JP2007285550A - Storage type heat exchanger and air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To efficiently exchange heat among a heat carrying-in medium, a heat storage material and a heat carrying-out medium. <P>SOLUTION: This storage type heat exchanger 1 comprising the heat storage material 2, the heat carrying-in medium 4 exchanging heat with the heat storage material 2, and the heat carrying-out medium 6 exchanging heat with the heat storage material 2 and the heat carrying-in medium 4, comprises a first indirect heat exchanging portion 8 where the heat carrying-in medium 4 and the heat carrying-out medium 6 exchange heat through the heat storage material 2, and a first direct heat exchanging portion 9 where the heat carrying-in medium 4 and the heat carrying-out medium 6 exchange heat through a partitioning wall 10 defining flow channels of the mediums 4, 6, and the heat carrying-in medium 4 and the heat carrying-out medium 6 flow toward the first indirect heat exchanging portion 8 toward the first direct heat exchanging portion 9 respectively in the flow channels 5, 7. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a heat storage type heat exchanger that performs heat exchange between a heat carrying medium such as a refrigerant and a heat storage medium (including a cold storage material) and a heat carrying medium such as brine, and an air conditioner using the heat exchanger. It is about the system.

  As is well known, a compression heat pump is mounted on a vehicle. The power source of the heat pump is an internal combustion engine or a motor that also serves as a power source for traveling. Therefore, when a large driving force is required for driving the vehicle, the power that can be used by the heat pump is In contrast, when the power required for traveling is small, so-called surplus power that can be used for a heat pump or the like increases. Since such fluctuations in power and power required for the heat pump do not always match, it is preferable to store heat or cool stored heat obtained by driving the heat pump.

  In this way, surplus power generated in the power source can be recovered in the form of heat storage or cold storage, and if the driving force of the heat pump required for cooling or heating is insufficient, Cooling or heating can be performed using the thermal energy stored in the material. Moreover, when comprised in this way, since the heat | fever discharge | released outside from the condenser in a refrigerating cycle can be collect | recovered, energy efficiency can be improved and by extension, the fuel consumption of a vehicle can be improved.

  When performing heat storage as described above (hereinafter referred to as heat storage including cold storage), in order to simplify the overall configuration, heat is transferred between the heat carry-in medium and the heat carry-out medium together with the heat storage function. It is preferable to use a heat storage type heat exchanger having a function of performing exchange. A heat exchanger having such a function is described in Patent Document 1. The heat exchanger described in Patent Document 1 forms a first flow path for flowing a heat source fluid and a second flow path for flowing a heat recovery fluid in close contact via a partition wall that divides both, These two integrated flow paths are penetrated into the heat storage material, and heat is transferred from the heat source fluid to the heat recovery fluid in the entire flow path of the first flow path inside the heat storage material, and at the same time, from the heat source fluid to the heat storage material. It is configured to transfer heat to.

JP 2003-336974 A

  In the heat exchanger described in Patent Document 1 described above, the heat source fluid directly exchanges heat with the heat recovery medium and with the heat storage material in the entire region flowing through the heat storage material. Yes. For this reason, even when heat storage is preferentially performed due to the heat recovery fluid being stopped, excessive heat is transferred to the heat recovery medium in contact with the partition wall, There is a possibility that the amount of heat storage is reduced or the heat storage efficiency is lowered. In addition, when the heat recovery fluid receives heat from the heat storage material and performs cooling or heating with a small amount of so-called heat input such as the heat source fluid not being able to flow sufficiently, the heat recovery fluid generates heat from the heat storage material. The so-called heat receiving area to be received is small, and there is a possibility that the efficiency of cooling or heating will be reduced by using the heat storage efficiency as a heat source.

  The present invention has been made paying attention to the above-mentioned problems, and can efficiently input heat to the heat storage material and release heat from the heat storage material, and can efficiently perform between the heat carry-in medium and the heat carry-out medium. It is an object of the present invention to provide a heat storage type heat exchanger capable of exchanging heat well and an air conditioning system using the heat storage type heat exchanger.

