CN204648760U - Heat exchanger and possess the refrigerating circulatory device of this heat exchanger - Google Patents
Heat exchanger and possess the refrigerating circulatory device of this heat exchanger Download PDFInfo
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- CN204648760U CN204648760U CN201520235255.6U CN201520235255U CN204648760U CN 204648760 U CN204648760 U CN 204648760U CN 201520235255 U CN201520235255 U CN 201520235255U CN 204648760 U CN204648760 U CN 204648760U
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Abstract
The heat exchanger that the utility model provides and possess the refrigerating circulatory device of this heat exchanger, can supply uniform refrigerant to each heat pipe.This heat exchanger has: the multiple and fin of row arrangement; Be thermally connected to multiple heat pipes of fin; And branched pipe, its multiple refrigerant outflow port that there is refrigerant inflow port and be connected to each heat pipe, the cold-producing medium flowed into from refrigerant inflow port is dispensed to multiple heat pipe, branched pipe has impact portions, this impact portions is formed at the opposed locations of the opening surface of refrigerant inflow port, for the cold-producing medium collision flowed into from refrigerant inflow port.
Description
Technical field
The utility model relates to heat exchanger and possesses the refrigerating circulatory device of this heat exchanger.
Background technology
Aircondition such as has: these parts are connected with refrigerant piping by the compressor of compressed refrigerant, the condenser (radiator) that condensation of refrigerant is liquefied, the throttling arrangement that cold-producing medium is reduced pressure and the evaporimeter that cold-producing medium evaporation is gasified.Wherein, condenser and evaporimeter are made up of heat exchanger, and this heat exchanger such as has: multiple fin arranged side by side and the multiple heat pipes (pipe) installed in the mode orthogonal with fin.
The cold-producing medium of gas-liquid two-phase state post-decompression in throttling arrangement is supplied to evaporimeter.Propose a kind of heat exchanger being connected with branched pipe at this, this branched pipe is used for each heat pipe (for example, referring to the patent document 1) cold-producing medium supplied from throttling arrangement being dispensed to evaporimeter.
In addition, also propose a kind of heat exchanger being connected with distributor, this distributor is used for each heat pipe (for example, referring to the patent document 2) cold-producing medium supplied from throttling arrangement being dispensed to evaporimeter.The side of the distributor described in patent document 2 is connected to throttling arrangement, and is connected with multiple conduit at opposite side.And each tubes connection is in each heat pipe.
Patent document 1: Japanese Unexamined Patent Publication 2004-44747 publication (for example, referring to the 8th page and Fig. 1)
Patent document 2: Japanese Unexamined Patent Publication 8-200886 publication (for example, referring to the 6th page and Fig. 4)
In throttling arrangement, the cold-producing medium of post-decompression gas-liquid two-phase state, supplies to evaporimeter.Therefore, produce following phenomenon sometimes, namely, due to the shape etc. of branched pipe, and due to Action of Gravity Field, the side be branched in the cold-producing medium of pipe branch easily flows into heat pipe, and the opposing party is difficult to flow into heat pipe.That is, in the condenser of supply high-pressure gaseous refrigerant, be difficult to produce above-mentioned phenomenon.But, comprise in the evaporimeter of the cold-producing medium of liquid refrigerant in supply, because liquid refrigerant easily flows to below under gravity, so produce above-mentioned phenomenon sometimes, thus equably cold-producing medium can not be supplied to each heat pipe of evaporimeter, the density of described liquid refrigerant is higher than the density of gaseous refrigerant.If can not by uniform refrigerant to each heat pipe supply of evaporimeter, then the heat exchanger effectiveness of heat exchanger can reduce.
Utility model content
The utility model makes to solve above such problem, object be to provide a kind of can by uniform refrigerant the ground heat exchanger that supplies to each heat pipe and the refrigerating circulatory device possessing this heat exchanger.
Heat exchanger of the present utility model, has: multiple fin, and they are row arrangement also; Multiple heat pipe, they are thermally connected to described fin; And branched pipe, it has refrigerant inflow port and multiple refrigerant outflow port, multiple described refrigerant outflow port is connected to each heat pipe, the cold-producing medium flowed into from described refrigerant inflow port distributes to multiple described heat pipe by this branched pipe, described branched pipe has impact portions, this impact portions is formed at the opposed locations of the opening surface of described refrigerant inflow port, for the cold-producing medium collision flowed into from described refrigerant inflow port.
Preferably, described branched pipe is formed as: make the internal diameter of described refrigerant inflow port less than the internal diameter of described refrigerant outflow port.
Preferably, described branched pipe has: cold-producing medium inflow part, and its one end is connected to distributor via throttling arrangement, and has described refrigerant inflow port; And branch, it is connected with the other end of described cold-producing medium inflow part, and is formed with described impact portions in the opposed locations of the opening surface of described cold-producing medium inflow part.
