AU2017442329B2 - Heat exchanger, refrigeration cycle apparatus and method of manufacturing heat exchanger - Google Patents
Heat exchanger, refrigeration cycle apparatus and method of manufacturing heat exchanger Download PDFInfo
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- AU2017442329B2 AU2017442329B2 AU2017442329A AU2017442329A AU2017442329B2 AU 2017442329 B2 AU2017442329 B2 AU 2017442329B2 AU 2017442329 A AU2017442329 A AU 2017442329A AU 2017442329 A AU2017442329 A AU 2017442329A AU 2017442329 B2 AU2017442329 B2 AU 2017442329B2
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- tube
- protrusions
- heat exchanger
- protrusion
- heat medium
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Classifications
-
- 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
- F28D7/0016—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 the conduits for one medium or the conduits for both media being bent
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
- B21C37/00—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
- B21C37/06—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
- B21C37/15—Making tubes of special shape; Making tube fittings
- B21C37/156—Making tubes with wall irregularities
- B21C37/158—Protrusions, e.g. dimples
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D53/00—Making other particular articles
- B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
- B21D53/06—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of metal tubes
-
- 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
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
- F28F1/424—Means comprising outside portions integral with inside portions
- F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/09—Improving heat transfers
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/007—Condensers
-
- 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
- F28D7/02—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 being helically coiled
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2210/00—Heat exchange conduits
- F28F2210/06—Heat exchange conduits having walls comprising obliquely extending corrugations, e.g. in the form of threads
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Shaping Metal By Deep-Drawing, Or The Like (AREA)
Abstract
A heat exchanger relating to the present invention has: a first pipe, in which a first heat medium flows; and a second pipe, which is wound around the first pipe, and in which a second heat medium flows. The first pipe has, on the inner surface thereof, a plurality of protrusions, which are formed in spiral lines in the direction in which the first heat medium flows in the first pipe, and the protrusions formed in each line are disposed at unequal intervals.
Description
Title of Invention HEAT EXCHANGER, REFRIGERATION CYCLE APPARATUS AND METHOD OF
Technical Field
[0001]
The present disclosure relates to a heat exchanger including a first tube
and a second tube wound around the first tube, a refrigeration cycle apparatus
including the heat exchanger, and a method of manufacturing the heat
exchanger.
Background Art
[0002]
Conventionally, there has been a heat exchanger including a first tube in which a
path through which a first heat medium flows is formed, and a second tube in which a
path through which a second heat medium flows is formed, the second tube being
wound around the outer periphery of the first tube. In such a heat exchanger, heat is
exchanged between the first heat medium flowing in the first tube and the second heat
medium flowing in the second tube. The first tube may be called a core tube. The
second tube may be called an external tube. One example of the first heat medium is
water or antifreeze. One example of the second heat medium is refrigerant.
[0003]
As such a heat exchanger, as described in Patent Literature 1, there has been
proposed "a heat exchanger including a core tube having a plurality of protrusions on
the inside of the core tube, formed by pressing the outside of the core tube, and a
winding tube wound around the outside of the core tube".
[0004]
The heat exchanger of Patent Literature 1 includes the core tube having the
plurality of protrusions on the inside of the core tube, formed by pressing the outside of
the core tube. By making the core tube in such a manner, in the heat exchanger of
Patent Literature 1, a flow of the first heat medium flowing in the core tube is agitated by
the protrusions, thereby improving a heat exchange performance between water as the
first heat medium flowing in the core tube and refrigerant as the second heat medium
flowing in the winding tube.
Citation List Patent Literature
[0005] Patent Literature 1: Japanese Unexamined Patent Application Publication No.
2006-317114
Summary of Invention
Technical Problem
[0006]
In the heat exchanger of Patent Literature 1, when forming the plurality of
protrusions on the inside of the core tube by pressing the outside of the core tube, as a
method of forming the plurality of protrusions, a gearwheel-like jig is used, and teeth
parts of the gearwheel-like jig are pressed against the outside of the core tube to form
the inside protrusions in a spiral manner. In the following description, the gearwheel
like jig is simply referred to as the jig. Moreover, for a further improvement of the heat
exchange performance by adding the protrusions, it is possible to provide a large
number of inside protrusions in a spiral direction with the use of a plurality of jigs. The
plurality of protrusions are provided by independently operating each of the plurality of
jigs.
[0007]
In the case where the protrusions are formed by the plurality of jigs, the positional
relationship between the protrusions to be added by the respective gearwheels is
determined by the phase difference between the respective gearwheels. Depending
on the phase difference between the respective jigs, the protrusions to be added by one
jig and the protrusions to be added by other jig may be aligned with each other in a tube
axis direction. A flow of the first heat medium is agitated by the protrusions provided
on an upstream side of the flow of the first heat medium, thereby improving the heat exchange performance. On the other hand, at the protrusions provided on a downstream side of the flow of the first heat medium, the flow rate is reduced, the agitation effect is decreased, and the effect of improving the heat exchange performance by the protrusions is decreased.
[0008] Considering the above problem in the background, it is desirable to provide a
heat exchanger configured to improve the heat exchange performance by avoiding a
decrease in the agitation effect of the plurality of protrusions, a refrigeration cycle
apparatus including the heat exchanger, and a method of manufacturing the heat
exchanger.
Solution to Problem
[0009]
[0010] A heat exchanger of an embodiment of the present disclosure includes: a
first tube through which a first heat medium flows; and a second tube through which
a second heat medium flows, the second tube being wound around the first tube, the
first tube having a plurality of protrusions protruding inside of the first tube, the
plurality of protrusions being provided in a plurality of streaks being provided in a
spiral manner in a direction to which the first heat medium of the first path flows in
the first tube, one streak of the plurality of streaks including the plurality of
protrusions each being arranged at unequal spacing intervals.
In another embodiment, the present disclosure provides a method of
manufacturing a heat exchanger includes a first tube in which a first path through which
a first heat medium flows is formed, and a second tube in which a second path through
which a second heat medium flows is formed, the second tube being wound around the
first tube. The method comprises providing a plurality of protrusions protruding inside of
the first tube in a plurality of streaks in a spiral manner by pressing an outside of the first
tube using a plurality of jigs each having a gearwheel on which a plurality of protruding
parts are provided, wherein, in each of the jigs, the plurality of protruding parts are
arranged at unequal spacing intervals on the gearwheel to provide each of the plurality
of protrusions at unequal spacing intervals.
Advantageous Effects of Invention
[0011]
According to the heat exchanger of the embodiment of the present disclosure, in a projection in which the first tube is projected in the tube axis direction, adjacent
protrusions do not overlap, and therefore the flow rate is not reduced even at the
protrusions provided on the downstream side of the flow of the first heat medium, and
the heat exchange performance is improved.