  In order to achieve the above object, the invention of claim 1 includes a heat storage material, a heat carry-in medium that exchanges heat with the heat storage material, and a heat carry-out medium that exchanges heat between the heat storage material and the heat carry-in medium. In the heat storage type heat exchanger comprising: a first indirect heat exchange unit in which the heat carry-in medium and the heat carry-out medium exchange heat via the heat storage material, the heat carry-in medium, and the heat carry-out medium A first direct heat exchange unit that exchanges heat through a partition wall that forms a flow path for each medium, and the heat carry-in medium and the heat carry-out medium exchange the respective flow paths with the first indirect heat exchange. It is comprised so that it may flow toward a 1st direct heat exchange part from a part.

  According to a second aspect of the present invention, in the first aspect of the invention, the heat carry-in medium downstream from the first direct heat exchange section and the heat carry-out medium upstream from the first direct heat exchange section are interposed via the heat storage material. A second indirect heat exchanging part that exchanges heat, the heat carry-in medium downstream from the second indirect heat exchange part, and the heat carry-out medium downstream from the second heat exchange part form respective flow paths. And a second direct heat exchange section that exchanges heat through the partition wall.

  The invention of claim 3 is compressed / expanded by a first circulation passage for circulating and flowing the heat carrying-out medium in the heat storage type heat exchanger according to claim 1 or 2 to the indoor heat exchanger, and a refrigeration cycle. An air conditioning system comprising: a second circulation channel that circulates and flows a refrigerant in the heat storage type heat exchange as the heat carrying medium.

  The invention of claim 4 is the invention of claim 3, which is formed by branching from the first circulation flow path, and the heat carrying-out medium is repeated inside the heat storage material without passing through the indoor heat exchanger. An air conditioning system comprising: a third circulation channel for circulation; and a switching valve for switching the heat carrying medium to the first circulation channel and the third circulation channel.

  According to a fifth aspect of the present invention, in the fourth aspect of the present invention, the reservoir for temporarily storing the heat carrying-out medium is provided in a portion of the flow path common to the first circulation flow path and the third circulation flow path. It is an air conditioning system characterized by that.

  A sixth aspect of the present invention is the air conditioning system according to any one of the third to fifth aspects, which is mounted on a vehicle.

  According to the first aspect of the present invention, the heat carrying medium initially has a sufficient amount of heat (including the amount of cold heat; the same shall apply hereinafter) when it flows into the heat storage material. In this case, heat is exchanged between the heat storage materials, and heat is also exchanged with the heat transfer medium via the heat storage materials. Therefore, heat can be sufficiently transmitted to the heat storage material and stored. Further, in the first direct heat exchange section on the downstream side of the heat carry-in medium, the heat carry-in medium that has released some amount of heat and the heat carry-out medium that has received some heat amount partition each flow path. To exchange heat. In that case, since the heat storage material does not intervene, the heat transfer amount or heat transfer efficiency between the respective media can be improved. As a result, the heat that the heat carrying medium has can be sufficiently stored in the heat storage material, and the heat can be efficiently transferred to the heat carrying medium. In addition, even when the heat carry-out medium has stopped carrying out heat, heat can be sufficiently transferred to the heat storage material in the first indirect heat exchange section, so that the amount of heat taken away by the heat carry-in medium can be reduced, and heat storage Efficiency can be made favorable.

  According to the invention of claim 2, the indirect heat exchange described above is performed on the upstream side and the downstream side in the heat storage material of the heat carrying-in medium, in other words, on the downstream side and the upstream side in the heat storage material of the heat carrying-out medium. Since a pair of direct heat exchange units are provided, heat exchange efficiency and heat storage efficiency between the heat carry-in medium and the heat carry-out medium can be improved.

  According to invention of Claim 3, while being able to store efficiently the heat and / or cold heat which generate | occur | produce in a refrigerating cycle, cooling and / or heating can be performed efficiently with the heat which a thermal storage material has.

  According to the invention of claim 4, when the heat carrying medium is not circulated through the indoor heat exchanger, the heat carrying medium is repeatedly circulated with respect to the heat accumulating material, so that the heat exchange time between the heat accumulating material and the heat carrying medium is increased. The amount of heat exchange between the two can be increased.

  According to the invention of claim 5, when the heat carrying-out medium is circulated in the third circulation channel, the volume of the third circulation channel as a whole is increased by the reservoir to the same extent as the second circulation channel. Therefore, the overall length of the third circulation channel can be shortened.

  According to the invention of claim 6, the thermal efficiency of the air conditioning system for vehicles can be improved, and even when the fluctuation of the power for air conditioning obtained from the power source of the vehicle is large, the air conditioning can be stably performed. This can improve the fuel efficiency of the vehicle.