Preferably, described heat pipe is configured with multiple in mode side by side along the vertical direction, and described branched pipe has: upside outflow portion, and its one end is connected to the upside side surface part of described branch, the other end is connected to the end of described heat pipe, and is formed with described refrigerant outflow port; With downside outflow portion, its one end is connected to the downside side surface part of described branch, the other end is connected to the end of the end described heat pipe be on the lower positioned at than the described heat pipe being connected with described upside outflow portion, and be formed with described refrigerant outflow port, at described branch, at the link position than described upside outflow portion on the lower and than the link position top side place of described downside outflow portion, be formed with described impact portions.
Preferably, in the mode making described cold-producing medium inflow part, described upside outflow portion and described downside outflow portion parallel, described cold-producing medium inflow part, described upside outflow portion and described downside outflow portion is connected at described branch.
Preferably, described heat pipe is configured with multiple in mode side by side along the vertical direction, described heat pipe is configured with multiple in mode side by side along the vertical direction, upside outflow portion, its one end is connected to the upper surface part of described branch, the other end is connected to the end of described heat pipe, and is formed with described refrigerant outflow port; With downside outflow portion, its one end is connected to the lower surface portion of described branch, the other end is connected to the end of the end described heat pipe be on the lower positioned at than the described heat pipe being connected with described upside outflow portion, and be formed with described refrigerant outflow port, at described branch, at the link position than described upside outflow portion on the lower and than the link position top side place of described downside outflow portion, be formed with described impact portions.
Preferably, described upside outflow portion extends from the link position with described branch to upside, and be bent to form and with horizontal direction parallel extend, described downside outflow portion extends from the link position with described branch to downside, and be bent to form and with horizontal direction parallel extend.
Preferably, described cold-producing medium inflow part, than the position of described downside outflow portion near outflow portion side, described upside, is connected to described branch.
Preferably, described cold-producing medium inflow part connects in mode outstanding in branch described in other end side direction.
Preferably, described upside outflow portion and described downside outflow portion connect to outstanding mode in described branch with end side.
Preferably, described heat pipe is flat tube, and the described upside outflow portion of described branched pipe and described downside outflow portion, be formed as flat accordingly with described heat pipe.
Preferably, described upside outflow portion and described downside outflow portion are the flat perforated pipes being formed with multiple refrigerant flow path, the internal diameter of described cold-producing medium inflow part is less than the summation of following arbitrary flow path area, that is: the summation of the flow path area of the summation of the flow path area of multiple refrigerant flow paths of described upside outflow portion and multiple refrigerant flow paths of described downside outflow portion.
Preferably, when observing from horizontal profile, the inner surface of the side that described branched pipe is opposed with described impact portions is formed as arc-shaped.
Preferably, described impact portions has: the upper conical surface, and its described refrigerant outflow port side be formed as on the upside of described refrigerant inflow port side direction extends; The upper conical surface, its described refrigerant outflow port side be formed as on the upside of described refrigerant inflow port side direction extends; Top, it is formed at the link position of the lower end of the described upper conical surface and the upper end of the described lower conical surface.
Preferably, in the opposed part of described refrigerant inflow port, protuberance is formed with in described impact portions.
Preferably, at described branch and in top and bottom, be formed with the opening portion that the end for described heat pipe connects respectively.
Refrigerating circulatory device of the present utility model has above-mentioned heat exchanger.
According to heat exchanger of the present utility model, there is the branched pipe being connected to each heat pipe, and this branched pipe has impact portions.Therefore be expelled to the cold-producing medium of branch from refrigerant inflow port, collide with impact portions, thus be stirred in branched pipe.Thus when heat pipe configures in mode side by side up and down, cold-producing medium disperses equably up and down in branched pipe.In addition, when heat pipe in the horizontal direction side by side too.Like this according to heat exchanger of the present utility model, flow to each refrigerant outflow port while uniform refrigerant can be made, thus uniform refrigerant can be supplied to each heat pipe.
Accompanying drawing explanation
Fig. 1 is an example of the refrigerant loop structure of the refrigerating circulatory device 100 of the heat exchanger 1 with embodiment 1 of the present utility model.
Fig. 2 is the figure of the overall structure example of the heat exchanger 1 of embodiment 1 of the present utility model.
Fig. 3 A is the longitudinal section of the branched pipe 2 that heat exchanger 1 that Fig. 1 represents has.
Fig. 3 B is the sectional view of the branched pipe 2 at the A-A place that Fig. 3 A represents.
Fig. 3 C is the sectional view of the branched pipe 2 at the B-B place that Fig. 3 A represents.
Fig. 4 A is the variation 1 of the branched pipe 2 of the heat exchanger 1 of embodiment 1 of the present utility model.