Brief Description of Drawings
[0012]
[Fig. 1] Fig. 1 is a schematic configuration diagram schematically illustrating an
example of a circuit configuration of a refrigeration cycle apparatus including a heat
exchanger according to Embodiment 1 of the present disclosure.
[Fig. 2] Fig. 2 is a perspective diagram schematically illustrating a configuration of
the heat exchanger according to Embodiment 1 of the present disclosure.
[Fig. 3] Fig. 3 is an explanatory diagram for explaining an example of providing
protrusions on a first tube of the heat exchanger according to Embodiment 1 of the
present disclosure.
[Fig. 4] Fig. 4 is an explanatory diagram for explaining a conventional example of
providing protrusions on the first tube as a comparative example.
[Fig. 5] Fig. 5 is an explanatory diagram for explaining the first tube having the
protrusions provided by the method of Fig. 3.
[Fig. 6] Fig. 6 is an explanatory diagram for explaining the first tube having the
protrusions provided by the method of Fig. 4.
[Fig. 7] Fig. 7 is an explanatory diagram for explaining other example of providing
protrusions on the first tube according to Embodiment 1 of the present disclosure.
[Fig. 8] Fig. 8 is an explanatory diagram for explaining the spacing interval of the
protrusions of the first tube of the heat exchanger according to Embodiment 1 of the
present disclosure.
[Fig. 9] Fig. 9 is an explanatory diagram for explaining the spacing interval of the
protrusions of the first tube of the heat exchanger according to Embodiment 1 of the
present disclosure.
[Fig. 10] Fig. 10 is an explanatory diagram for explaining a shape of the first tube
of the heat exchanger according to Embodiment 2 of the present disclosure.
[Fig. 11] Fig. 11 is an explanatory diagram for explaining a shape of the first tube
of the heat exchanger according to Embodiment 3 of the present disclosure.
Description of Embodiments
[0013] Embodiments of the present disclosure will be described hereinafter with
reference to the drawings as appropriate. In the following drawings including Fig. 1, the relationship in size among component parts may be different from the actual
relationship. In the following drawings including Fig. 1, the component parts labelled
with the same reference signs are the same component parts or equivalent, and the
same can be said for the entire description. Moreover, the forms of the components
stated in the full description are merely examples, and not what limits the scope of
matters in present disclosure.
[0014]
Embodiment 1
Fig. 1 is a schematic configuration diagram schematically illustrating an example
of a circuit configuration of a refrigeration cycle apparatus 200 including a heat
exchanger 100 according to Embodiment 1 of the present disclosure. The refrigeration
cycle apparatus 200 will be described with reference to Fig. 1.
In Embodiment 1, the description is given on an assumption that a first heat
medium is water, and a second heat medium is refrigerant.
[0015]
[Overall Configuration of Refrigeration Cycle Apparatus 200]
The refrigeration cycle apparatus 200 has a refrigerant circuit Al, and a heat
medium circuit A2. The refrigerant circuit Al and the heat medium circuit A2 are
thermally connected through the heat exchanger 100. The heat medium circuit A2 is also connected to a water supply circuit A3 through a hot water storage tank 207. The water supply circuit A3 is connected to a hot water supply utility unit U, and configured to supply hot water to the hot water supply utility unit U. Examples of the hot water supply utility unit U include at least one of various loads that require hot water, such as a faucet and a bath of a household. The water supply circuit A3 is connected to a water pipe or other pipe, and is configured to be able to supply water.
[0016] Refrigerant circulates in the refrigerant circuit Al through a refrigerant tube 20A.
Carbon dioxide can be used as the refrigerant. The refrigerant circuit Al is configured
to include a compressor 201 for compressing the refrigerant, the heat exchanger 100
functioning as a condenser, an expansion device 202, and a heat exchanger 203
functioning as an evaporator.
[0017]
The compressor 201 compresses the refrigerant. The refrigerant compressed
by the compressor 201 is discharged from the compressor 201 and sent to the heat
exchanger 100. The compressor 201 can be made of, for example, a rotary
compressor, a scroll compressor, a screw compressor, or a reciprocating compressor.
[0018] The heat exchanger 100 functions as a condenser, exchanges heat between
high-temperature, high-pressure refrigerant flowing in the refrigerant circuit Al and
water flowing in the heat medium circuit A2, heats the water, and condenses the
refrigerant. The heat exchanger 100 is a water-refrigerant heat exchanger that
exchanges heat between water and refrigerant. The heat exchanger will be described
in detail later.
The heat exchanger 100 is an equivalent of a heat exchanger of the present
disclosure.
[0019]
The expansion device 202 expands the refrigerant flowing out of the heat
exchanger 100 and reduces the pressure. The expansion device 202 maybe made of, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant. As the expansion device 202, not only the electric expansion valve, but also a mechanical expansion valve using a diaphragm for a pressure receiving part, a capillary tube or the like is applicable.
[0020]
The heat exchanger 203 functions as an evaporator, exchanges heat between
low-temperature, low-pressure refrigerant discharged from the expansion device 202
and air supplied by a fan 203A attached to the heat exchanger 203, and evaporates
low-temperature, low-pressure liquid refrigerant or two-phase refrigerant. The heat
exchanger 203 can be made of, for example, a fin-and-tube type heat exchanger, a
micro channel heat exchanger, or a heat pipe type heat exchanger.
[0021]
The water circulates in the heat medium circuit A2 through a heat medium tube
A. The heat medium circuit A2 is configured to include the heat exchanger 100 and
a pump 205 for conveying the water.
[0022]
Moreover, the refrigeration cycle apparatus 200 includes a controller 60 for
generally controlling the entire refrigeration cycle apparatus 200. The controller 60
controls a driving frequency of the compressor 201. Further, the controller 60 controls
the opening degree of the expansion device 202, according to the operation state.
Furthermore, the controller 60 controls driving of the fan 203A and the pump 205. That
is, based on an operation instruction, the controller 60 uses information sent from each
of temperature sensors (not shown) and each of pressure sensors (not shown), and
controls actuators of the compressor 201, the expansion device 202, the fan 203A, the
pump 205, etc.
[0023]
Each of functional units included in the controller 60 is made of dedicated
hardware, or a micro processing unit (MPU) for executing a program stored in a
memory.
[0024]
[Configuration of Heat Exchanger 100]
Fig. 2 is a perspective diagram schematically illustrating the configuration of the
heat exchanger 100.
The heat exchanger 100 has a first tube 1 in which a first path FP1 through which
water as the first heat medium flows, and a second tube 2 in which a second path FP2
through which refrigerant as the second heat medium flows is formed. The second
tube 2 is wound in one turn or a plurality of turns around the outer periphery of the first
tube 1 and in contact with the first tube 1. The first tube 1 makes a part of the heat
medium tube 10A. The second tube 2 makes a part of the refrigerant tube 20A.
[0025]
In the first tube 1, a water inlet 1a and a water outlet 1b communicating with the
first path FP1 are provided. In the second tube 2, a refrigerant inlet 2a and a
refrigerant outlet 2b communicating with the second path FP2 are provided.