  Next, the present invention will be described more specifically. First, an example of the heat storage type heat exchanger 1 according to the present invention will be described. In FIG. 1, reference numeral 2 denotes a latent heat storage material, and the first heat storage 21 and the second heat storage 38 include sodium acetate trihydrate. Is used, and the regenerator 26 is a latent heat storage material having a low melting point and a relatively large melting heat, such as water, an ethyl glycol aqueous solution, or an ammonium chloride aqueous solution. Yes. The heat storage material 2 is housed inside a housing 3 having a heat insulating structure, and two flow paths are provided so as to penetrate the heat storage material 2.

  One flow path is a heat carry-in flow path 5 for circulating a heat carry-in medium 4 such as a refrigerant. In the example shown in FIG. It enters from the lower left side, is folded inside the heat storage material 2, and comes out of the heat storage material 2 at the upper left side in FIG. The other flow path is a heat carry-out flow path 7 for circulating a heat carry-out medium 6 such as brine, and this heat carry-out flow path 7 enters from the upper right side of FIG. 2 is folded back from the heat storage material 2 at the lower right side in FIG.

  These flow paths 5 and 7 are configured so that heat exchange occurs between the respective media 4 and 6 and the heat storage material 2 inside the heat storage material 2, and further, between the respective media 4 and 6. Direct heat exchange is configured to occur. Specifically, the upstream side portion of the heat carry-in flow channel 5, that is, the inlet side portion of the heat carry-in flow channel 5, and the downstream portion of the heat carry-out flow channel 7, that is, the heat carry-out flow channel 7 The portions close to the outlet side are arranged so as to approach each other with the heat storage material 2 interposed therebetween and to exchange heat via the heat storage material 2. In this way, the first indirect heat exchange unit 8 is formed.

  A first direct heat exchanging section 9 in which the heat carry-in medium 4 and the heat carry-out medium 6 directly exchange heat is formed in a portion of the heat carry-in flow path 5 downstream of the first indirect heat exchange section 8. The first direct heat exchanging unit 9 exchanges heat between the heat carrying-in medium 4 and the heat carrying-out medium 6 that have passed through the first indirect heat exchanging unit 8 via the partition walls 10 that partition the flow paths 5 and 7. This is the part that produces Therefore, the first direct heat exchanging section 9 can be configured such that one of the flow paths 5 and 7 is passed through the other flow paths 7 and 5 while maintaining an airtight state, or two airtight states are provided. A flow path is formed, and each heat flow path can be configured by an appropriate heat exchanger in which the heat carry-in flow path 5 and the heat carry-out flow path 7 are connected.

  Furthermore, a second indirect heat exchange unit 11 is provided in the heat carry-in channel 5 in a portion downstream of the first direct heat exchange unit 9. The second indirect heat exchanging portion 11 has substantially the same configuration as the first indirect heat exchanging portion 8 described above, and is the most close to the outlet side of the heat carry-in flow path 5 and the heat carry-out flow path 7. The upstream side portion, that is, the inlet side portion approaches the heat storage material 2 so that heat exchange occurs between the media 4 and 6 via the heat storage material 2.

  And the partition in which the heat carrying-in medium 4 and the heat carrying-out medium 6 divide each flow path 5 and 7 in the downstream part from the said 2nd indirect heat exchange part 11 in the heat carrying-in flow path 5, ie, the part on the exit side. A second direct heat exchange unit 12 that directly exchanges heat through 10 is provided. The second direct heat exchange unit 12 has substantially the same configuration as the first direct heat exchange unit 9 described above, and maintains one air flow path 5, 7 in an airtight state with the other flow path 7, 5. It can be configured to penetrate, or is constituted by an appropriate heat exchanger in which two flow paths are formed in an airtight state, and the above-described heat carry-in flow path 5 and heat carry-out flow path 7 are connected to the respective flow paths. can do.

  Therefore, the heat storage type heat exchanger 1 shown in FIG. 1 supplies the heat carry-in medium 4 from the lower left part in FIG. 1 of the heat carry-in flow path 5 and flows it out from the upper left part. It supplies from the upper right part of FIG. 1 of the path 7, and flows out from the lower right part. While each medium 4 and 6 flows in this way, heat exchange occurs between the three media 4 and 6 and the heat storage material 2 or between any one of the media 4 and 6 and the heat storage material 2. More specifically, first, in the first indirect heat exchange unit 8, the heat of the heat carry-in medium 4 is transmitted to the surrounding heat storage material 2 and further transferred to the heat carry-out medium 6 inside the heat carry-out flow path 7. Is done. In this case, since the heat carrying medium 4 has a large amount of heat, it can sufficiently transfer heat to the heat storage material 2, and even heat transfer to the heat carrying medium 6 can be performed sufficiently. can do.

