US20050039897A1 - Internal heat exchanger - Google Patents
Internal heat exchanger Download PDFInfo
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- US20050039897A1 US20050039897A1 US10/901,476 US90147604A US2005039897A1 US 20050039897 A1 US20050039897 A1 US 20050039897A1 US 90147604 A US90147604 A US 90147604A US 2005039897 A1 US2005039897 A1 US 2005039897A1
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- Prior art keywords
- passage
- high pressure
- low pressure
- pressure passage
- heat exchanger
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F7/00—Elements not covered by group F28F1/00, F28F3/00 or F28F5/00
- F28F7/02—Blocks traversed by passages for heat-exchange media
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
Definitions
- This invention is applied to a vapor compression type refrigerator using carbon dioxide as a refrigerant, between internal heat exchangers, for conducting heat exchange between a high pressure side refrigerant and a low pressure side refrigerant.
- Most internal heat exchangers applied to vapor compression type refrigerators are employed to perform heat exchange between a high pressure side refrigerant flowing into a pressure reduction device such as an expansion valve and a low pressure refrigerant sucked into a compressor, to lower the temperature and enthalpy of the refrigerant flowing into the pressure reduction device and to improve a refrigeration capacity of the vapor compression type refrigerators by increasing a heat absorption quantity in an evaporator, that is, a rising amount of enthalpy in the evaporator.
- the capacity of the vapor compression type refrigerator can be improved. Because the number of components constituting the vapor compression type refrigerator increases in this case, the size of the internal heat exchanger must be reduced in order to mount a vapor compression type refrigerator having the internal heat exchanger into an air conditioner for a car having a limited mounting space.
- the invention is directed to provide, in the first place, a novel internal heat exchanger different from internal heat exchangers of the prior art and to provide, in the second place, an internal heat exchanger suitable for a vapor compression type refrigerator using carbon dioxide as a refrigerant.
- a first aspect of the invention provides an internal heat exchanger applied to a vapor compression type refrigerator using carbon dioxide as a refrigerant, having a high pressure passage ( 5 a ) through which a high pressure refrigerant flows and a low pressure passage ( 5 c ) through which a low pressure side refrigerant flows, and conducting heat exchange between the high pressure side refrigerant and the low pressure side refrigerant while the flow of the high pressure side refrigerant and the flow of the low pressure side refrigerant constitute counter-flows, wherein, when the length units are millimeters and a corresponding diameter of the high pressure passage ( 5 a ) is ⁇ h, a passage length (Lh) of the high pressure passage ( 5 a ) is greater than 9.16/ ⁇ LN(4.5 ⁇ h +1.03) ⁇ and smaller than 46/ ⁇ LN(4.5 ⁇ h +1.03) ⁇ , and when the length units are millimeters and a corresponding diameter of the low pressure passage ( 5 c ) is
- an internal heat exchanger applied to a vapor compression type refrigerator using carbon dioxide as a refrigerant having a high pressure passage ( 5 a ) through which a high pressure refrigerant flows and a low pressure passage ( 5 c ) through which a low pressure side refrigerant flows, and conducting heat exchange between the high pressure side refrigerant and the low pressure side refrigerant while the flow of the high pressure side refrigerant and the flow of the low pressure side refrigerant constitute counter-flows, wherein, when a length unit is millimeter and a corresponding diameter of the high pressure passage ( 5 a ) is ⁇ h, a passage sectional area (Ah) of the high pressure passage ( 5 a ) is greater than 100 ⁇ (0.25 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) and smaller than 100 ⁇ (500 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) , and when the length units are millimeters and a
- both of both of the high pressure passage and the low pressure passage ( 5 c ) are constituted by a plurality of passages, and wherein the number (Nh) of the high pressure passages ( 5 a ) is greater than 400/( ⁇ h 2 ) ⁇ (0.25 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) and smaller than 400/( ⁇ h 2 ) ⁇ (500 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) , and the number (Nl) of the low pressure passages ( 5 c ) is greater than 2.1/ ⁇ l 2.47 and smaller than 797/ ⁇ l 2.67 .
- the high pressure passage ( 5 a ) and the low pressure passage ( 5 c ) are aligned on the same axis and constitute a double tube structure.
- the high pressure passage ( 5 a ) and the low pressure passage ( 5 c ) are shaped into a flat shape.
- FIG. 1 is a schematic view of a vapor compression type refrigerator according to an embodiment of the invention
- FIG. 2 is a schematic view of an internal heat exchanger according to a first embodiment of the invention
- FIG. 3 is a graph showing the relation between heat exchange efficiency Q and a passage length Lh of a high pressure passage 5 a in a high pressure tube 5 b when a passage sectional diameter ⁇ of the high pressure passage 5 a is used as a parameter;
- FIG. 4 is a graph showing the relation between heat exchange efficiency Q and a passage length Ll of a low pressure passage 5 c in a low pressure tube 5 d when a passage sectional diameter ⁇ of the low pressure passage 5 c is used as a parameter;
- FIG. 5 is a graph showing the relation between a pressure loss ⁇ P/L per unit passage length and a passage sectional area Ah of the high pressure passage 5 a in the high pressure tube 5 b when a passage sectional diameter ⁇ of the high pressure passage 5 a is used as a parameter;
- FIG. 6 is a graph showing the relation between heat exchange efficiency Q and a passage sectional area Al of the low pressure passage 5 c in the low pressure tube 5 d when a passage sectional diameter ⁇ of the low pressure passage 5 c is used as a parameter;
- FIG. 7 is a schematic view of an internal heat exchanger according to a second embodiment of the invention.