The heat exchanger 100 can be connected to the refrigerant circuit Al and the
heat medium circuit A2 such that the direction of the water flowing through the first tube
1 and the direction of the refrigerant flowing through the second tube 2 are opposite.
Hence, the heat exchange efficiency between the heat medium and the refrigerant is
improved.
[0026]
[Operation of Refrigeration Cycle Apparatus 200]
Here, returning to Fig. 1, an operation of the refrigeration cycle apparatus 200 will
be described.
The refrigeration cycle apparatus 200 can perform a hot water supply operation,
based on an instruction from the load side.
The operations of the actuators are controlled by the controller 60.
[0027]
The low-temperature, low-pressure refrigerant is compressed by the compressor
201 to be high-temperature, high-pressure gas refrigerant, and is discharged from the
compressor 201. The high-temperature, high-pressure gas refrigerant discharged from
the compressor 201 flows into the heat exchanger 100. The refrigerant that has flowed
into the heat exchanger 100 circulates in the second tube 2, and exchanges heat with the water flowing in the first tube 1. At this time, the refrigerant is condensed to be low temperature, high-pressure liquid refrigerant, and flows out of the heat exchanger 100.
In the case where carbon dioxide is used as the refrigerant, the refrigerant undergoes a
temperature change while in a supercritical state.
On the other hand, the water that has flowed into the first tube 1 is heated by the
refrigerant flowing in the second tube 2, and is supplied to the load side.
[0028]
The low-temperature, high-pressure liquid refrigerant flowing out of the heat
exchanger 100 is made low-temperature, low-pressure liquid refrigerant or two-phase
refrigerant by the expansion device 202, and flows into the heat exchanger 203. The
refrigerant that has flowed into the heat exchanger 203 exchanges heat with the air
supplied by the fan 203A attached to the heat exchanger 203, becomes low
temperature, low-pressure gas refrigerant, and flows out of the heat exchanger 203.
The refrigerant that has flowed out of the heat exchanger 203 is sucked into the
compressor 201 again.
[0029]
In Fig. 1, the case where the refrigerant flows in a fixed direction in the refrigerant
circuit Al is shown as an example, but a path switching device may be provided on the
discharge side of the compressor 201 to make it possible to reverse the flow of the
refrigerant. In the case where the path switching device is provided, the heat
exchanger 100 also functions as an evaporator, and the heat exchanger 203 also
functions as a condenser. As the path switching device, it is possible to use, for
example, a combination of two-way valves, a combination of three-way valves, or a
four-way valve.
[0030]
As the refrigerant to be used in the refrigeration cycle apparatus 200, carbon
dioxide is desirable, but the refrigerant is not necessarily limited to carbon dioxide.
Other than carbon dioxide, it is possible to use natural refrigerant such as hydrocarbons
or helium, alternative refrigerant containing no chlorine, such as HFC410A, HFC407C or
HFC404A, or fluorocarbon refrigerant used in existing products, such as R22 or R134a.
[0031]
[Detailed Configuration of Heat Exchanger 100]
Fig. 3 is an explanatory diagram for explaining an example of providing
protrusions on the first tube. Fig. 4 is an explanatory diagram for explaining a
conventional example of providing protrusions on the first tube as a comparative
example. The first tube will be described in detail based on Fig. 3 in comparison to the
first tube of Fig. 4. In the conventional example of Fig. 4, "X" is added to the end of
reference signs for distinguishing from the first tube 1. A case where two streaks of
protrusions are formed on the first tube using two jigs is described for convenience. In
Figs. 3 and 4, Fig. 3(a) and Fig. 4(a) each schematically illustrate a state of the first tube
seen from a side, and Fig. 3(b) and Fig. 4(b) each schematically illustrate a projection in
which the first tube is projected in the tube axis direction. Further, in Figs. 3 and 4, the
tube axis is shown as a tube axis CL.
[0032] As shown in Fig. 3, when forming two streaks of protrusions 3 on the first tube 1,
a plurality of gearwheel-like jigs are used. One of the gearwheel-like jigs is called a jig
6a, and another is called a jig 6b. The protrusions 3 to be formed by the jig 6a are
called protrusions 3a, and the protrusions 3 to be formed by the jig 6b are called
protrusions 3b. In the state shown in Fig. 3, it is assumed that the protrusions 3a
formed by the jig 6a are placed on the upstream side of the flow of the first heat
medium, and the protrusions 3b formed by the jig 6b are provided on the downstream
side of the flow of the first heat medium.
[0033] The jig 6a has a gearwheel 9A. In the gearwheel 9A, a plurality of protruding
parts 9a for forming the protrusions 3a are provided at mutually different spacing
intervals. When an outside of the first tube 1 is pressed by the jig 6a, an inside of the
first tube 1 protrudes due to the protruding parts 9a of the gearwheel 9A, and a plurality
of protrusions 3a are formed as a streak in a spiral direction. The spacing intervals
between the plurality of protrusions 3a formed by the jig 6a are shown as a pitch 5a, a
pitch 5b, and a pitch 5c.
[0034]
Similarly, the jig 6b has a gearwheel 9B. In the gearwheel 9B, a plurality of protruding parts 9b for forming the protrusions 3b are provided at mutually different
spacing intervals. When the outside of the first tube 1 is pressed by the jig 6b, the
inside of the first tube 1 protrudes due to the protruding parts 9b of the gearwheel 9B,
and a plurality of protrusions 3b are formed as another streak in a spiral direction. The
spacing intervals between the plurality of protrusions 3b formed by the jig 6b are shown
as a pitch 5d, a pitch 5e, and a pitch 5f.
[0035] As shown in Fig. 3, the pitch 5a, the pitch 5b and the pitch 5c of the protrusions
3a are of different lengths. That is, the plurality of protrusions 3a are provided at
unequal spacing intervals.
Similarly, the pitch 5d, the pitch 5e and the pitch 5f of the protrusions 3b are of
different lengths. That is, the plurality of protrusions 3b are provided at unequal
spacing intervals.
Here, the unequal spacing intervals mean that two or more lengths are present as
the spacing intervals between the protrusions 3 formed by each of the jig 6a and the jig
6b.
[0036] The positional relationship between the protrusion 3a and the protrusion 3b is
determined by the phase difference between the gearwheel 9A of the jig 6a and the
gearwheel 9B of the jig 6b. That is, in the jig 6a, the plurality of protruding parts 9a are
provided at unequal spacing intervals, and therefore the plurality of protrusions 3a to be
formed also have unequal spacing intervals. Similarly, in the jig 6b, the plurality of
protruding parts 9b are provided at unequal spacing intervals, and therefore the plurality
of protrusions 3b to be formed also have unequal spacing intervals. Hence, the flow of
the first heat medium is agitated by both the protrusions 3a and the protrusions 3b,
thereby improving the heat exchange performance.