  Heat exchange between the heat carry-in medium 4 with the reduced amount of heat and the heat carry-out medium 6 with the increased amount of heat occurs in the first direct heat exchange unit 9. Here, since heat is exchanged between the media 4 and 6 by so-called direct heat exchange only through the partition walls 10 partitioning the flow paths 5 and 7, the amount of heat of the heat transfer medium 4 is somewhat as described above. Even if the amount of heat of the heat transfer medium 6 decreases and increases, that is, even if the difference in the amount of heat (temperature) between the media 5 and 7 decreases, heat transfer is performed efficiently and sufficiently. In this way, even if the heat carrying medium 4 having a large amount of heat and the heat carrying medium 6 that receives heat flow in the same direction, so-called indirect heat exchange is performed via the heat storage material 2 on the upstream side. Since so-called direct heat exchange is performed on the downstream side, heat can be stored efficiently and sufficiently, and heat can be efficiently and sufficiently exchanged between the media 4 and 6. .

  Indirect heat exchange between the heat carry-in medium 4 and the heat carry-out medium 6 occurs on the relatively upstream side of the heat carry-in flow path 5, and direct heat exchange between the two media 4 and 6 occurs on the downstream side. The same applies to the second indirect heat exchange unit 11 and the second direct heat exchange unit 12 described above. That is, the heat carry-in medium 4 in which the amount of heat is reduced by applying heat to the heat carry-out medium 6 in the first direct heat exchange unit 9 described above is transferred to the second indirect heat exchange unit 11 via the heat storage material 2. Heat exchange is performed with the medium 6. In that case, even if the amount of heat of the heat carrying-in medium 4 is reduced, the amount of heat of the heat carrying-out medium 6 is not increased, so that there is a large heat amount difference (for example, a temperature difference) between the two. The heat exchange efficiency with the heat carrying-out medium 6 can be improved, and necessary and sufficient heat exchange can be caused.

  And in the 2nd direct heat exchange part 12, heat exchange arises between the heat carrying-in medium 4 in which the calorie | heat amount further falls, and the heat carrying-out medium 6 in which the calorie | heat amount has increased somewhat. In this case, the heat amount difference (for example, temperature difference) between the heat carrying medium 4 and the heat carrying medium 6 is small, but since the heat exchange is so-called direct heat exchange through the partition wall 10, it is efficient and necessary. Heat exchange can be performed sufficiently.

  On the other hand, when the heat transfer is stopped because the flow of the heat transfer medium 6 is stopped, the difference in the amount of heat between the heat transfer medium 4 and the heat transfer medium 6 in each of the direct heat exchange units 9 and 12. Therefore, heat transfer to the heat transfer medium 6 hardly occurs. On the other hand, the heat carry-in channel 5 passes through the inside of the heat storage material 2 except for the direct heat exchange portions 9 and 12 and exchanges heat with the heat storage material 2. Therefore, coupled with the large heat exchange area between the heat carrying-in flow path 5 and the heat storage material 2, the heat storage material 2 can be efficiently and sufficiently heated to store heat. Such a situation is the same when heat is carried out in the state where heat is not carried in by the heat carrying-in medium 4, and the heat carrying-out flow path 7 is connected to the heat storage material 2 and the heat except for the direct heat exchange parts 9 and 12. Contact is possible in exchange. Therefore, the heat exchange area between the heat storage material 2 and the heat transfer medium 6 is wide, and the heat of the heat storage material 2 can be efficiently and sufficiently transferred to the heat transfer medium 6.

The state of heat exchange in the case where the refrigerant whose internal energy has been reduced in the refrigeration cycle is continuously circulated and flown as the heat carry-in medium 4 and the cooling brine is continuously circulated and flown as the heat carry-out medium. Table 1 summarizes the results.