- FIG. 8 is a schematic view of an internal heat exchanger according to a third embodiment of the invention.
- FIG. 1 is a schematic view of the vapor compression type refrigerator according to the embodiment.
- a compressor 1 acquires power from an external driving source such as a driving source for a vehicle (e.g. internal combustion engine such as an engine) and sucks and compresses a refrigerant.
- a radiator 2 is a high pressure side radiator that performs heat exchange between a high pressure refrigerant ejected from the compressor 1 and external air and cools the high pressure refrigerant.
- a pressure reduction device 3 reduces the pressure of the high pressure side refrigerant flowing out from the radiator 2 .
- This embodiment uses a device that equi-enthalpically reduces the pressure such as an expansion valve or a fixed choke.
- An evaporator 4 is a low pressure side heat exchanger that evaporates a low pressure side refrigerant the pressure of which is reduced by the pressure reduction device 3 , performs heat exchange between the low pressure side refrigerant and air blowing into a passenger compartment and exhibits a cooling capacity by evaporating the low pressure refrigerant.
- this embodiment uses carbon dioxide as the refrigerant and the critical temperature of carbon dioxide is as low as about 31° C. Therefore, the pressure of the high pressure side coolant, that is, the discharge pressure of the compressor 1 , is set to be higher than the critical pressure of the refrigerant to secure a necessary heat radiation capacity (temperature difference). As the high pressure side refrigerant has a pressure higher than the critical pressure, its enthalpy is lowered by lowering the temperature without condensing the coolant inside the radiator 2 .
- the internal heat exchanger 5 is a heat exchanger that performs heat exchange between the low pressure side refrigerant flowing out from the evaporator 4 and the high pressure side refrigerant flowing out from the radiator 2 .
- the internal heat exchanger 5 includes a high pressure tube 5 b having a plurality of high pressure passages 5 a through which the high pressure side refrigerant flows and a low pressure tube 5 d having low pressure passages 5 c through which the low pressure side refrigerant flows, as shown in FIG. 2 .
- Both tubes 5 b and 5 d are shaped into a flat shape by applying an extrusion process or a drawing process to a metal material such as an aluminum alloy, and both passages 5 a and 5 c are formed in the respective tubes 5 b and 5 d simultaneously with molding of the tubes 5 b and 5 c.
- brazing used hereby means a bonding technology that uses a brazing material or a solder without melting a base material as described in “Connection-Bonding Technology” (Tokyo Electric University Press).
- a bonding technology that uses a filler metal having a melting point of 450° C. or above is referred to as “brazing” and the filler metal used is referred to as a “brazing material”.
- a bonding technology that uses a filler metal having a melting point of 450° C. or below is referred to “soldering” and the filler metal is referred to as “solder”.
- the passage length Lh of the high pressure passage 5 a is so set as to be greater than 9.16/ ⁇ LN(4.5 ⁇ h +1.03) ⁇ and smaller than 46/ ⁇ LN(4.5 ⁇ h +1.03) ⁇ .
- the passage length Ll of the low pressure passage 5 c is so set as to be greater than 9.16/ ⁇ LN(0.56 ⁇ 6 ⁇ l +1.02) ⁇ and smaller than 46/ ⁇ LN(0.56 ⁇ 6 ⁇ l +1.02) ⁇ .
- the passage sectional area Ah of the high pressure passage 5 a is so set as to be greater than 100 ⁇ (0.25 ⁇ h 1.2 ) ⁇ 1(0.04 ⁇ h+1.7) and smaller than 100 ⁇ (500 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) .
- the passage sectional area Al of the low pressure passage 5 c is so set as to be greater than 1.65/ ⁇ h 0.67 and smaller than 626/ ⁇ l 0.67 .
- the units of length are millimeters.
- corresponding diameter means the value obtained by multiplying by 4 the sum of the passage sectional areas of the passages 5 a , 5 c and dividing the product by the sum of the circumferences of the passages 5 a , 5 c corresponding to the length of a wetted perimeter.
- the passage sectional area of one passage is multiplied by 4 and the product is then divided by the circumference corresponding to the length of the wetted perimeter.
- FIG. 3 shows a numerical value simulation result representing the relation between heat exchange efficiency Q and the passage length Lh of the high pressure passage 5 a in the high pressure tube 5 b when the passage sectional diameter ⁇ of the high pressure passage 5 a is used as a parameter
- FIG. 4 shows a numerical value simulation result representing the relation between heat exchange efficiency Q and the passage length Ll of the low pressure passage 5 c in the low pressure tube 5 d when the passage sectional diameter ⁇ of the low pressure passage 5 c is used as a parameter.
- Lh 10 ⁇ LN ⁇ 1/(1 ⁇ Q ) ⁇ / LN ⁇ 1/4.5 ⁇ h +1.03 ⁇
- Ll 10 ⁇ LN ⁇ 1/(1 ⁇ Q ) ⁇ / LN ⁇ 0.56/6 ⁇ l +1.02 ⁇
- heat exchange efficiency Q of at least 0.6 is required.