[0037] On the other hand, in the conventional example of Fig. 4, when forming two streaks of protrusions 3X on a first tube 1X, a jig 6aX and a jig 6bX are used, but the spacing interval between protruding parts 9aX of a gearwheel 9AX of the jig 6aX and the spacing interval between protruding parts 9bX of a gearwheel 9BX of the jig 6bX are constant. Moreover, as shown in Fig. 4, the spacing intervals between protrusions 3aX and protrusions 3bX adjacent to each other in a tube axis direction are equal. Thus, as shown in Fig. 4, a pitch 5aX, a pitch 5bX and a pitch 5cX of the protrusions 3aX are of the same length. That is, the plurality of protrusions 3aX are provided at equal spacing intervals. Similarly, a pitch 5dX, a pitch 5eX and a pitch 5fX of the protrusions 3bX are of the same length. That is, the plurality of protrusions 3bX are provided at equal spacing intervals.
[0038] That is, in the jig 6aX, the plurality of protruding parts 9aX are provided at equal
spacing intervals, and therefore the plurality of protrusions 3aX to be formed also have
equal spacing intervals. Similarly, in the jig 6bX, the plurality of protruding parts 9bX
are provided at equal spacing intervals, and therefore the plurality of protrusions 3bX to
be formed also have equal spacing intervals. Hence, the protrusions 3aX and the
protrusions 3bX are all arranged in alignment in the tube axis direction. In this case, the effect of improving the heat exchange performance by the protrusions 3bX provided
on the downstream side is decreased. This is because, at the protrusions 3aX, the
flow of the first heat medium is agitated and the heat exchange performance is
improved, but, at the protrusions 3bX, the flow rate is reduced and the effect of agitating
the flow of the first heat medium is decreased.
[0039]
[Method of Manufacturing First Tube 1]
A method of manufacturing the first tube 1 will be described based on Fig. 3 in
comparison to the conventional example of Fig. 4. Here, a case where two streaks of
protrusions are formed on the first tube using two jigs is also described for convenience.
[0040]
As a method of forming the plurality of protrusions 3 on the inside of the first tube
1, as shown in Fig. 3, the jig 6a having the gearwheel 9A and the jig 6B having the gearwheel 9B are used. In the gearwheel 9A, the plurality of protruding parts 9a are provided. In the gearwheel 9B, the plurality of protruding parts 9b are provided. The protruding parts 9a are pressed against an outer wall of the first tube 1 to form one streak of protrusions 3a in a spiral manner on the inside of the first tube 1. Similarly, the protruding parts 9b are pressed against the outer wall of the first tube 1 to form one streak of protrusions 3b in a spiral manner on the inside of the first tube 1. That is, two streaks of the plurality of protrusions 3 are provided in a spiral manner on the first tube
1.
[0041]
The jig 6a and the jig 6b are rotated independently of each other, and the
protruding parts 9a and the protruding parts 9b provided intermittently are successively
pressed against the outside of the first tube 1. Consequently, the two streaks of
protrusions 3 are formed in a spiral manner on the first tube 1. Since the spacing
intervals between each of the protruding parts 9a and the spacing intervals between
each of the protruding parts 9b are unequal spacing intervals, the protrusions 3a to be
formed by the protruding parts 9a and the protrusions 3b to be formed by the protruding
parts 9b also have unequal spacing intervals.
[0042]
Whereas, in the conventional example shown in Fig. 4, although the two streaks
of protrusions 3X are formed in a spiral manner on the first tube 1X by rotating each of
the jig 6aX and the jig 6bX, the spacing intervals between each of the protruding parts
9aX and the spacing intervals between each of the protruding parts 9bX are regular
spacing intervals, that is, equal spacing intervals. Therefore, the protrusions 3aX to be
formed by the protruding parts 9aX and the protrusions 3bX to be formed by the
protruding parts 9bX also have regular spacing intervals, that is, equal spacing intervals.
[0043]
Fig. 5 is an explanatory diagram for explaining the first tube 1 having the
protrusions 3 formed by the method of Fig. 3. Fig. 6 is an explanatory diagram for
explaining the first tube 1X having the protrusions 3X formed by the method of Fig. 4.
The first tube will be described in detail based on Fig. 5 in comparison to the first tube of
Fig. 6. In Figs. 5 and 6, Fig. 5(a) and Fig. 6(a) each schematically illustrate a state of the first tube seen from a side, and Fig. 5(b) and Fig. 6(b) each schematically illustrate a projection in which the first tube is projected in the tube axis direction. In Figs. 5 and 6, the tube axis is shown as the tube axis CL.
[0044]
As shown in Fig. 5, the protrusions 3a are provided at unequal spacing intervals
on the first tube 1. That is, the pitch 5a, the pitch 5b and the pitch 5c of the protrusions
3a are of different lengths.
Similarly, the protrusions 3b are provided at unequal spacing intervals on the first
tube 1. That is, the pitch 5d, the pitch 5e and the pitch 5f of the protrusions 3a are of
different lengths.
Therefore, even when the spacing intervals between the protrusion 3a and the
protrusion 3b are equal, the protrusion 3a and the protrusion 3b adjacent to each other
in the tube axis direction are not aligned with each other in the tube axis direction.
[0045]
As shown in Fig. 5, the topmost protrusion 3a-1 on the topmost level in the
drawing paper is provided on a straight line Lal, the protrusion 3a-2 on the second level
from the top in the drawing paper is provided on a straight line La2, the protrusion 3a-3
on the third level from the top in the drawing paper is provided on a straight line La3,
and the protrusion 3a-4 on the lowermost level in the drawing paper is provided on a
straight line La4.
Each of the straight lines Lal to La4 is a straight line parallel to the tube axis CL.
In the following description, the straight lines Lal to La4 may be collectively referred to
as straight lines La. The fact that the protrusion 3a is provided on the straight line La
parallel to the tube axis CL means that a portion including the top of the protrusion 3a
overlaps the straight line La.
[0046]
Similarly, the protrusion 3b-1 on the topmost level in the drawing paper is
provided on a straight line Lbl, the protrusion 3b-2 on the second level from the top in
the drawing paper is provided on the straight line La2, a protrusion 3b-3 on the third level from the top in the drawing paper is provided on a straight line Lb3, and the protrusion 3b-4 on the lowermost level in the drawing paper is provided on a straight line Lb4.
Each of the straight lines Lb1-Lb4 is a straight line parallel to the tube axis CL.
In the following description, the straight lines Lbl to Lb4 may be collectively referred to
as straight lines Lb. The fact that the protrusion 3b is provided on the straight line Lb
parallel to the tube axis CL means that a portion including the top of the protrusion 3b
overlaps the straight line Lb.