Fig. 4 B is the variation 2 of the branched pipe 2 of the heat exchanger 1 of embodiment 1 of the present utility model.
Fig. 4 C is the variation 3 of the branched pipe 2 of the heat exchanger 1 of embodiment 1 of the present utility model.
Fig. 4 D is the variation 4 of the branched pipe 2 of the heat exchanger 1 of embodiment 1 of the present utility model.
Fig. 4 E is the variation 5 of the branched pipe 2 of the heat exchanger 1 of embodiment 1 of the present utility model.
Fig. 5 is the key diagram of the branched pipe 2B that the heat exchanger of embodiment 2 of the present utility model has.
Fig. 6 is the key diagram of the branched pipe 2C that the heat exchanger of embodiment 3 of the present utility model has.
Fig. 7 A is the longitudinal section of the branched pipe 2D that the heat exchanger of embodiment 4 of the present utility model has.
Fig. 7 B is the sectional view of the branched pipe 2D at the A-A place that Fig. 7 A represents.
Fig. 8 A is the longitudinal section of the branched pipe 2E that the heat exchanger of embodiment 5 of the present utility model has.
Fig. 8 B is the sectional view of the branched pipe 2E at the A-A place that Fig. 8 A represents.
Fig. 9 is the longitudinal section of the branched pipe 2F that the heat exchanger of embodiment 6 of the present utility model has.
Figure 10 is the longitudinal section of the branched pipe 2G that the heat exchanger of embodiment 7 of the present utility model has.
Figure 11 is the key diagram of existing heat exchanger and periphery thereof.
Description of reference numerals: 1 ... heat exchanger; 2 ... branched pipe; 2B ... branched pipe; 2C ... branched pipe; 2D ... branched pipe; 2E ... branched pipe; 2F ... branched pipe; 2G ... branched pipe; 2T1 ... branched pipe; 2T2 ... branched pipe; 2T3 ... branched pipe; 2T4 ... branched pipe; 2T5 ... branched pipe; 3 ... distributor; 4 ... capillary; 5 ... heat pipe; 5A ... arm; 5B ... bend; 6 ... collector; 7 ... heat pipe; 8 ... fin; 11 ... direction; 12 ... direction; 21 ... cold-producing medium inflow part; 21B ... cold-producing medium inflow part; 21B1 ... protuberance; 21a ... opening portion; 22Ea ... opening portion; 22a ... opening portion; 23 ... branch; 23a ... impact portions; 23aT4 ... impact portions; 23B ... branch; 23C ... branch; 23E ... branch; 23F ... branch; 23Fa ... impact portions; 23Fa1 ... the upper conical surface; 23Fa2 ... the lower conical surface; 23Fa3 ... top; 23G ... branch; 23T4 ... branch; 23T4A ... circular-arc part; 23T5 ... impact portions; 23T5A ... circular-arc part; 30A ... pressure fan; 30B ... pressure fan; 70 ... protuberance; 100 ... refrigerating circulatory device; 101 ... compressor; 102 ... heat exchanger; 122 ... upside outflow portion; 122C ... upside outflow portion; 122C1 ... protuberance; 122D ... upside outflow portion; 122E ... upside outflow portion; 222 ... downside outflow portion; 222C ... downside outflow portion; 222C1 ... protuberance; 222D ... downside outflow portion; 222E ... downside outflow portion; I ... refrigerant inflow port; O ... refrigerant outflow port; Q ... refrigerant flow path.
Detailed description of the invention
Below, with reference to accompanying drawing, while be described the embodiment of refrigerating plant of the present utility model.In addition, the embodiment not by following explanation limits the utility model.In addition, comprise Fig. 1, in the following figures, there is the situation different from reality in the magnitude relationship of each component parts.
Embodiment 1
Fig. 1 is an example of the refrigerant loop structure of the refrigerating circulatory device 100 of the heat exchanger 1 with present embodiment 1.Fig. 2 is the figure of the overall structure example of the heat exchanger 1 of embodiment 1.With reference to Fig. 1 and Fig. 2, the structure of heat exchanger 1 grade of present embodiment 1 is described.In addition, the X-direction in figure and Y-direction are the directions with horizontal direction parallel, and Z-direction is the direction parallel with gravity direction (above-below direction).Further, X-direction is orthogonal with Y-direction.
The heat exchanger 1 of present embodiment 1 is each heat pipe 7 of the subtend heat exchanger that improved of the supply system cryogen equably.
Structure explanation
Refrigerating circulatory device 100 has: the compressor 101 of compressed refrigerant, make the heat exchanger 102 (radiator) of condensation of refrigerant, be connected to the distributor 3 in the downstream of heat exchanger 102, be connected to multiple capillaries 4 of distributor 3 and be connected to the branched pipe 2 of distributor 3, and possesses the heat exchanger 1 that cold-producing medium is evaporated, the pressure fan 30A being attached to heat exchanger 102 and be attached to the pressure fan 30B of heat exchanger 1.