  In Table 1, Tr-1, Tr-2, Tr-3, and Tr-4 are, in order, a first indirect heat exchange unit 8, a first direct heat exchange unit 9, a second indirect heat exchange unit 11, and a second direct The temperature of the refrigerant | coolant in the heat exchange part 12 is shown, Tb-1, Tb-2, Tb-3, Tb-4 are the 1st indirect heat exchange part 8, the 1st direct heat exchange part 9, and the 2nd indirect heat in order. The temperature of the brine in the exchange part 11 and the 2nd direct heat exchange part 12 is shown. As known from Table 1, in the case of indirect heat exchange in which the heat storage material 2 is interposed between the heat carry-in channel 5 and the heat carry-out channel 7, the temperature difference between the refrigerant and the brine is large and the opposite. In the case of direct heat exchange in which the heat storage material 2 does not intervene, the temperature difference between the refrigerant and the brine becomes small. As a result, heat storage for the heat storage material 2 and heat exchange between the refrigerant and the brine can be performed efficiently.

  The heat storage heat exchanger 1 described above can be used in an air conditioning system mounted on a vehicle. An example of this is shown schematically in FIG. The example shown in FIG. 2 is an example in which the present invention is applied to a condenser and an evaporator in a heat pump operating in a refrigeration cycle, and a heat exchange section between brine and cooling water. First, the refrigeration cycle will be described. A compressor 20 driven by a power source such as an engine or an electric motor (not shown) is a known one configured to pressurize and compress a refrigerant, and a discharge portion thereof. The 1st heat storage device 21 concerning this invention is connected to. The first heat accumulator 21 has the configuration shown in FIG. 1 described above, and is configured to liquefy the refrigerant by removing the heat of the refrigerant whose pressure has been increased by pressurization and compression by the heat storage material 2. . Therefore, the first heat accumulator 21 corresponds to a condenser (condenser) in the refrigeration cycle.

  A receiver tank 22 and an expansion valve 23 are connected in order to the output side of the first heat accumulator 21. The receiver tank 22 is for temporarily storing a refrigerant (liquid refrigerant) liquefied by radiating heat, and has a function of separating the liquid refrigerant and the gas refrigerant together. A temperature sensor 24 and a pressure sensor 25 are interposed in the pipe line between the receiver tank 22 and the first heat accumulator 21. The expansion valve 23 is a valve that adiabatically expands the refrigerant to reduce its pressure, and a conventionally known one such as a throttle valve or a capillary tube can be used.

  A regenerator (evaporator) 26 is provided for applying heat to the adiabatically expanded refrigerant to vaporize it. The regenerator 26 is a heat storage type heat exchanger configured to give the cold energy of the refrigerant to the heat storage material 2 and the brine, and has the configuration shown in FIG. 1 described above. A pressure sensor 27 and a temperature sensor 28 for detecting the pressure of the adiabatically expanded refrigerant are interposed in the pipe line between the expansion valve 23 and the regenerator 26. The output side of the regenerator 26 is connected to the suction part of the compressor 20.

  The heat and cold generated in the refrigeration cycle can be used as heat energy, and is used for air conditioning of a passenger compartment in a vehicle as an example. For this purpose, the air in the passenger compartment is heated by the heat of the pressure-compressed refrigerant or the heat of the first regenerator 21, and the air in the passenger compartment is cooled by the adiabatic expansion of the refrigerant or the cool heat of the regenerator 26. A vehicle interior heat exchanger 29 is provided. The configuration for supplying heating heat to the vehicle interior heat exchanger 29 will be described. The heating heat medium (brine) is circulated between the first heat accumulator 21 and the vehicle interior heat exchanger 29. One circulation channel 30 is provided.

  The heat exchange between the heating heat medium and the refrigerant is configured to be performed inside the first heat accumulator 21, and therefore the first circulation passage 30 is shown in FIG. It is connected to a pipe line corresponding to the heat carrying-out flow path 7.

  A temperature sensor 31 is interposed in a so-called forward path in which the heating heat medium flows from the first heat accumulator 21 to the vehicle interior heat exchanger 29 in the first circulation flow path 30. A so-called return path through which the heating heat medium flows from the vehicle interior heat exchanger 29 to the first heat accumulator 21 includes a three-way valve 32, a temperature sensor 33, a storage tank 34, a pump 35, and a check valve 36. Are inserted in order. The three-way valve 32 is a switching valve for selectively communicating the second circulation channel 37 branched from the first circulation channel 30 with the so-called return path, and is configured to be switched by an electric signal. ing. Further, when the storage tank 34 flows the heating heat medium to the second circulation channel 37 without passing through the vehicle interior heat exchange 30, the volume of the second circulation channel 37 itself is the first circulation channel. Since it is smaller than the volume of 30, it is provided for temporarily storing an excess heating medium. Further, the check valve 36 allows the flow of the heating heat medium in the so-called forward direction from the vehicle interior heat exchanger 29 toward the first heat accumulator 21, and prevents the so-called reverse flow that is opposite to this. It is a valve. Therefore, the three-way valve 32, the temperature sensor 33, the storage tank 34, the pump 35, and the check valve 36 are provided in a so-called common part of the first circulation channel 30 and the second circulation channel 37. .