- heat exchange efficiency Q substantially gets into saturation at 0.99 and can hardly be improved any longer. Therefore, heat exchange efficiency is preferably a value that is greater than 0.6 and smaller than 0.99.
- the upper limit values and the lower limit values of the passage length Lh of the high pressure passage 5 a and the passage length Ll of the low pressure passage 5 c are determined in the following way on the basis of the equations given above: 9.16/ ⁇ LN (4.5 ⁇ h +1.03) ⁇ Lh ⁇ 46/ ⁇ LN (4.5 ⁇ h +1.03) ⁇ 9.16 / ⁇ LN (0.56 ⁇ 6 ⁇ l +1.02) ⁇ Ll ⁇ 46/ ⁇ LN (0.56 ⁇ 6 ⁇ l +1.02) ⁇
- a compact and high performance internal heat exchange 5 can be obtained by so setting the passage length Lh of the high pressure passage 5 a as to be greater than 9.16/ ⁇ LN(4.5 ⁇ h +1.03) ⁇ and smaller than 46/ ⁇ LN(4.5 ⁇ h +1.03) ⁇ when the corresponding diameter of the high pressure passage 5 a is ⁇ h, and by so setting the passage length Ll of the low pressure passage 5 c as to be greater than 9.16/ ⁇ LN(0.56 ⁇ 6 ⁇ l +1.02) ⁇ and smaller than 46/ ⁇ LN(0.56 ⁇ 6 ⁇ l +1.02) ⁇ when the corresponding diameter of the low pressure passage 5 c is ⁇ l.
- each passage 5 a and 5 c gets elongated, the contact area between the high pressure tube 5 b and the low pressure tube 5 d, that is, the heat exchange area, increases. Consequently, when the passage length of each passage 5 a and 5 c increases, the pressure loss occurring in each passage 5 a and 5 c increases though the heat exchange quantity between the high pressure side refrigerant and the low pressure side refrigerant increases. As a result, the velocity of the refrigerant flowing through each passage 5 a and 5 c drops and the heat transfer rate as well as heat exchange efficiency Q drop.
- FIG. 5 shows a numerical value simulation result representing the relation between a pressure loss ⁇ P/L per unit passage length and the passage sectional area Ah of the high pressure passage 5 a in the high pressure tube 5 b when the passage sectional diameter ⁇ of the high pressure passage 5 a is used as a parameter
- FIG. 6 shows a numerical value simulation result representing the relation between heat exchange efficiency Q and the passage sectional area Al of the low pressure passage 5 c in the low pressure tube 5 d when the passage sectional diameter ⁇ of the low pressure passage 5 c is used as a parameter.
- the pressure loss occurring in the internal heat exchanger 5 must be less than 1,000 kPa.
- the pressure loss hardly changes with respect to the increase of the passage sectional area when the pressure loss per unit passage length is 0.005 kPa/mm or less.
- the pressure loss per unit passage length is preferably greater than 0.1 kPa/mm.
- the upper limit values and the lower limit values of the passage sectional area Ah of the high pressure passage 5 a and the passage sectional area Al of the low pressure passage 5 c are determined in the following way: 100 ⁇ (0.25 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) ⁇ Ah ⁇ 100 ⁇ (500 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) 1.65/ ⁇ l 0.67 ⁇ Al ⁇ 626/ ⁇ l 0.67
- a compact and high performance internal heat exchange 5 can be reliably obtained by so setting the passage sectional area Ah of the high pressure passage 5 a as to be greater than 100 ⁇ ( 0.25 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) and smaller than 100 ⁇ (500 ⁇ h 1.2) ⁇ 1/(0.04 ⁇ h+1.7) and by so setting the passage sectional area Al of the low pressure passage 5 c as to be greater than 1.65/ ⁇ l 0.67 and smaller than 626/ ⁇ l 0.67 .
- the passages 5 a and 5 c have a circular sectional shape and a plurality of passages 5 a and 5 c exist. Therefore, the number Nh of the high pressure passages 5 a and the number Nl of the low pressure passages 5 c are given as follows: 400/( ⁇ h 2 ) ⁇ (0.25 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) ⁇ Nh ⁇ 400/( ⁇ h 2 ) ⁇ (500 ⁇ h 1.2 ) ⁇ 1/(0.04 ⁇ h+1.7) 2.1/ ⁇ l 2.67 ⁇ Nl ⁇ 797/ ⁇ l 2.67
- the values obtained by counting fractions are used as the lower limit values of the numbers Nh and Nl and those obtained by omitting the fractions are used as the upper limit values of Nh and Nl.
- the high pressure tube 5 b and the low pressure tube 5 d are unified by brazing, etc, but in this embodiment, the high pressure tube 5 b and the low pressure tube 5 d are integrally molded by the extrusion process or the drawing process as shown in FIG. 7 .
- the flat tubes constitute the internal heat exchanger.
- the high pressure passage 5 a and the low pressure passages 5 c are aligned on the same axis to form a double wall structure as shown in FIG. 8 .
- the passage sectional area Ah is the passage sectional area of one high pressure passage 5 a and the passage sectional area Al of the low pressure passages 5 c is the sum of a plurality of low pressure passages 5 c.
- the embodiment is not limited to this construction and the high pressure passages 5 a may be arranged outside the low pressure passage 5 c.