Compressor 101
Compressor 101 compresses and discharging refrigerant.The cold-producing medium discharge side of compressor 101 is connected to heat exchanger 102, and cold-producing medium suction side is connected to heat exchanger 1.Compressor 101 such as can adopt frequency-changeable compressor etc.
Heat exchanger 102
Heat exchanger 102 plays function as condenser (radiator).At heat exchanger 102, refrigerant inflow side is connected to compressor 101, and refrigerant outflow side is connected to distributor 3.Heat exchanger 102 such as can be made up of fin-tube heat exchanger etc., has: the multiple and fin of row arrangement and be thermally connected to the heat pipe of multiple fin.
Distributor 3
Distributor 3 is arranged at the leading portion (upstream side) of the branched pipe 2 of heat exchanger 1, for making the refrigerant branches of condensation liquefaction in heat exchanger 102.The refrigerant inflow side of distributor 3 is connected to heat exchanger 102, and refrigerant outflow side is connected to capillary 4.Existing refrigerating circulatory device has with under type, that is: via capillary 4, heat conductive pipes 5 supplies (with reference to Figure 11) cold-producing medium making to utilize distributor 3 to shunt.In the refrigerating circulatory device of heat exchanger 1 with present embodiment 1, distributor 3 is connected to branched pipe 2 via capillary 4.
In addition, in Fig. 1 and Fig. 2, although illustrate example heat exchanger 1 being connected with to a distributor 3, be not limited thereto, also can be connected with multiple distributor 3.
Capillary 4
The refrigerant inflow side of capillary 4 is connected to distributor 3, and refrigerant outflow side is connected to the branched pipe 2 of heat exchanger 1.Capillary 4 is for reducing pressure to the cold-producing medium of coming that flows via heat exchanger 102 and distributor 3.
Heat exchanger 1
Heat exchanger 1 plays function as evaporimeter.The refrigerant outflow side of heat exchanger 1 is connected to compressor 101, and refrigerant inflow side is connected to distributor 3.Heat exchanger 1 is fin-tube heat exchanger, has: the multiple and fin 8 of row arrangement and the multiple heat pipes 7 connected in the mode orthogonal with fin 8.Heat pipe 7 has: arm 5A, and it is formed as extending abreast with X-direction; Bend 5B, it is bent to the U-shaped be connected to each other by arm 5A.In addition, heat pipe 7 is to be configured with multiple in above-below direction mode side by side.
Wherein, heat exchanger 1 has branched pipe 2, and this branched pipe 2 is connected to adjacent heat pipe up and down 7.That is, heat exchanger 1 has the branched pipe 2 be connected with the heat pipe 7 of the heat pipe 7 of upside and the downside adjacent with branched pipe 2 on the upside of this.This branched pipe 2 is connected with the end of the side that cold-producing medium heat exchanger 1 in the end (end of arm 5A) of heat pipe 7 flows into.
In addition, heat exchanger 1 has collector 6, and this collector 6 is connected with the end of the side that cold-producing medium in the end (end of arm 5A) of heat pipe 7 flows out from heat exchanger 1.Utilize Fig. 3 A and Fig. 3 B etc., the structure of heat exchanger 1 is described in detail.
Pressure fan 30A and pressure fan 30B
Pressure fan 30A is attached to heat exchanger 102.Pressure fan 30A for the fin that to promote in heat exchanger 102 cold-producing medium of flowing and have through over-heat-exchanger 102 and heat pipe air between heat exchange.
Pressure fan 30B is attached to heat exchanger 1.Pressure fan 30B for the fin 8 that to promote in heat exchanger 1 cold-producing medium of flowing and have through over-heat-exchanger 1 and heat pipe 7 air between heat exchange.
About the details of branched pipe 2
Fig. 3 A is the longitudinal section of the branched pipe 2 that heat exchanger 1 that Fig. 1 represents has.Fig. 3 B is the sectional view of the branched pipe 2 at the A-A place that Fig. 3 A represents.Fig. 3 C is the sectional view of the branched pipe 2 at the B-B place that Fig. 3 A represents.With reference to Fig. 3 A, Fig. 3 B and Fig. 3 C, the detailed construction of branched pipe 2 and action effect thereof etc. are described.