  A second heat accumulator 38 that performs heat recovery and heating from a fluid other than the heating heat medium is provided. The second heat accumulator 38 is composed of a heat accumulating heat exchanger similar to the first heat accumulator 21 described above. The second heat accumulator 38 is replaced with the above refrigerant as a heat carrying medium, and engine coolant or automatic transmission oil ( ATF-OIL) cooling water is circulated, and the heating heat medium is circulated as a heat carrying medium. In addition, when warming up the engine or automatic transmission oil (ATF-OIL), the heating heat medium is circulated, the heat of the first heat accumulator 21 is moved to the second heat accumulator 38, and engine cooling water is supplied. And automatic transmission oil (ATF-OIL) cooling water to warm up. That is, the second heat accumulator 38 includes a heat carry-in flow path, and the first circulation flow path 31 is connected to the heat carry-in flow path. In addition, two heat carrying-out passages are provided, the engine cooling water conduit 39 is connected to one heat carrying-out passage, and the automatic transmission oil cooling water conduit 40 is connected to the other heat carrying-out passage. . Further, temperature sensors 41 and 42 and pumps 43 and 44 are interposed in the pipe lines 39 and 40, respectively.

  Further, in order to perform cooling, a third circulation passage 45 for selectively circulating a cooling heat medium (brine) between the regenerator 26 and the vehicle interior heat exchanger 29 is provided. The third circulation flow path 45 is configured so that heat exchange occurs between the refrigerant and the heat storage material 2 and the cooling heat medium inside the regenerator 26. As the heat exchanger, FIG. A configuration similar to that shown in FIG. A pump 46 and a temperature sensor 47 are interposed in a so-called forward path in which the cooling heat medium flows from the regenerator 26 toward the vehicle interior heat exchanger 29 in the third circulation channel 45. In addition, a temperature sensor 48 is interposed in a so-called return path in which a cooling heat medium flows from the vehicle interior heat exchanger 29 to the regenerator 26. In addition, the temperature sensor 49 which detects the temperature of the heat storage material 2 in the 1st heat storage device 21, the temperature sensor 50 which detects the temperature of the heat storage material 2 in the 2nd heat storage device 38, and the temperature sensor which detects the temperature of the cool storage device 26 51 and a temperature sensor 52 that detects an air blowing temperature in the vehicle interior heat exchanger 29 are provided.

  The compressor 20 and each pump are driven and stopped electrically controlled. For this purpose, a control device 53 is provided. The control device 53 is configured mainly with a microcomputer as an example, and is input with temperature information and pressure information detected by each of the temperature sensors and pressure sensors described above, and also includes a cooling request signal and heating (not shown). Another signal such as a request signal is input.

  Next, the operation of the above-described apparatus will be described. First, the operation of the refrigeration cycle will be briefly described. The compressor 20 is driven based on the cooling requirement, and the gas refrigerant is pressurized and compressed. The refrigerant, which has become a superheated steam due to an increase in pressure, dissipates heat in the first heat accumulator 21 and gives heat to the heating heat medium and the heat storage material 2. The state of heat storage and heat exchange in that case is as described with reference to FIG. As a result, the temperature of the refrigerant (the internal energy of the refrigerant) decreases and condenses gradually. The temperature of the refrigerant in that state is detected by the temperature sensor 24 (which may be converted from the detection value of the pressure sensor 25), and the pressure is detected by the pressure sensor 25 (which may be converted from the detection value of the temperature sensor 24). Is done. If the refrigerant is not supercooled, the temperature and pressure are higher than a predetermined value determined by design.