- the construction of the internal heat exchanger 5 according to the invention is not limited to those described in the foregoing embodiments.
- both high pressure passage 5 a and low pressure passage 5 c extend linearly but the invention is not limited thereto.
- both passages 5 a and 5 c may well extend in a zigzag form.
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Abstract
In an internal heat exchanger, when a corresponding diameter of a high pressure passage 5 a is ψh, a passage length Lh of the high pressure passage (5 a) is so set as to satisfy the relation 9.16/{LN(4.5−ψh+1.03)}<Lh<46/{LN(4.5−ψh+1.03)}, and when a corresponding diameter of a low pressure passage 5 c is ψl, a passage length Ll of the low pressure passage 5 c is so set as to satisfy the relation 9.16/{LN(0.56×6−ψl+1.02)}<Ll<46/{LN(0.56×6−ψ+1.02)}, a passage sectional area Ah of the high pressure passage 5 a is so set as to satisfy the relation 100×(0.25×ψh1.2)−1/(0.04×ψh+1.7)<Ah <100×(500×ψh1.2)−1(0.04×ψh+1.7), and a passage sectional area Al of the low pressure passage 5 c is so set as to satisfy the relation 1.65/ψl0.67<Al<626/ψl0.67.
Description
- 1. Field of the Invention
- This invention is applied to a vapor compression type refrigerator using carbon dioxide as a refrigerant, between internal heat exchangers, for conducting heat exchange between a high pressure side refrigerant and a low pressure side refrigerant.
- 2. Description of the Related Art
- Most internal heat exchangers applied to vapor compression type refrigerators are employed to perform heat exchange between a high pressure side refrigerant flowing into a pressure reduction device such as an expansion valve and a low pressure refrigerant sucked into a compressor, to lower the temperature and enthalpy of the refrigerant flowing into the pressure reduction device and to improve a refrigeration capacity of the vapor compression type refrigerators by increasing a heat absorption quantity in an evaporator, that is, a rising amount of enthalpy in the evaporator.
- When such an internal heat exchanger is used, the capacity of the vapor compression type refrigerator can be improved. Because the number of components constituting the vapor compression type refrigerator increases in this case, the size of the internal heat exchanger must be reduced in order to mount a vapor compression type refrigerator having the internal heat exchanger into an air conditioner for a car having a limited mounting space.
- When the size of the internal heat exchanger is merely reduced, the high pressure side refrigerant cannot sufficiently be cooled in the internal heat exchanger, and the refrigeration capacity of the vapor compression type refrigerator cannot sufficiently be improved.
- In view of the problems described above, the invention is directed to provide, in the first place, a novel internal heat exchanger different from internal heat exchangers of the prior art and to provide, in the second place, an internal heat exchanger suitable for a vapor compression type refrigerator using carbon dioxide as a refrigerant.
- To accomplish these objects, a first aspect of the invention provides an internal heat exchanger applied to a vapor compression type refrigerator using carbon dioxide as a refrigerant, having a high pressure passage (5 a) through which a high pressure refrigerant flows and a low pressure passage (5 c) through which a low pressure side refrigerant flows, and conducting heat exchange between the high pressure side refrigerant and the low pressure side refrigerant while the flow of the high pressure side refrigerant and the flow of the low pressure side refrigerant constitute counter-flows, wherein, when the length units are millimeters and a corresponding diameter of the high pressure passage (5 a) is ψh, a passage length (Lh) of the high pressure passage (5 a) is greater than 9.16/{LN(4.5−ψh+1.03)} and smaller than 46/{LN(4.5−ψh+1.03)}, and when the length units are millimeters and a corresponding diameter of the low pressure passage (5 c) is ψl, a passage length (Ll) of the low pressure passage (5 c) is greater than 9.16/{LN(0.56×6−ψl+1.02)} and smaller than 46/{LN(0.56×6−ψl+1.02)}.
- In consequence, a compact and high performance internal heat exchanger can be obtained as shown in later-appearing
FIGS. 3 and 4 . - According to another aspect of the invention, there is provided an internal heat exchanger applied to a vapor compression type refrigerator using carbon dioxide as a refrigerant, having a high pressure passage (5 a) through which a high pressure refrigerant flows and a low pressure passage (5 c) through which a low pressure side refrigerant flows, and conducting heat exchange between the high pressure side refrigerant and the low pressure side refrigerant while the flow of the high pressure side refrigerant and the flow of the low pressure side refrigerant constitute counter-flows, wherein, when a length unit is millimeter and a corresponding diameter of the high pressure passage (5 a) is ψh, a passage sectional area (Ah) of the high pressure passage (5 a) is greater than 100×(0.25×ψh1.2)−1/(0.04×ψh+1.7) and smaller than 100×(500×ψh1.2)−1/(0.04×ψh+1.7), and when the length units are millimeters and a corresponding diameter of the low pressure passage (5 c) is ψl, a passage sectional area (Al) of the low pressure passage (5 c) is greater than 1.65/ψl0.67 and smaller than 626/ψl0.67.