[0047]
That is, the protrusion 3a-1 and the protrusion 3b-1 are provided on different
straight lines parallel to the tube axis CL, and are not aligned with each other in the tube
axis direction, and similarly the protrusion 3a-2 and the protrusion 3b-2 are provided on
different straight lines parallel to the tube axis CL, and are not aligned with each other in
the tube axis direction. Similarly, the protrusion 3a-3 and the protrusion 3b-3 are
provided on different straight lines parallel to the tube axis CL, and are not aligned with
each other in the tube axis direction. Similarly, the protrusion 3a-4 and the protrusion
3b-4 are provided on different straight lines parallel to the tube axis CL, and are not
aligned with each other in the tube axis direction.
[0048]
Therefore, even at the protrusions 3b provided on the downstream side of the
flow of the first heat medium, the flow rate is not decreased, and the effect of agitating
the flow of the first heat medium is not decreased. Hence, the flow of the first heat
medium is agitated with both the protrusions 3a and the protrusions 3b, and the effect of
improving the heat exchange performance is not decreased.
[0049]
On the other hand, in the conventional example of Fig. 6, the protrusions 3aX are
provided at regular spacing intervals on the first tube 1X. That is, the pitch 5aX, the
pitch 5bX and the pitch 5cX of the protrusions 3aX are of the same length.
Similarly, the protrusions 3bX are provided at regular spacing intervals on the first
tube 1X. That is, the pitch 5dX, the pitch 5eX and the pitch 5fX of the protrusions 3aX are of the same length.
Therefore, when the spacing intervals between the protrusions 3aX and the protrusions 3bX are equal, the protrusion 3aX and the protrusion 3bX adjacent to each
other in the tube axis direction are aligned with each other in the tube axis direction at
some phase difference.
[0050] As shown in Fig. 6, the protrusion 3a-5X on the lowermost level in the drawing
paper is provided on a straight line La5.
Like the straight lines Lal to La4, the straight line La5 is a straight line parallel to
the tube axis CL. The fact that the protrusion 3aX is provided on the straight line La
parallel to the tube axis CL means that a portion including the top of the protrusion 3aX
overlaps the straight line La. The protrusion 3a-4X is provided on the fourth level from
the top in the drawing paper in Fig. 6.
[0051] Similarly, the protrusion 3b-5X on the lowermost level in the drawing paper is
provided on the straight line Lb4.
Like the straight lines Lbl to Lb4, the straight line Lb5 is a straight line parallel to
the tube axis CL. The fact that the protrusion 3bX is provided on the straight line Lb
parallel to the tube axis CL means that a portion including the top of the protrusion 3bX
overlaps the straight line Lb. The protrusion 3b-4X is provided on the fourth level from
the top in the drawing paper in Fig. 6.
[0052] Here, as shown in Fig. 6, in the state seen from a side, the straight line Lal and
the straight line Lbl overlap in the tube axis direction, and are the same straight line.
Similarly, the straight line La2 and the straight line Lb2 overlap in the tube axis direction,
and are the same straight line. Similarly, the straight line La3 and the straight line Lb3
overlap in the tube axis direction, and are the same straight line. Similarly, the straight
line La4 and the straight line Lb4 overlap in the tube axis direction, and are the same
straight line. Similarly, the straight line La5 and the straight line Lb5 overlap in the tube
axis direction, and are the same straight line.
[0053] That is, the protrusion 3a-1X and the protrusion 3b-1X are provided on the same
straight line parallel to the tube axis CL, and are aligned with each other in the tube axis
direction. Similarly, the protrusion 3a-2X and the protrusion 3b-2X are provided on the
same straight line parallel to the tube axis CL, and are aligned with each other in the
tube axis direction. Similarly, the protrusion 3a-3X and the protrusion 3b-3X are
provided on the same straight line parallel to the tube axis CL, and are aligned with
each other in the tube axis direction. Similarly, the protrusion 3a-4X and the protrusion
3b-4X are provided on the same straight line parallel to the tube axis CL, and are
aligned with each other in the tube axis direction. Similarly, the protrusion 3a-5X and
the protrusion 3b-5X are provided on the same straight line parallel to the tube axis CL,
and are aligned with each other in the tube axis direction.
[0054] Therefore, as shown by an arrow F in Fig. 6, at the protrusions 3aX provided on
the upstream side of the flow of the first heat medium, the flow of the first heat medium
is agitated, but, at the protrusions 3bX provided on the downstream side of the flow of
the first heat medium, the flow rate is reduced, and the effect of agitating the flow of the
first heat medium is decreased. That is, the effect of improving the heat exchange
performance with the protrusions 3bX provided on the downstream side of the first heat
medium is decreased.
[0055]
[Modified Example of First Tube 1]
Fig. 7 is an explanatory diagram for explaining other example of forming the
protrusions of the first tube. Based on Fig. 7, the effect achieved by the heat
exchanger 100 including the first tube 1 will be described. In Fig. 7, Fig. 7(a)
schematically illustrates a state of the first tube seen from a side, and Fig. 7(b)
schematically illustrates a projection in which the first tube is projected in the tube axis
direction. Here, a case where two streaks of protrusions are formed on the first tube
using two jigs is described for convenience.
[0056]
Like Fig. 3, in the case of forming the plurality of protrusions 3 in a spiral manner, Fig. 7 schematically shows a case where the protrusions 3 were provided at unequal
spacing intervals so that the spacing interval between the protrusions 3a and the
spacing interval between the protrusions 3b to be added by the identical jig 6a and jig
6b, respectively, had two or more different lengths. Although the jig 6a and the jig 6b
had the same configuration, the spacing interval between the protruding parts 9a and
the spacing interval between the protruding parts 9b have different lengths.
[0057] As shown in Fig. 7, when the spacing interval between the protruding parts 9a
and the spacing interval between the protruding parts 9b are unequal spacing intervals,
the protrusions 3a and the protrusions 3b are also provided at unequal spacing intervals
on the first tube 1. Further, although the spacing interval between the protruding parts
9a and the spacing interval between the protruding parts 9b are made different, some
protrusion 3a and protrusion 3b adjacent to each other in the tube axis direction may be
aligned with each other in the tube axis direction. This case is reviewed. In Fig. 7, the case where the protrusion 3a-1 on the topmost level in the drawing paper and the
protrusion 3b-1 on the topmost position in the drawing paper are aligned with each other
in the tube axis direction is shown as an example.
[0058] Also in Fig. 7, the spacing interval between the protruding parts 9a and the
spacing interval between the protruding parts 9b are unequal spacing intervals, and the
spacing interval between the protruding parts 9a and the spacing interval between the
protruding parts 9b are different between that in the jig 6a and that in the jig 6b, and
therefore the protrusions 3 other than the topmost protrusion 3a-1 and the topmost
protrusion 3b-1 are not aligned with each other in the tube axis direction. Hence, even
when some of the protrusions 3 are aligned with each other in the tube axis direction,
deterioration of the heat exchange performance can be reduced and the heat exchange
performance can be improved compared to the first tube of the conventional example.