  The condensed refrigerant is temporarily stored in the receiver tank 22. In that case, if uncondensed refrigerant is mixed, gas-liquid separation is performed here. Next, the refrigerant is adiabatically expanded in the expansion valve 23, and a part of the refrigerant evaporates, so that the liquid refrigerant and the gas refrigerant are mixed. The pressure of the mixed refrigerant is detected by the pressure sensor 27 (which may be converted from the detection value of the temperature sensor 28), and the temperature is detected by the temperature sensor 28 (which may be converted from the detection value of the pressure sensor 27). The Then, the mixed refrigerant is sent to the regenerator 26 and evaporates by taking heat from the heat storage material 2 and the cooling heat medium inside. In this case, the cold storage occurs as described with reference to FIG. 1, and so-called cold heat is stored in the regenerator 26, and the cooling heat medium is cooled. The refrigerant thus vaporized is pressurized and compressed again by the compressor 20.

  In addition, since it is comprised so that heat exchange may occur between the thermal storage material 2 in the 2nd thermal storage device 38 mentioned above, engine cooling water, and automatic transmission oil cooling water, when the temperature of these cooling water is low The cooling water is heated by the heat of the heat storage material 2, and so-called warm-up is promoted. Moreover, when the temperature of these cooling waters becomes high by continuing driving | running | working of a vehicle, the heat of the cooling water is transmitted to the thermal storage material 2, and is heat-recovered.

  As described above, the condensation of the refrigerant is performed by the heat storage material 2 or the heating medium deprived of heat. However, when the temperature of the heat storage material 2 gradually increases or the heating medium does not transport heat. In this case, the cooling efficiency of the refrigerant is lowered, and there is a possibility that the refrigerant cannot be cooled to the supercooled state. Therefore, in the present invention, in order to reliably cool the refrigerant to the supercooled state, forced supercooling is performed as follows.

  FIG. 3 is a flowchart for explaining the supercooling operation. First, various pieces of information are read (step S1). For example, an operation request signal for the compressor 20 or the refrigeration cycle, information from each pressure sensor, information from each temperature sensor, and the like are read. Next, it is determined whether or not the pump 35 that causes the heating heat medium in the first circulation passage 30 to flow is in operation (step S2). That is, it is determined whether the heating heat medium flows through the first circulation flow path 30 and exchanges heat with the heat storage material 2 or the refrigerant. If the determination in step S2 is affirmative, the routine is temporarily terminated without performing any particular control.

  On the other hand, if a negative determination is made in step S2, it is determined whether or not forced cooling of the refrigerant is necessary (step S3). When the compressor 20 or the refrigeration cycle is operating in a state where the heating heat medium is not circulated, heat is gradually stored in the heat storage material 2 of the first heat storage device 21 that functions as a condenser in the refrigeration cycle. In particular, when the temperature of the heat storage material 2 around the heat carry-in flow path 5 rises, the condensation of the refrigerant becomes low, and the thermal efficiency of the refrigeration cycle decreases. In step S3, such a situation is determined. Specifically, it can be determined based on the map.

  FIG. 4 shows an example of the map. The detection value of the pressure sensor 25 provided immediately before the receiver tank 22 (or the detection value of the temperature sensor 24) is taken on the horizontal axis, and the first heat accumulator is shown. 21 is a map in which the detection value of the temperature sensor 49 for detecting the temperature of the heat storage material 2 in 21 is taken on the vertical axis, and the region is defined by these detection values. In the map shown here, a region where the pressure is equal to or higher than a predetermined value and the temperature of the heat storage material 2 is equal to or lower than a predetermined temperature is defined as a forced cooling operation region. That is, when the condensation of the refrigerant becomes insufficient, the pressure gradually increases. Therefore, it can be determined by the pressure that the refrigerant needs to be further cooled by the first heat accumulator 21. In that case, the temperature of the first heat accumulator 21 may become high, but when the temperature becomes higher than a predetermined value, it becomes difficult to receive heat from the refrigerant. Therefore, the forced cooling operation region is set to a region below a predetermined temperature, and if the temperature becomes higher than that, measures such as stopping the system may be taken.

