Three / Kg
Flow velocity 1 (in three pipes with an inner diameter of 12 mm): 0.00551 × 0.0476 × 4 / (0.012 × 0.012 × 3.14 × 3) = 0.773 m / s
Flow velocity 2 (in 40 heat transfer tubes with an inner diameter of 8.3): 0.00551 × 0.0476 × 4 / (0.0083 × 0.0083 × 3.14 × 40) = 0.121 m / s
At a flow rate of 1, the refrigerant flows in the pipe almost uniformly through gas-liquid mixing. However, at the flow rate of 2 that branches to the heat transfer tube, the flow rate is too slow, so the refrigerant flows in a state where the gas-liquid two phases are separated by gravity. The gas phase flows upward and the liquid phase flows downward. Thus, since the flow velocity after branching becomes extremely slow, it is difficult to distribute the vapor-phase refrigerant in a state of being uniformly mixed with the liquid-phase refrigerant. As a result, the refrigerant cannot be uniformly distributed because the flow is different before and after branching.
[0104]
Example:
Dryness immediately after expansion valve: 0
Specific volume of liquid refrigerant immediately after expansion valve: 0.00087261m ^Three / Kg
Flow velocity 3 (in three pipes with an inner diameter of 12 mm): 0.00087261 × 0.0476 (1−0.242) × 4 / (0.012 × 0.012 × 3.14 × 3) = 0.0928 m / s
Flow velocity 4 (in 40 heat transfer tubes with an inner diameter of 8.3): 0.00087261 × 0.0476 (1−0.242) × 4 / (0.0083 × 0.0083 × 3.14 × 40) = 0 .0146 m / s
As described above, since both the flow velocity 3 and the flow velocity 4 are slow and only the liquid phase flows, it can be uniformly distributed to the heat transfer tubes.
[0105]
As described above, in the fourth embodiment, the second fluid has been described using the vaporizing humidifier and the watering pipe and using the outside air whose temperature has been lowered by the heat of vaporization of water, but not only in such a case. As in the third embodiment shown in FIG. 5, the regeneration air can be heated in the second section.
[0106]
【The invention's effect】
As described above, according to the present invention, since the second heat exchanger that evaporates and condenses the refrigerant under the second pressure that is lower than the first pressure is provided, the enthalpy difference per unit amount of the refrigerant Therefore, it is possible to provide a heat pump with significantly improved COP.
[0107]
Therefore, when the heat pump of the present invention is used as a heat source of a desiccant air conditioner, for example, the efficiency of the desiccant air conditioner can be remarkably increased.
[0108]
When the second heat exchanger is provided with a gas-liquid separator, the refrigerant gas and the refrigerant liquid are separated, so that the heat exchange in the second heat exchanger becomes uniform.
[Brief description of the drawings]
FIG. 1 is a flowchart of a desiccant air conditioning system using a heat pump according to a first embodiment of the present invention.
FIG. 2 is a schematic cross-sectional view of a heat exchanger suitable for use in the heat pump shown in FIG.
FIG. 3 is a Mollier diagram of the heat pump shown in FIG. 1;
FIG. 4 is a flowchart of a desiccant air conditioning system using a heat pump according to a second embodiment of the present invention.
FIG. 5 is a flowchart of a desiccant air conditioning system using a heat pump according to a third embodiment of the present invention.
6 is a schematic cross-sectional view of a heat exchanger suitable for use in the heat pump shown in FIG.
FIG. 7 is a Mollier diagram of the heat pump shown in FIG.
FIG. 8 is a flowchart of a desiccant air conditioning system using a heat pump according to a fourth embodiment of the present invention.
9 is a schematic cross-sectional view of a heat exchanger suitable for use in the heat pump shown in FIG.
10 is a Mollier diagram of the heat pump shown in FIG. 8. FIG.
FIG. 11 is a flowchart of a desiccant air conditioning system using a conventional heat pump.
12 is a Mollier diagram of the heat pump shown in FIG. 11. FIG.
[Explanation of symbols]
165 Vaporizing humidifier
251 Evaporation section
252 Condensation section
230A, 230B, 230C
240A, 240B, 240C Aperture
300, 300b, 300c heat exchanger
310 First compartment
320 Second compartment
325 Watering pipe
HP, HP1, HP2, HP3 heat pump

Claims (5)

A refrigerant compressor for compressing the refrigerant;
A first heat exchanger that draws heat from the refrigerant compressed by the refrigerant compressor by a high-temperature fluid and condenses the refrigerant under a first pressure;
A first throttle for reducing the refrigerant condensed in the first heat exchanger to a second pressure;
Under the second pressure, the refrigerant decompressed by the first throttle is evaporated by the heat from the first fluid, and after the evaporation, the refrigerant is deprived of heat by the second fluid and condensed. A second heat exchanger to cause;
A second throttle that depressurizes the refrigerant to a third pressure after condensing in the second heat exchanger;
A third heat exchanger configured to evaporate the refrigerant depressurized by the second throttle by applying heat from a cryogenic fluid under the third pressure;
heat pump. The second heat exchanger is
A first compartment for flowing said first fluid;
A second compartment for flowing said second fluid;
A first fluid flow path through which the refrigerant that passes through the first compartment and exchanges heat with the first fluid flows;
A second fluid flow path that passes through the second compartment and flows the refrigerant that exchanges heat with the second fluid;
The refrigerant flows from the first fluid flow path through the second fluid flow path, and the refrigerant evaporates under the second pressure on the flow side heat transfer surface of the first fluid flow path. And the refrigerant is configured to condense substantially under the second pressure on the flow path side heat transfer surface of the second fluid flow path;
The heat pump according to claim 1. The gas-liquid separator which isolate | separates the said refrigerant | coolant decompressed to the front 2nd pressure into a refrigerant | coolant liquid and a refrigerant gas between the said 1st aperture_diaphragm | restriction and the said 2nd heat exchanger is characterized by the above-mentioned. Item 3. The heat pump according to item 1 or 2. A gas-liquid separator between the first throttle and the second heat exchanger that separates the refrigerant, which has been reduced to the second pressure before, into refrigerant liquid and refrigerant gas;
A third fluid channel provided in parallel with the second fluid channel;
The refrigerant liquid separated by the gas-liquid separator flows into the first fluid flow path, and the refrigerant gas separated by the machine liquid separator bypasses the first fluid flow path, and Configured to flow through three fluid flow paths;
The heat pump according to claim 2. The second heat exchanger is
A first compartment for flowing said first fluid;
A second compartment for flowing said second fluid;
A first fluid flow path through which the refrigerant that passes through the first compartment and exchanges heat with the first fluid flows;
A second fluid flow path that passes through the second compartment and flows the refrigerant that exchanges heat with the second fluid;
The refrigerant flows from the first fluid flow path through the second fluid flow path, and the refrigerant evaporates under the second pressure on the flow side heat transfer surface of the first fluid flow path. And the refrigerant is configured to condense substantially under the second pressure on the channel-side heat transfer surface of the second fluid channel;
A plurality of the first fluid flow paths are provided, and the second pressures in the plurality of fluid flow paths are configured to be different from each other;
The heat pump according to claim 1.

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