[0059]
[Detailed Configuration of Jig 6a and Jig 6b]
Fig. 8 and Fig. 9 are explanatory diagrams for explaining the spacing interval
between the protrusions 3 of the first tube 1. Based on Fig. 8 and Fig. 9, a description will be given for the maximum angle and the minimum angle of the spacing intervals
between the protrusions 3a and the spacing intervals between the protrusions 3b
formed by the jigs of the same configuration, namely the jig 6a and the jig 6b, to realize
unequal spacing intervals between the protrusions 3. In Figs. 8 and 9, Fig. 8(a) and Fig. 9(a) each schematically illustrate a state of the first tube seen from a side, and Fig.
8(b) and Fig. 9(b) each schematically illustrate a projection in which the first tube is
projected in the tube axis direction. An angle e between the protrusions 3a is defined
by two straight lines connecting the center of the first tube 1 and the center of each of
target protrusions 3a.
[0060] First, the minimum value of the angle of the spacing interval between the
protrusions 3a to be added to the first tube 1 by the jig 6a, that is, the minimum angle 61
[rad] will be described based on Fig. 8.
In Fig. 8, a case where five protrusions 3a are provided from the topmost level in
the drawing paper to the lowermost level in the drawing paper is shown as an example,
and the protrusions 3a are shown as the protrusion 3a-1, the protrusion 3a-2, the
protrusion 3a-3, the protrusion 3a-4, and the protrusion 3a-5 from the topmost level in
the drawing paper. It is assumed that the protrusion 3a-1, the protrusion 3a-2, the
protrusion 3a-3, the protrusion 3a-4, and the protrusion 3a-5 are provided in the same
shape and the same size.
[0061] Here, as shown in Fig. 8(b), the width of each of the protrusions 3a, that is, the
diameter of the protrusion 3a is defined as a width W. Moreover, as shown in Fig. 8(b), the length equivalent to the width W of the protrusion 3a is defined as a length 3b1.
Further, the inner diameter of the first tube 1 is defined as an inner diameter Dwi.
[0062] Consider a case where, between the protrusion 3a-1 to be added by the jig 6a
and the protrusion 3a-2 to be added subsequently by the jig 6a, the protrusion 3b is added by the jig 6b. In Fig. 8(b), when the protrusions 3a to be added by the jig 6a and the protrusions 3b to be added by the jig 6b are arranged not to overlap each other, the minimum angle 01 between the protrusion 3a-1 and the protrusion 3a-2 is given by
Expression (1).
[0063]
[Expression 1]
W x 2 4xW Dwi x z Dwi
[0064] Next, the maximum value of the angle of the spacing interval between the
protrusions 3a to be added to the first tube 1 by the jig 6a, that is, the maximum angle
02 [rad] will be described based on Fig. 9. The description will be given on an
assumption that n pieces of protrusions 3 per circumferential length are formed on the
first tube 1.
In Fig. 9, a case where four protrusions 3a are provided from the topmost level in
the drawing paper to the lowermost level in the drawing paper is shown as an example,
and the protrusions 3a are shown as the protrusion 3a-1, the protrusion 3a-2, the
protrusion 3a-3, and the protrusion 3a-4 from the topmost level in the drawing paper. It
is assumed that the protrusions 3a-1, the protrusion 3a-2, the protrusion 3a-3, and the
protrusion 3a-4 are provided in the same shape and the same size.
[0065] The distance from the protrusion 3a-1 to the protrusion 3a-2 is determined by the
above-mentioned minimum angle 01. The angle from the protrusion 3a-2 to the
protrusion 3a-3 is made 01 x3/2, that is, 1.5 times of 01 so that the protrusions 3a are
provided at unequal spacing intervals without overlapping from the protrusion 3a-1 to
the protrusion 3a-2. Similarly, the angle from the protrusion 3a-3 to the protrusion 3a-4
is made 01 x4/2. Therefore, the angle from the protrusion 3a-1 to the protrusion 3a-4 is
01 x9/2.
[0066]
Thus, an angle corresponding to the maximum angle 92'[rad] of the maximum
spacing interval when the number of the protrusions 3a are four can be given by
Expression (2).
[0067]
[Expression 2]
0 2 '=2 x - -i- - (2) 2
[0068] In Expression (2), when the number of the protrusions 3 to be provided is n (n>2),
the maximum angle 02 can be given by Expression (3).
[0069]
[Expression 3]
2xW xYi 0 2 = 2 x c- i=2 -- . (3) Dwi
[0070]
From the above, the angle between the protrusions 3 to be added by the jig 6a is within the range of Expression (4).
[0071]
[Expression 4]
4x W Dwi 0 5 2 x r - 2 x W Dwi i J -=2(4)
[0072]
Here, the relationship between the adjacent protrusions 3a and 3b is described
by taking, as an example, the case where the protrusions 3 are formed by two jigs,
namely the jig 6a and the jig 6b. That is, the above description applies to the
relationship between the protrusions to be provided adjacent to each other by the respective jigs when the protrusions are formed using the plurality of jigs. However, although the case where the protrusions 3 are formed by the two jigs is described as an example, the number of the jigs is not particularly limited. Even when two or more jigs are used, a range of the angle between each of the protrusions 3 can be given by
Expression (4). Thus, when the spacing intervals of the protrusions 3 to be added by the same jig are made unequal spacing intervals, the effect of improving the heat
exchange performance can be obtained.
[0073]
[Effects Achieved by Heat Exchanger 100, Refrigeration Cycle Apparatus 200 and
Method of Manufacturing Heat Exchanger]
As described above, in the heat exchanger 100, one protrusion 3a and the
protrusion 3b adjacent to the protrusion 3a are provided on different straight lines
parallel to the tube axis direction, and the adjacent protrusions 3 do not overlap each
other in the projection in which the first tube 1 is projected in the tube axis direction.
Therefore, according to the heat exchanger 100, the phenomenon described in Fig. 6 is
less likely to occur, and the heat exchange performance is improved.
[0074]
According to the heat exchanger 100, since the protrusions 3 provided in one
streak are arranged at unequal spacing intervals, it is possible to arrange the adjacent
protrusions 3 not to overlap each other in the projection in which the first tube 1 is
projected in the tube axis direction.
[0075]
According to the heat exchanger 100, since the anglee between the protrusions
3 is arranged to be within the range of Expression (4) described above, it is possible to
arrange the adjacent protrusions 3 not to overlap each other in the projection in which
the first tube 1 is projected in the tube axis direction.
[0076]
According to the refrigeration cycle apparatus 200, since the above-described
heat exchanger is provided as a condenser, an improvement in the heat exchange
performance of the condenser can be expected.