Branched pipe 2 has: cold-producing medium inflow part 21, and its one end becoming refrigerant inflow side is connected to capillary 4; Branch 23, it is connected to the other end of cold-producing medium inflow part 21, and has the impact portions 23a for the cold-producing medium collision of discharging from cold-producing medium inflow part 21; Upside outflow portion 122, it is connected to the upper end side of branch 23; Downside outflow portion 222, it is connected to the lower end side of branch 23.Be formed with refrigerant inflow port I in cold-producing medium inflow part 21, be formed with refrigerant outflow port O in upside outflow portion 122 and downside outflow portion 222.Wherein, cold-producing medium inflow part 21, branch 23, upside outflow portion 122 and downside outflow portion 222 form.
Cold-producing medium inflow part 21
Cold-producing medium inflow part 21 is cartridges of linearity, and one end is connected to distributor 3 via capillary 4, and the other end is connected to branch 23.And under the state that branched pipe 2 is connected to heat pipe 7, cold-producing medium inflow part 21 is connected to branch 23 in the mode parallel with X-direction.The shape that the section parallel with Z-direction of cold-producing medium inflow part 21 is observed is circular.Cold-producing medium inflow part 21 is connected to the middle body of the width of the short transverse of branch 23 in branch 23.Therefore the distance, identical with the distance of the short transverse of downside outflow portion 222 with cold-producing medium inflow part 21 of cold-producing medium inflow part 21 and the short transverse of upside outflow portion 122.
Cold-producing medium inflow part 21 is formed as its flow path area and is less than the upside flow path area of outflow portion 122 and the flow path area of downside outflow portion 222.That is, cold-producing medium inflow part 21 is formed as its internal diameter and is less than the upside internal diameter of the outflow portion 122 and internal diameter of downside outflow portion 222.Like this, by the internal diameter of cold-producing medium inflow part 21 is suppressed less, thus this partial response the trend of the cold-producing medium of discharging from cold-producing medium inflow part 21 to branch 23 is strengthened.The liquid refrigerant of discharging from cold-producing medium inflow part 21 to branch 23 is particularly made to collide with impact portions 23a more effectively.If liquid refrigerant and impact portions 23a collide, then due to this impact, liquid refrigerant is disperseed up and down equably.Therefore, it is possible to make the cold-producing medium of discharging from cold-producing medium inflow part 21 to branch 23, flow into upside outflow portion 122 and downside outflow portion 222 equably.
Branch 23
Branch 23 is connected with cold-producing medium inflow part 21 in its side, in another side opposed with side, is connected with upside outflow portion 122 and downside outflow portion 222.And, at branch 23, at the middle body of the width of short transverse, the middle body of namely parallel with Y-direction width, be connected with cold-producing medium inflow part 21.In addition at branch 23, be connected with upside outflow portion 122 in upper end, be connected with downside outflow portion 222 in lower end.In addition, branched pipe 2 is connected to heat pipe 7 (with reference to Fig. 2) in the mode that branch 23 is parallel relative to the fin 8 of heat exchanger 1.
Branch 23 is the strip parts formed in the mode extended on long side direction that is Z-direction, is formed with the space of the cold-producing medium of discharging from cold-producing medium inflow part 21 in inside.Impact portions 23a is formed with in the opposed locations of the opening surface of cold-producing medium inflow part 21 at branch 23.That is, at branch 23, at the inner surface opposed with the face being connected with cold-producing medium inflow part 21, impact portions 23a is formed with.Impact portions 23a has smooth vertical plane, and under the state of heat pipe 7 that impact portions 23a is connected to heat exchanger 1, this smooth vertical plane and Z-direction extend abreast.In addition, impact portions 23a is formed in link position than upside outflow portion 122 on the lower and than the link position of downside outflow portion 222 top side place.Because branch 23 has this impact portions 23a, therefore, it is possible to liquid towards cold-producing medium stirs in branch 23.
In addition, in present embodiment 1, be illustrated as an example although there is smooth vertical plane using impact portions 23a, be not limited thereto, also slightly can stagger relative to Z-direction, can also be formed as wavy in z-direction or be formed as wavy in the Y direction.In addition, the horizontal profile of impact portions 23a also can become arc-shaped.
Upside outflow portion 122
Upside outflow portion 122 is cartridges of linearity.Upside outflow portion 122, in mode parallel with X-direction under the state being connected to heat pipe 7, is connected to branch 23.The shape that the section parallel with Z-direction of upside outflow portion 122 is observed is rectangle.One end of upside outflow portion 122, in the mode orthogonal relative to branch 23, is connected to the upside side surface part in branch 23.Wherein, in present embodiment 1, upside side surface part refers to the upside (such as, upper end) in the horizontal side of branch 23.In addition, the other end of upside outflow portion 122 is connected to heat pipe 7.