- Inconsequence, a compact and high performance internal heat exchanger can be obtained as shown in later-appearing
FIGS. 5 and 6 . - According to the invention, both of both of the high pressure passage and the low pressure passage (5 c) are constituted by a plurality of passages, and wherein the number (Nh) of the high pressure passages (5 a) is greater than 400/(π×ψh2)×(0.25×ψh1.2)−1/(0.04×ψh+1.7) and smaller than 400/(π×ψh2)×(500×ψh1.2)−1/(0.04×ψh+1.7), and the number (Nl) of the low pressure passages (5 c) is greater than 2.1/ψl2.47 and smaller than 797/ψl2.67.
- According to the invention, further, the high pressure passage (5 a) and the low pressure passage (5 c) are aligned on the same axis and constitute a double tube structure.
- According to the invention, further, the high pressure passage (5 a) and the low pressure passage (5 c) are shaped into a flat shape.
- The present invention may be more fully understood from the description of preferred embodiments of the invention as set forth below together with the accompanying drawings.
- In the drawings:
-
FIG. 1 is a schematic view of a vapor compression type refrigerator according to an embodiment of the invention; -
FIG. 2 is a schematic view of an internal heat exchanger according to a first embodiment of the invention; -
FIG. 3 is a graph showing the relation between heat exchange efficiency Q and a passage length Lh of ahigh pressure passage 5 a in ahigh pressure tube 5 b when a passage sectional diameter ψ of thehigh pressure passage 5 a is used as a parameter; -
FIG. 4 is a graph showing the relation between heat exchange efficiency Q and a passage length Ll of alow pressure passage 5 c in alow pressure tube 5 d when a passage sectional diameter ψ of thelow pressure passage 5 c is used as a parameter; -
FIG. 5 is a graph showing the relation between a pressure loss ΔP/L per unit passage length and a passage sectional area Ah of thehigh pressure passage 5 a in thehigh pressure tube 5 b when a passage sectional diameter ψ of thehigh pressure passage 5 a is used as a parameter; -
FIG. 6 is a graph showing the relation between heat exchange efficiency Q and a passage sectional area Al of thelow pressure passage 5 c in thelow pressure tube 5 d when a passage sectional diameter ψ of thelow pressure passage 5 c is used as a parameter; -
FIG. 7 is a schematic view of an internal heat exchanger according to a second embodiment of the invention; and -
FIG. 8 is a schematic view of an internal heat exchanger according to a third embodiment of the invention. - In this embodiment, an internal heat exchanger for a vapor compression type refrigerator according to the invention is applied to an air conditioner for a car using carbon dioxide as a refrigerant, and
FIG. 1 is a schematic view of the vapor compression type refrigerator according to the embodiment. - Referring to
FIG. 1 , acompressor 1 acquires power from an external driving source such as a driving source for a vehicle (e.g. internal combustion engine such as an engine) and sucks and compresses a refrigerant. Aradiator 2 is a high pressure side radiator that performs heat exchange between a high pressure refrigerant ejected from thecompressor 1 and external air and cools the high pressure refrigerant. - A pressure reduction device 3 reduces the pressure of the high pressure side refrigerant flowing out from the
radiator 2. This embodiment uses a device that equi-enthalpically reduces the pressure such as an expansion valve or a fixed choke. - An evaporator 4 is a low pressure side heat exchanger that evaporates a low pressure side refrigerant the pressure of which is reduced by the pressure reduction device 3, performs heat exchange between the low pressure side refrigerant and air blowing into a passenger compartment and exhibits a cooling capacity by evaporating the low pressure refrigerant.
- Incidentally, this embodiment uses carbon dioxide as the refrigerant and the critical temperature of carbon dioxide is as low as about 31° C. Therefore, the pressure of the high pressure side coolant, that is, the discharge pressure of the
compressor 1, is set to be higher than the critical pressure of the refrigerant to secure a necessary heat radiation capacity (temperature difference). As the high pressure side refrigerant has a pressure higher than the critical pressure, its enthalpy is lowered by lowering the temperature without condensing the coolant inside theradiator 2. - The
internal heat exchanger 5 is a heat exchanger that performs heat exchange between the low pressure side refrigerant flowing out from the evaporator 4 and the high pressure side refrigerant flowing out from theradiator 2. Theinternal heat exchanger 5 includes ahigh pressure tube 5 b having a plurality ofhigh pressure passages 5 a through which the high pressure side refrigerant flows and alow pressure tube 5 d havinglow pressure passages 5 c through which the low pressure side refrigerant flows, as shown inFIG. 2 . - Both
tubes passages respective tubes tubes - Both
tubes - Incidentally, a bonding technology that uses a filler metal having a melting point of 450° C. or above is referred to as “brazing” and the filler metal used is referred to as a “brazing material”. A bonding technology that uses a filler metal having a melting point of 450° C. or below is referred to “soldering” and the filler metal is referred to as “solder”.