[0077] In the method of manufacturing the heat exchanger 100, the protrusions 3a are
formed at unequal spacing intervals by arranging each of the plurality of protruding parts
9a of the jig 6a at unequal spacing intervals, and the protrusions 3b are formed at
unequal spacing intervals by arranging each of the plurality of protruding parts 9b of the
jig 6b at unequal spacing intervals. Thus, according to the method of manufacturing
the heat exchanger 100, it is possible to manufacture the heat exchanger 100 without
using a special jig and going through a special process.
[0078]
Embodiment 2
Fig. 10 is an explanatory diagram for explaining a shape of a first tube 1A of a
heat exchanger of Embodiment 2 of the present disclosure. Based on Fig. 10, the
shape of the first tube 1A of the heat exchanger of Embodiment 2 will be described.
In Embodiment 2, differences from Embodiment 1 will be mainly described, and
the same parts as those in Embodiment 1 will be labelled with the same reference signs
and description thereof will be omitted. In Fig. 10, Fig. 10(a) schematically illustrates a
state of the first tube seen from a side, and Fig. 10(b) schematically illustrates a
projection in which the first tube is projected in the tube axis direction.
[0079]
In Embodiment 1, the case where the first tube 1 is a circular tube having no
unevenness on the outer circumferential surface is described as an example, whereas,
in Embodiment 2, a case where the first tube 1A is a corrugated tube having a single
streak of spiral groove 35 provided on the outer circumferential surface is described as
an example. When providing the protrusions 3 on the first tube 1A, as shown in Fig.
, the protrusions 3 are provided at portions other than the spiral groove 35. The
second tube is wound around the spiral groove 35 of the first tube 1A.
[0080] Thus, by making the first tube 1A by the corrugated tube, it is possible to further
promote a turbulent flow of the refrigerant inside the first tube 1A. Hence, the heat
exchange performance can be further improved compared to the case where the protrusions are added to the first tube 1 as described in Embodiment 1.
[0081] Embodiment 3
Fig. 11 is an explanatory diagram for explaining a shape of a first tube 1B of a
heat exchanger of Embodiment 3 of the present disclosure. Based on Fig. 11, the
shape of the first tube 1B of the heat exchanger according to Embodiment 3 will be
described.
In Embodiment 3, differences from Embodiment 1 will be mainly described, and
the same parts as those in Embodiment 1 will be labelled with the same reference
signs, and description thereof will be omitted. In Fig. 11, Fig. 11(a) schematically
illustrates a state of the first tube seen from a side, and Fig. 11(b) schematically
illustrates a projection in which the first tube is projected in the tube axis direction.
[0082] In Embodiment 1, the case where the first tube 1 is a circular tube having no
unevenness on the outer circumferential surface is described as an example, whereas,
in Embodiment 3, a case where the first tube 1B is a torsion tube having a peak portion
a and a valley portion 30b is described as an example. The peak portion 30a is a
portion that protrudes in a radially expanding direction in which the diameter of the first
tube 1B expands, and is formed in a spiral manner in a direction to which the first heat
medium flows in the first path FP1. The valley portion 30b is a portion in which an
outer diameter of the first tube is smaller than in a portion where the peak portion 30a is
formed, and around which the second tube is to be wound, and is formed in a spiral
manner along the peak portion 30a. When providing the protrusions 3 on the first tube
1B, as shown in Fig. 11, the protrusions 3 are provided in the valley portion 30b. That
is, the protrusions 3 are provided in the spiral direction that is the direction in which the
valley portion 30b is formed. The second tube is wound around the first tube 1B by
being fitted in the valley portion 30b.
[0083] Thus, by making the first tube 1B by the torsion tube, it is possible to further
promote a turbulent flow of the refrigerant inside the first tube 1B. Moreover, the contact area between the first tube 1B and the second tube can be increased. Hence, the heat exchange performance can be further improved compared to the case where the protrusions are added to the first tube 1 as described in Embodiment 1.
[0084] Although the present disclosure is described by separate embodiments, specific
configurations are not limited to the described embodiments, and can be modified within
a range not departing from the gist of the invention.
[0085] It is to be understood that, if any prior art publication is referred to herein, such
reference does not constitute an admission that the publication forms a part of the
common general knowledge in the art, in Australia or any other country.
In the claims which follow and in the preceding description of the invention,
except where the context requires otherwise due to express language or necessary
implication, the word "comprise" or variations such as "comprises" or "comprising" is
used in an inclusive sense, i.e. to specify the presence of the stated features but not to
preclude the presence or addition of further features in various embodiments of the
invention.
Reference Signs List
[0086] 1 first tube, 1A first tube, 1B first tube, 1X first tube, la
inlet, lb outlet, 2 second tube, 2a inlet, 2b outlet, 3 protrusion, 3X protrusion, 3a protrusion, 3a-1 protrusion, 3a-1X protrusion,3a-2 protrusion, 3a-2X protrusion,3a-3 protrusion, 3a-3X protrusion, 3a-4 protrusion, 3a4X protrusion, 3a-5 protrusion, 3a-5X protrusion,3aX protrusion, 3b
protrusion, 3b-1 protrusion, 3b-1X protrusion,3b-2 protrusion, 3b-2X
protrusion, 3b-3 protrusion, 3b-3X protrusion,3b-4 protrusion, 3b-4X
protrusion, 3b-5X protrusion,3b-5X4 protrusion, 3bX protrusion, 5a pitch, 5aX pitch, 5b pitch, 5bX pitch, 5c pitch, 5cX pitch, 5d pitch, 5dX
pitch, 5e pitch, 5eX pitch, 5f pitch, 5fX pitch, 6B jig, 6a jig, 6aX
jig, 6b jig, 6bX jig, 9A gearwheel, 9AX gearwheel, 9B gearwheel,
9BX gearwheel, 9a protruding part, 9aX protruding part, 9b protruding part, 9bX protruding part, 10A heat medium tube, 20A refrigerant
tube, 30a peakportion, 30b valley portion, 35 spiral groove, 60
controller, 100 heat exchanger, 200 refrigeration cycle apparatus, 201
compressor, 202 expansion device, 203 heat exchanger, 203A fan, 205
pump,207 hot water storage tank, Al refrigerant circuit, A2 heat medium
circuit, A3 water supply circuit, FP1 first path, FP2 second path, U hot water supply utility part.
Claims (7)
- [Claim 1] A heat exchanger comprising:a first tube through which a first heat medium flows; anda second tube through which a second heat medium flows, the second tube beingwound around the first tube,the first tube having a plurality of protrusions protruding inside of the first tube,the plurality of protrusions being provided in a plurality of streaks being providedin a spiral manner in a direction to which the first heat medium of the first path flows inthe first tube,one streak of the plurality of streaks including the plurality of protrusions eachbeing arranged at unequal spacing intervals.
- [Claim 2]The heat exchanger of claim 1, wherein, from among the plurality of protrusionsprovided in the one streak and the plurality of protrusions provided in an other streak ofthe plurality of streaks, two protrusions adjacent to each other in a tube axis direction ofthe first tube are each provided on one of different straight lines being in parallel to thetube axis direction.