  If a negative determination is made in step S3 because the situation that requires forced cooling has not been reached, this routine is temporarily terminated without performing any particular control. On the contrary, if the determination is affirmative, the three-way valve 32 is operated (step S4), the second circulation passage 37 is communicated with the first circulation passage 30, and the pump 35 is turned on. By operating (step S5), the heating heat medium is circulated through the first heat accumulator 21 without passing through the vehicle interior heat exchanger 29. As shown in FIG. 1, the first heat accumulator 21 includes first and second direct heat exchange units 9 and 12, so that the heating heat medium that receives heat directly from the refrigerant performs each indirect heat exchange. Heat is transmitted to the heat storage material 2 in the parts 8 and 11. That is, since the heating heat medium mediates heat transfer between the refrigerant and the heat storage material 2 and the action repeatedly occurs, the heat of the refrigerant is efficiently and efficiently transferred to the heat storage material 2 to supercool the refrigerant. It becomes possible to cool to a state.

  Thus, the heating heat medium circulating in the first circulation path 21 itself has a heat storage function and promotes heat transfer to the heat storage material 2, so that a sufficient amount of heat for cooling the refrigerant is secured, Can be supercooled. As a result, the thermal efficiency of the entire refrigeration cycle can be improved. Further, since heat for condensing the refrigerant and cold heat for evaporation can be stored, it is possible to effectively use the heat energy and thus improve the fuel efficiency of the vehicle.

  Note that the present invention is not limited to the specific examples described above, and can be applied not only to a system that air-conditions a vehicle interior, but also to a system for heating and cooling an appropriate space such as a living room or a storage.

It is a figure which shows typically an example of the heat storage type heat exchanger which concerns on this invention. It is a block diagram which shows an example of the vehicle air conditioning system which used the thermal storage type heat exchanger as a thermal storage or a cool storage. It is a flowchart for demonstrating an example of the control which makes object the system shown in FIG. It is a figure which shows an example of the mop used in order to determine the necessity of forced cooling in the example of control.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Heat storage type heat exchanger, 2 ... Latent heat storage material, 4 ... Heat carrying-in medium, 5 ... Heat carrying-in channel, 6 ... Heat carrying-out medium, 7 ... Heat carrying-out channel, 8 ... 1st indirect heat exchange part, 9 DESCRIPTION OF SYMBOLS 1st direct heat exchange part, 10 ... Partition, 11 ... 2nd indirect heat exchange part, 12 ... 2nd direct heat exchange part, 20 ... Compressor, 21 ... 1st regenerator, 29 ... Car interior heat exchanger, 30 ... 1st circulation flow path, 34 ... Storage tank, 37 ... 2nd circulation flow path, 38 ... 2nd heat accumulator, 45 ... 3rd circulation flow path, 53 ... Control apparatus.

Claims (6)

In a heat storage type heat exchanger comprising a heat storage material, a heat carrying medium that exchanges heat between the heat storage material, and a heat carrying medium that exchanges heat between the heat storage material and the heat carrying medium,
The first indirect heat exchanging unit in which the heat carrying medium and the heat carrying medium exchange heat via the heat storage material, the heat carrying medium and the heat carrying medium form a flow path for each medium. A first direct heat exchanging part for exchanging heat through the partition wall,
The heat storage type heat exchanger, wherein the heat carrying medium and the heat carrying medium are configured to flow through the respective flow paths from the first indirect heat exchange section toward the first direct heat exchange section. . A second indirect heat exchange section in which the heat carry-in medium downstream from the first direct heat exchange section and a heat carry-out medium upstream from the first direct heat exchange section exchange heat through the heat storage material;
The second heat exchange medium downstream from the second indirect heat exchange part and the heat carry-out medium downstream from the second heat exchange part exchange heat through the partition walls forming the respective flow paths. The heat storage type heat exchanger according to claim 1, further comprising a direct heat exchange unit. A first circulation flow path for circulating and flowing the heat carrying-out medium in the heat storage type heat exchanger according to claim 1 or 2 to an indoor heat exchanger;
An air conditioning system comprising: a second circulation passage that circulates and flows the refrigerant compressed and expanded by a refrigeration cycle to the heat storage type heat exchange as the heat carrying medium.   A third circulation passage formed by branching from the first circulation passage, and repeatedly circulating the heat carrying medium inside the heat storage material without passing through the indoor heat exchanger; and the heat carrying medium. The air conditioning system according to claim 3, further comprising a switching valve that switches between the first circulation channel and the third circulation channel.   5. The reservoir according to claim 4, wherein a reservoir for temporarily storing the heat carrying-out medium is provided in a portion of a flow path common to the first circulation flow path and the third circulation flow path. Air conditioning system.   6. The air conditioning system according to claim 3, wherein the air conditioning system is mounted on a vehicle.

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