- In this embodiment, when a corresponding diameter of the
high pressure passage 5 a is ψh, the passage length Lh of thehigh pressure passage 5 a is so set as to be greater than 9.16/{LN(4.5−ψh+1.03)} and smaller than 46/{LN(4.5−ψh+1.03)}. When a corresponding diameter of thelow pressure passage 5 c is ψl, the passage length Ll of thelow pressure passage 5 c is so set as to be greater than 9.16/{LN(0.56×6−ψl+1.02)} and smaller than 46/{LN(0.56×6−ψl+1.02)}. - Furthermore, when the corresponding diameter of the
high pressure passage 5 a is ψh, the passage sectional area Ah of thehigh pressure passage 5 a is so set as to be greater than 100×(0.25×ψh1.2)−1(0.04×ψh+1.7) and smaller than 100×(500×ψh1.2)−1/(0.04×ψh+1.7). When the corresponding diameter of thelow pressure passage 5 c is ψl, the passage sectional area Al of thelow pressure passage 5 c is so set as to be greater than 1.65/ψh0.67 and smaller than 626/ψl0.67. The units of length are millimeters. - Here, the term “corresponding diameter” means the value obtained by multiplying by 4 the sum of the passage sectional areas of the
passages passages passages - The symbol “LN” is the abbreviation of “Natural Logarithm” as is well known in the art and is a logarithm using e (=2.71828 . . . ) as the base. Therefore, LN10, for example, means log.10.
- Next, the features of the
internal heat exchanger 5 according to the embodiment will be described. -
FIG. 3 shows a numerical value simulation result representing the relation between heat exchange efficiency Q and the passage length Lh of thehigh pressure passage 5 a in thehigh pressure tube 5 b when the passage sectional diameter ψ of thehigh pressure passage 5 a is used as a parameter andFIG. 4 shows a numerical value simulation result representing the relation between heat exchange efficiency Q and the passage length Ll of thelow pressure passage 5 c in thelow pressure tube 5 d when the passage sectional diameter ψ of thelow pressure passage 5 c is used as a parameter. - The graph shown in
FIG. 3 is numerically formulated as follows:
Q=1−(1/4.5ψh+1.03)−Lh/10. - When this equation is modified as to Lh:
Lh=10·LN{1/(1−Q)}/LN{1/4.5ψh+1.03} - The graph shown in
FIG. 4 is numerically formulated as follows:
Q=1−(0.56/6ψl+1.02)−Ll/10. - When this equation is modified as to Ll:
Ll=10·LN{1/(1−Q)}/LN{0.56/6ψl+1.02} - In order to let the
internal heat exchanger 5 operate as means for improving the capacity of the vapor compression type refrigerator, heat exchange efficiency Q of at least 0.6 is required. - As can be obviously understood from
FIGS. 3 and 4 , on the other hand, heat exchange efficiency Q substantially gets into saturation at 0.99 and can hardly be improved any longer. Therefore, heat exchange efficiency is preferably a value that is greater than 0.6 and smaller than 0.99. - Therefore, the upper limit values and the lower limit values of the passage length Lh of the
high pressure passage 5 a and the passage length Ll of thelow pressure passage 5 c are determined in the following way on the basis of the equations given above:
9.16/{LN(4.5−ψh+1.03)}<Lh< 46/{LN(4.5−ψh+1.03)}
9.16/{LN(0.56×6−ψl+1.02)}<Ll<46/{LN(0.56×6−ψl+1.02)} - Therefore, a compact and high performance
internal heat exchange 5 can be obtained by so setting the passage length Lh of thehigh pressure passage 5 a as to be greater than 9.16/{LN(4.5−ψh+1.03)} and smaller than 46/{LN(4.5−ψh+1.03)} when the corresponding diameter of thehigh pressure passage 5 a is ψh, and by so setting the passage length Ll of thelow pressure passage 5 c as to be greater than 9.16/{LN(0.56×6−ψl+1.02)} and smaller than 46/{LN(0.56×6−ψl+1.02)} when the corresponding diameter of thelow pressure passage 5 c is ψl. - When the passage sectional area of each
passage passage passage - When the passage length of each
passage high pressure tube 5 b and thelow pressure tube 5 d, that is, the heat exchange area, increases. Consequently, when the passage length of eachpassage passage passage -
FIG. 5 shows a numerical value simulation result representing the relation between a pressure loss ΔP/L per unit passage length and the passage sectional area Ah of thehigh pressure passage 5 a in thehigh pressure tube 5 b when the passage sectional diameter ψ of thehigh pressure passage 5 a is used as a parameter andFIG. 6 shows a numerical value simulation result representing the relation between heat exchange efficiency Q and the passage sectional area Al of thelow pressure passage 5 c in thelow pressure tube 5 d when the passage sectional diameter ψ of thelow pressure passage 5 c is used as a parameter. - The graph shown in
FIG. 5 is numerically formulated as follows:
ΔPh/Lh=0.02×ψh −1.2×(100/Ah)0.04×ψh+1.7 - The graph shown in
FIG. 6 is numerically formulated as follows:
ΔPl/Ll=0.18×ψl −1.3×(100/Al)1.95 - Here, to satisfy the requirement for the vapor compression type refrigerator, the pressure loss occurring in the
internal heat exchanger 5 must be less than 1,000 kPa. As can be obviously seen fromFIGS. 5 and 6 , the pressure loss hardly changes with respect to the increase of the passage sectional area when the pressure loss per unit passage length is 0.005 kPa/mm or less. To reduce the size of theinternal heat exchanger 5, therefore, the pressure loss per unit passage length is preferably greater than 0.1 kPa/mm. - Therefore, the upper limit values and the lower limit values of the passage sectional area Ah of the
high pressure passage 5 a and the passage sectional area Al of thelow pressure passage 5 c are determined in the following way:
100×(0.25×ψh 1.2 )−1/(0.04×ψh+1.7) <Ah<100×(500×ψh 1.2)−1/(0.04×ψh+1.7)
1.65/ψl 0.67 <Al<626/ψl 0.67 - Therefore, a compact and high performance
internal heat exchange 5 can be reliably obtained by so setting the passage sectional area Ah of thehigh pressure passage 5 a as to be greater than 100×(0.25×ψh 1.2)−1/(0.04×ψh+1.7) and smaller than 100×(500ψh1.2) −1/(0.04×ψh+1.7) and by so setting the passage sectional area Al of thelow pressure passage 5 c as to be greater than 1.65/ψl0.67 and smaller than 626/ψl0.67. - In this embodiment, the
passages passages high pressure passages 5 a and the number Nl of thelow pressure passages 5 c are given as follows:
400/(π×ψh 2)×(0.25×ψh 1.2)−1/(0.04×ψh+1.7) <Nh<400/(π×ψh 2)×(500×ψh 1.2)−1/(0.04×ψh+1.7)
2.1/ψl 2.67 <Nl<797/ψl 2.67 - As the number Nh of the
high pressure passages 5 a and the number Nl of thelow pressure passages 5 c are the natural numbers, the values obtained by counting fractions are used as the lower limit values of the numbers Nh and Nl and those obtained by omitting the fractions are used as the upper limit values of Nh and Nl. - In the first embodiment, the
high pressure tube 5 b and thelow pressure tube 5 d are unified by brazing, etc, but in this embodiment, thehigh pressure tube 5 b and thelow pressure tube 5 d are integrally molded by the extrusion process or the drawing process as shown inFIG. 7 . - In the embodiments given above, the flat tubes constitute the internal heat exchanger. In this embodiment, however, the
high pressure passage 5 a and thelow pressure passages 5 c are aligned on the same axis to form a double wall structure as shown inFIG. 8 . - Incidentally, as the
high pressure passage 5 a is only one in this embodiment, the passage sectional area Ah is the passage sectional area of onehigh pressure passage 5 a and the passage sectional area Al of thelow pressure passages 5 c is the sum of a plurality oflow pressure passages 5 c. - Though the
high pressure passage 5 a is arranged inside thelow pressure passages 5 c in this embodiment, the embodiment is not limited to this construction and thehigh pressure passages 5 a may be arranged outside thelow pressure passage 5 c. - Though the invention is applied to the air conditioner for a car in the embodiments described above, the application of the invention is not limited thereto.
- The construction of the
internal heat exchanger 5 according to the invention is not limited to those described in the foregoing embodiments. - In the
internal heat exchanger 5 according to the invention, bothhigh pressure passage 5 a andlow pressure passage 5 c extend linearly but the invention is not limited thereto. For examples, bothpassages - While the invention has been described by reference to specific embodiments chosen for the purposes of illustration, it should be apparent that numerous modifications could be made thereto by those skilled in the art without departing from the basic concept and scope of the invention.
Claims (7)
1. An internal heat exchanger applied to a vapor compression type refrigerator using carbon dioxide as a refrigerant, having a high pressure passage (5 a) through which a high pressure refrigerant flows and a low pressure passage (5 c) through which a low pressure side refrigerant flows, and conducting heat exchange between said high pressure side refrigerant and said low pressure side refrigerant while the flow of said high pressure side refrigerant and the flow of said low pressure side refrigerant constitute counter-flows, wherein:
when the length units are millimeters and a corresponding diameter of said high pressure passage (5 a) is ψh, a passage length (Lh) of said high pressure passage (5 a) is greater than 9.16/{LN(4.5−ψh+1.03)} and smaller than 46/{LN(4.5−ψh+1.03)}, and when a length unit is millimeter and a corresponding diameter of said low pressure passage (5 c) is ψl, a passage length (Ll) of said low pressure passage (5 c) is greater than 9.16/{LN(0.56×6−ψl+1.02)} and smaller than 46/{LN(0.56×6−ψl+1.02)}.
2. An internal heat exchanger according to claim 1 , wherein said high pressure passage (5 a) and said low pressure passage (5 c) are aligned on the same axis and constitute a double tube structure.
3. An internal heat exchanger according to claim 1 , wherein tubular members constituting said high pressure passage (5 a) and said low pressure passage (5 c) are shaped into a flat shape.
4. An internal heat exchanger applied to a vapor compression type refrigerator using carbon dioxide as a refrigerant, having a high pressure passage (5 a) through which a high pressure refrigerant flows and a low pressure passage (5 c) through which a low pressure side refrigerant flows, and conducting heat exchange between said high pressure side refrigerant and said low pressure side refrigerant while the flow of said high pressure side refrigerant and the flow of said low pressure side refrigerant constitute counter-flows, wherein:
when the length units are millimeters and a corresponding diameter of said high pressure passage (5 a) is ψh, a passage sectional area (Ah) of said high pressure passage (5 a) is greater than 100×(0.25×ψh 1.2)−1/(0.04×ψh+1.7) and smaller than 100×(500×ψh 1.2)−1/(0.04×ψh+1.7), and when a length unit is millimeter and a corresponding diameter of said low pressure passage (5 c) is ψl, a passage sectional area (Al) of said low pressure passage (5 c) is greater than 1.65/ψl0.67 and smaller than 626/ψl0.67.