Downside outflow portion 222
Downside outflow portion 222 also has the shape identical with upside outflow portion 122.That is, downside outflow portion 222 is cartridges of linearity.In addition, downside outflow portion 222, under the state being connected to heat pipe 7, is connected to branch 23 in the mode parallel with X-direction.In addition, the shape that the section parallel with Z-direction of downside outflow portion 222 is observed is rectangle.One end of downside outflow portion 222, in the mode orthogonal relative to branch 23, is connected to the downside side surface part in branch 23.Wherein, in present embodiment 1, downside side surface part refers to the downside (such as, lower end) in the horizontal side of branch 23.In addition, the other end of downside outflow portion 222 is connected to heat pipe 7.
The flowing of working fluid (cold-producing medium)
Next, be described with reference to the above-mentioned flowing of Fig. 1, Fig. 2, Fig. 3 A and Fig. 3 B to working fluid.The high temperature of being discharged by compressor 101, the cold-producing medium of high pressure, be supplied to heat exchanger 102 and carry out condensation liquefaction and become gas-liquid two-phase cold-producing medium.As shown in the flow of refrigerant direction 11 of Fig. 2, the cold-producing medium flowed out from heat exchanger 102 flows into distributor 3.Flow into distributor 3 and the cold-producing medium be assigned with, flow into each capillary 4.The cold-producing medium flowing into capillary 4 is depressurized.
The gas-liquid two-phase cold-producing medium flowed out from capillary 4 flows into branched pipe 2.More specifically, flow into the gas-liquid two-phase cold-producing medium of branch 23 via cold-producing medium inflow part 21, collide the impact portions 23a being formed at branch 23, thus be stirred in branch 23.In addition, owing to setting in the mode of the internal diameter suppressing cold-producing medium inflow part 21, the trend therefore flowing into the cold-producing medium in branch 23 strengthens, thus gas-liquid two-phase cold-producing medium is stirred in impact portions 23a collision more effectively.
One side of the gas-liquid two-phase cold-producing medium after branch 23 is stirred, flows into upside outflow portion 122, and the opposing party flows into downside outflow portion 222.Then, flow into the cold-producing medium of upside outflow portion 122, flow to the heat pipe 7 of upside, flow into the cold-producing medium of downside outflow portion 222, flow to the heat pipe 7 of downside.Flow to the cold-producing medium after heat pipe 7, carry out heat exchange via fin 8 grade and air and evaporate.Then, as shown in the flow of refrigerant direction 12 of Fig. 2, the cold-producing medium of evaporation collaborates at collector 6, and flows out from heat exchanger 1.From the cold-producing medium that heat exchanger 1 flows out, attracted to the suction side of compressor 101.
The effect that the heat exchanger 1 etc. of present embodiment 1 has
The heat exchanger 1 of present embodiment 1 has: the branched pipe 2 being connected to the heat pipe 7 being configured at upper-lower position respectively, and this branched pipe 2 has impact portions 23a.Therefore comprise the cold-producing medium of the liquid refrigerant being expelled to branch 23 from cold-producing medium inflow part 21, collide with impact portions 23a.If the cold-producing medium and the impact portions 23a that comprise liquid refrigerant collide, then because it impacts, and the cold-producing medium comprising liquid refrigerant is disperseed up and down equably.Therefore, it is possible to make the cold-producing medium of discharging from cold-producing medium inflow part 21 to branch 23, flow into upside outflow portion 122 and downside outflow portion 222 equably.Uniform refrigerant can supply to each heat pipe 7 by the heat exchanger 1 of present embodiment 1 thus.
In addition, if if do not arrange impact portions 23a, be then expelled to the majority of the liquid refrigerant of branch 23 from cold-producing medium inflow part 21, flow to the downside of branch 23 due to Action of Gravity Field, and keep this state and easily flow to downside outflow portion 222.Like this, in the embodiment not being provided with impact portions 23a, cold-producing medium is difficult to flow to upside outflow portion 122, and the cold-producing medium flowing to upside outflow portion 122 easily produces deviation with the cold-producing medium flowing to downside outflow portion 222.On the other hand, the heat exchanger 1 of present embodiment 1, owing to having the branched pipe 2 being formed with impact portions 23a, in branch 23, therefore play the stirring action of liquid refrigerant, the cold-producing medium flowing to upside outflow portion 122 can be suppressed to produce deviation with the cold-producing medium flowing to downside outflow portion 222.That is, the heat exchanger 1 of present embodiment 1, produces deviation, therefore, it is possible to supplied to each heat pipe 7 by uniform refrigerant owing to can suppress the cold-producing medium flowing to upside outflow portion 122 with the cold-producing medium flowing to downside outflow portion 222.
The branched pipe 2 of the heat exchanger 1 of present embodiment 1 is configured to: opposed with the plane of the fin 8 of most end.Wherein, branched pipe 2 has the upside outflow portion 122 and downside outflow portion 222 that extend abreast with linearity and X-direction.That is, branched pipe 2 is formed as not only having cold-producing medium inflow part 21 and branch 23, also has the shape of upside outflow portion 122 and downside outflow portion 222.Therefore, when heat pipe 7 is connected with branched pipe 2, also can being bent to form heat pipe 7, not connecting pipe arrangement for being connected with branched pipe 2 by heat pipe 7 in addition.Heat pipe 7 can be suppressed thus to become complicated structure with the coupling part of branched pipe 2, therefore, it is possible to heat exchanger 1 is miniaturized.