- [Claim 3]The heat exchanger of claim 1 or 2, wherein, in a projection in which the first tubeis projected in the tube axis direction,an angle 0 between the protrusions is arranged to fall within a range given byexpression (5),[Expression 5]X 4 xWW 4 x 2 x 7r - 2 x i 2 Dwi Dwi where W is a width of each of the plurality of protrusions,Dwi is an inner diameter of the first tube, andn is the number of the plurality of protrusions to be provided per circumferentiallength of the first tube.
- [Claim 4]The heat exchanger of any one of claims 1 to 3, wherein the first tube is acorrugated tube.
- [Claim 5]The heat exchanger of any one of claims 1 to 3, whereinthe first tube includes:a peak portion protruding in a radially expanding direction in which a diameter ofthe first tube expands; anda valley portion in which an outer diameter of the first tube is smaller than in aportion where the peak portion is formed, and around which the second tube is wound,the peak portion being formed in a spiral manner in a direction to which the firstheat medium of the first path flows,the valley portion being formed in a spiral manner along the peak portion,the plurality of protrusions being provided in a spiral direction that is the directionin which the valley portion is formed.
- [Claim 6]A refrigeration cycle apparatus comprising the heat exchanger of any one ofclaims 1 to 5 as a condenser, wherein, in the heat exchanger, the first heat mediumflowing through a first path of the first tube constituting the heat exchanger is heated bythe second heat medium flowing through a second path of the second tube constitutingthe heat exchanger.
- [Claim 7]A method of manufacturing a heat exchanger including: a first tube in which a firstpath through which a first heat medium flows is formed; and a second tube in which asecond path through which a second heat medium flows is formed, the second tubebeing wound around the first tube,the method comprising providing a plurality of protrusions protruding inside of thefirst tube in a plurality of streaks in a spiral manner by pressing an outside of the firsttube using a plurality of jigs each having a gearwheel on which a plurality of protrudingparts are provided, wherein, in each of the jigs, the plurality of protruding parts arearranged at unequal spacing intervals on the gearwheel to provide each of the pluralityof protrusions at unequal spacing intervals.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2017/043818 WO2019111349A1 (en) | 2017-12-06 | 2017-12-06 | Heat exchanger, refrigeration cycle device, and method for manufacturing heat exchanger |
Publications (2)
Publication Number | Publication Date |
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AU2017442329A1 AU2017442329A1 (en) | 2020-06-11 |
AU2017442329B2 true AU2017442329B2 (en) | 2021-07-15 |
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AU2017442329A Active AU2017442329B2 (en) | 2017-12-06 | 2017-12-06 | Heat exchanger, refrigeration cycle apparatus and method of manufacturing heat exchanger |
Country Status (6)
Country | Link |
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EP (1) | EP3722729B1 (en) |
JP (1) | JPWO2019111349A1 (en) |
AU (1) | AU2017442329B2 (en) |
ES (1) | ES2882218T3 (en) |
SG (1) | SG11202004978QA (en) |
WO (1) | WO2019111349A1 (en) |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090071639A1 (en) * | 2005-05-16 | 2009-03-19 | Daikin Industries , Ltd. | Heat exchanger |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06100432B2 (en) * | 1984-06-20 | 1994-12-12 | 株式会社日立製作所 | Heat transfer tube |
JPS62242795A (en) * | 1986-04-15 | 1987-10-23 | Sumitomo Light Metal Ind Ltd | Heat transfer tube |
JPS6334489A (en) * | 1986-07-28 | 1988-02-15 | Nippon Denso Co Ltd | Heat exchanger |
JPH0356077U (en) * | 1989-09-28 | 1991-05-29 | ||
JPH09243284A (en) * | 1996-03-12 | 1997-09-19 | Kubota Corp | Heat exchanging pipe with internal surface projection |
EP1561795B1 (en) * | 2002-11-15 | 2014-04-02 | Kubota Corporation | Cracking tube with spiral fin |
CN100451531C (en) * | 2005-03-25 | 2009-01-14 | 清华大学 | Water heater heat exchange tube |
JP3982545B2 (en) * | 2005-09-22 | 2007-09-26 | ダイキン工業株式会社 | Air conditioner |
JP2007218486A (en) * | 2006-02-15 | 2007-08-30 | Hitachi Cable Ltd | Heat transfer tube for heat exchanger, and heat exchanger using the same |
JP2008023572A (en) * | 2006-07-24 | 2008-02-07 | Mori Machinery Corp | Dimple forming method in production line of heat exchange tube and dimple forming apparatus used in production line of heat exchange tube |
JP5044365B2 (en) * | 2006-11-04 | 2012-10-10 | 住友軽金属工業株式会社 | Double tube heat exchanger |
JP5224877B2 (en) * | 2008-04-01 | 2013-07-03 | 株式会社クボタ | Pyrolysis tube |
JP5642462B2 (en) * | 2010-09-08 | 2014-12-17 | 株式会社Uacj銅管 | Heat exchanger tube for heat exchanger and heat exchanger using the same |
JP5404589B2 (en) * | 2010-12-09 | 2014-02-05 | 三菱電機株式会社 | Twisted tube heat exchanger |
-
2017
- 2017-12-06 ES ES17934163T patent/ES2882218T3/en active Active
- 2017-12-06 JP JP2019557919A patent/JPWO2019111349A1/en active Pending
- 2017-12-06 AU AU2017442329A patent/AU2017442329B2/en active Active
- 2017-12-06 WO PCT/JP2017/043818 patent/WO2019111349A1/en unknown
- 2017-12-06 EP EP17934163.1A patent/EP3722729B1/en active Active
- 2017-12-06 SG SG11202004978QA patent/SG11202004978QA/en unknown
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090071639A1 (en) * | 2005-05-16 | 2009-03-19 | Daikin Industries , Ltd. | Heat exchanger |
Also Published As
Publication number | Publication date |
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EP3722729B1 (en) | 2021-07-07 |
JPWO2019111349A1 (en) | 2020-12-24 |
ES2882218T3 (en) | 2021-12-01 |
EP3722729A1 (en) | 2020-10-14 |
WO2019111349A1 (en) | 2019-06-13 |
AU2017442329A1 (en) | 2020-06-11 |
EP3722729A4 (en) | 2020-11-11 |
SG11202004978QA (en) | 2020-06-29 |
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Legal Events
Date | Code | Title | Description |
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DA3 | Amendments made section 104 |
Free format text: THE NATURE OF THE AMENDMENT IS: AMEND THE INVENTION TITLE TO READ HEAT EXCHANGER, REFRIGERATION CYCLE APPARATUS AND METHOD OF MANUFACTURING HEAT EXCHANGER |
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FGA | Letters patent sealed or granted (standard patent) |