5. An internal heat exchanger according to claim 4 , wherein both of said high pressure passage and said low pressure passage (5 c) are constituted by a plurality of passages, and wherein the number (Nh) of said high pressure passages (5 a) is greater than 400/(π×ψh2)×(0.25×ψh1.2)−1/(0.04×ψh+1.7) and smaller than 400/(π×ψh2)×(500×ψh1.2)−1/(0.04×ψh+1.7), and the number (Nl) of said low pressure passages (5 c) is greater than 2.1/ψl2.67 and smaller than 797/ψl2.67.
6. An internal heat exchanger according to claim 4 , wherein said high pressure passage (5 a) and said low pressure passage (5 c) are aligned on the same axis and constitute a double tube structure.
7. An internal heat exchanger according to claim 4 , wherein tubular members constituting said high pressure passage (5 a) and said low pressure passage (5 c) are shaped into a flat shape.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/649,319 US7621320B2 (en) | 2003-07-29 | 2007-01-03 | Internal heat exchanger |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003281817A JP4196774B2 (en) | 2003-07-29 | 2003-07-29 | Internal heat exchanger |
JP2003-281817 | 2003-07-29 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/649,319 Continuation-In-Part US7621320B2 (en) | 2003-07-29 | 2007-01-03 | Internal heat exchanger |
Publications (1)
Publication Number | Publication Date |
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US20050039897A1 true US20050039897A1 (en) | 2005-02-24 |
Family
ID=34190848
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/901,476 Abandoned US20050039897A1 (en) | 2003-07-29 | 2004-07-28 | Internal heat exchanger |
US11/649,319 Expired - Fee Related US7621320B2 (en) | 2003-07-29 | 2007-01-03 | Internal heat exchanger |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
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US11/649,319 Expired - Fee Related US7621320B2 (en) | 2003-07-29 | 2007-01-03 | Internal heat exchanger |
Country Status (3)
Country | Link |
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US (2) | US20050039897A1 (en) |
JP (1) | JP4196774B2 (en) |
DE (1) | DE102004036460B4 (en) |
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DE102005021464A1 (en) * | 2005-05-10 | 2006-11-16 | Modine Manufacturing Co., Racine | Intermediate heat exchanger for air-conditioning loop, has heat exchange ribs filling compartment between tube and two opposing walls, where refrigerant flowing through compartment does not flow through large space |
US20140144611A1 (en) * | 2011-05-06 | 2014-05-29 | Mitsubishi Electric Corporation | Heat exchanger and refrigeration cycle apparatus equipped with the same |
US20140174703A1 (en) * | 2011-07-28 | 2014-06-26 | Shun Yoshioka | Heat exchanger |
US20140202664A1 (en) * | 2013-01-21 | 2014-07-24 | Halliburton Energy Services, Inc. | Drilling Fluid Sampling System and Sampling Heat Exchanger |
US9746212B2 (en) | 2011-11-29 | 2017-08-29 | Mitsubishi Electric Coroporation | Refrigerating and air-conditioning apparatus |
CN108981431A (en) * | 2018-09-26 | 2018-12-11 | 上海加冷松芝汽车空调股份有限公司 | A kind of liquid collecting tube assembly and heat exchanger |
US11371758B2 (en) * | 2018-04-11 | 2022-06-28 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus |
US11725889B1 (en) * | 2019-02-26 | 2023-08-15 | National Technology & Engineering Solutions Of Sandia, Llc | Refractory high entropy alloy compact heat exchanger |
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JP4667134B2 (en) * | 2005-06-22 | 2011-04-06 | サンデン株式会社 | Air conditioner for vehicles |
DE102005056651A1 (en) * | 2005-11-25 | 2007-05-31 | Behr Gmbh & Co. Kg | Coaxial tube or tube-in-tube arrangement, in particular for a heat exchanger |
EP1978317B1 (en) * | 2007-04-06 | 2017-09-06 | Samsung Electronics Co., Ltd. | Refrigerant cycle device |
JP4849041B2 (en) * | 2007-09-11 | 2011-12-28 | 株式会社富士通ゼネラル | Heat exchanger |
FR2928997B1 (en) * | 2008-03-20 | 2014-06-20 | Valeo Systemes Thermiques | HEAT EXCHANGER AND INTEGRATED AIR CONDITIONING ASSEMBLY COMPRISING SUCH AN EXCHANGER. |
JP2010096372A (en) * | 2008-10-15 | 2010-04-30 | Hitachi Cable Ltd | Internal heat exchanger for carbon dioxide refrigerant |
JP5157811B2 (en) * | 2008-10-15 | 2013-03-06 | 株式会社デンソー | Pipe fitting |
US8931305B2 (en) | 2010-03-31 | 2015-01-13 | Denso International America, Inc. | Evaporator unit |
US12018900B2 (en) * | 2021-03-08 | 2024-06-25 | Rheem Manufacturing Company | Systems and methods for heat exchange |
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Also Published As
Publication number | Publication date |
---|---|
JP4196774B2 (en) | 2008-12-17 |
US7621320B2 (en) | 2009-11-24 |
DE102004036460A1 (en) | 2005-05-25 |
US20070107887A1 (en) | 2007-05-17 |
JP2005049026A (en) | 2005-02-24 |
DE102004036460B4 (en) | 2018-08-02 |
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