The heat exchanger 1 of present embodiment 1, although be illustrated the heat exchanger that the cold-producing medium inflow part 21 of branched pipe 2, branch 23, upside outflow portion 122 and downside outflow portion 222 form, but be not limited thereto, formed with also can distinguishing split.
Although the heat exchanger 1 of present embodiment 1 is illustrated the heat exchanger that branched pipe 2 is connected to neighbouring heat pipe 7, be not limited thereto.If the heat pipe of both sides 7 has upper and lower relation, then without the need to adjacent.Such as heat exchanger 1 has: upper guide heat pipe, adjacent with upper guide heat pipe and be configured in the pars intermedia heat pipe of the downside of upper guide heat pipe and adjacent with pars intermedia heat pipe and be configured in the lower guide heat pipe of the downside of pars intermedia heat pipe.In this case, branched pipe 2 also can be connected to upper guide heat pipe and lower guide heat pipe.
Possess the refrigerating circulatory device 100 of the heat exchanger 1 of present embodiment 1, owing to having heat exchanger 1, therefore there is the effect same with the heat exchanger 1 of present embodiment 1.
That is, the partition characteristic of heat exchanger 1 can be improved, efficient refrigerating circulatory device 100 can be obtained.In addition, due to can be miniaturized by heat exchanger 1, thus can realize the space-efficient of unit inside, therefore, it is possible to increase the heat-conducting area of heat exchanger 1, widen the free degree of spatial design, thus be easy to acquisition unit structure.
Although the branched pipe 2 of the heat exchanger 1 to present embodiment 1, situation about being connected with the heat pipe 7 being configured at upper-lower position is respectively illustrated, and is not limited thereto.Such as, even be configured to tilt relative to level by heat exchanger 1, and adjacent heat pipe 7 is configured at the mode of oblique upper (or below), also can obtain the effect same with the heat exchanger 1 of present embodiment 1.In addition, even if when branched pipe 2 is connected with the heat pipe 7 being configured at right position respectively, because cold-producing medium and impact portions 23a collide and be stirred, therefore also the effect same with the heat exchanger 1 of present embodiment 1 can be obtained.
Variation 1
Fig. 4 A is the variation 1 (branched pipe 2T1) of the branched pipe 2 of the heat exchanger 1 of present embodiment 1.Fig. 4 A is same with Fig. 3 A, is the longitudinal section of branched pipe 2.In present embodiment 1, although be illustrated the situation that cold-producing medium inflow part 21 is connected with the middle body of the width of the short transverse of branch 23 in branch 23, be not limited thereto.
Although can utilize impact portions 23a, liquid refrigerant is disperseed up and down, the fact that Action of Gravity Field plays a role does not change.Even if therefore utilize impact portions 23a to make liquid refrigerant disperse, also can imagine the refrigerant amount flowing to downside outflow portion 222, be slightly more than the refrigerant amount flowing to upside outflow portion 122, thus cause uneven situation.
Therefore, as shown in Figure 4 A, also can by cold-producing medium inflow part 21 link position with branch 23, be formed in than the top side of the middle body of short transverse and the position of center bias from branch 23.That is, at the branch 23 of branched pipe 2T1, than the position of downside outflow portion 222 near upside outflow portion 122 side, cold-producing medium inflow part 21 is connected with.More specifically, as shown in Figure 4 A, the top of the medial surface from cold-producing medium inflow part 21 is being set to Z1 to the distance of the short transverse at the top of the medial surface of upside outflow portion 122, when the bottom of the medial surface from cold-producing medium inflow part 21 is set to Z2 to the distance of the short transverse of the bottom of the medial surface of downside outflow portion 222, branched pipe 2T1 also can be configured to Z1 and be less than Z2.In the present embodiment, flowing to the refrigerant amount of upside outflow portion 122, when being less than the refrigerant amount flowing to downside outflow portion 222, the refrigerant amount of outflow portion 122 on the upside of the flow direction can being made to increase, thus both refrigerant amounts can be made even.In addition, even the manner, also the effect same with the heat exchanger 1 of present embodiment 1 can be obtained.
Variation 2
Fig. 4 B is the variation 2 (branched pipe 2T2) of the branched pipe 2 of the heat exchanger 1 of present embodiment 1.Fig. 4 B is the sectional view of Y-Z plane and is the sectional view of the position corresponding with the A-A of Fig. 3 A.In present embodiment 1, although situation cold-producing medium inflow part 21 being connected to the middle body of width parallel with Y-direction in branch 23 is illustrated, be not limited thereto.As shown in Figure 4 B, cold-producing medium inflow part 21, relative to the link position of branch 23, also can stagger relative to the width parallel with Y-direction.Even which, also the effect same with the heat exchanger 1 of present embodiment 1 can be obtained.
Variation 3
Fig. 4 C is the variation 3 (branched pipe 2T3) of the branched pipe 2 of the heat exchanger 1 of present embodiment 1.Fig. 4 C is the sectional view of Y-Z plane and the sectional view of the position corresponding with the A-A of Fig. 3 A.In present embodiment 1, although be illustrated the branched pipe 2 that cold-producing medium inflow part 21, upside outflow portion 122 and downside outflow portion 222 are in parallel position relationship, be not limited thereto.As shown in Figure 4 C, such as the position relationship of cold-producing medium inflow part 21, upside outflow portion 122 and downside outflow portion 222, also can be in the position of torsion.That is, also in the orthogonal mode in the direction parallel with cold-producing medium inflow part 21, the direction parallel with downside outflow portion 222 with upside outflow portion 122, cold-producing medium inflow part 21, upside outflow portion 122 and downside outflow portion 222 can be connected to branch 23.
Variation 4
Fig. 4 D is the variation 4 (branched pipe 2T4) of the branched pipe 2 of the heat exchanger 1 of embodiment 1.Fig. 4 D is the sectional view of X-Y plane and the sectional view of the position corresponding with the B-B of Fig. 3 A.In present embodiment 1, as shown in Figure 3 C, although be rectangle using the horizontal cross-sectional shape of branch 23, situation is illustrated as an example, is not limited thereto.Such as, the shape of branched pipe 2T3 also can be cylindric.That is, as shown in Figure 4 D, the horizontal cross-sectional shape of branched pipe 2T3 also can be circular.
In this approach, impact portions 23aT4 is formed as arc-shaped, and with impact portions 23aT4 continuous print inner surface, be also formed as arc-shaped.That is, branched pipe 2T4 has: be formed as the impact portions 23aT4 of arc-shaped and be namely connected with the circular-arc part 23T4A of cold-producing medium inflow part 21 with impact portions 23aT4 continuous print inner surface.
Therefore, in this variation 4, except the effect that the heat exchanger 1 with present embodiment 1 is same, following effect can also be obtained.That is, the cold-producing medium in branch 23T4 is flow into, after colliding impact portions 23aT4, swimmingly to Y-direction branch.Then, collide the cold-producing medium after impact portions 23aT4, along the circular-arc part 23T4A convection current swimmingly of branch 23T4.Therefore flow to the cold-producing medium in branch 23T4, become and be more easily stirred.
In addition, in this variation 4, although be illustrated the situation that impact portions 23aT4 and circular-arc part 23T4A is positioned on concentric circles, be not limited thereto.The center forming the circular arc of impact portions 23aT4 also can be different from the center of the circular arc forming circular-arc part 23T4A.
Variation 5
Fig. 4 E is the variation 5 (branched pipe 2T5) of the branched pipe 2 of the heat exchanger 1 of embodiment 1.Fig. 4 E is the sectional view of X-Y plane and the sectional view of the position corresponding with the B-B of Fig. 3 A.In variation 5, be impact portions 23T5 not to be formed as arc-shaped with the difference of variation 4, but identical with variation 4 in other respects.That is, branched pipe 2T5 has: the circular-arc part 23T5A of plane impact portions 23a and arc-shaped.In addition, in this variation 5, although be semicircle (central angle is 180 degree) with the section of circular-arc part 23T5A, situation is that an example is illustrated, and is not limited thereto.Even variation 5 also can obtain the effect same with variation 4.
Embodiment 2
Fig. 5 is the key diagram of the branched pipe 2B that the heat exchanger of present embodiment 2 has.In present embodiment 2, identical Reference numeral is marked to the structure common with embodiment 1, and is described centered by difference.In present embodiment 2, cold-producing medium inflow part 21B, with branch 23B, upside outflow portion 122 and downside outflow portion 222 be formed as split.And cold-producing medium inflow part 21B is to be connected to branch 23B to outstanding mode in branch 23B.
Be formed with opening portion 21a at branch 23B place, this opening portion 21a becomes the insertion section of inserting for cold-producing medium inflow part 21.
Cold-producing medium inflow part 21B has protuberance 21B1 outstanding in branch 23B.Cold-producing medium inflow part 21B is such as fixed on branch 23B by welding etc.Wherein, the overhang outstanding in branch 23B to cold-producing medium inflow part 21B, can suitably set.
By adjusting this overhang, the flow path resistance in branch 23B can be increased, thus can more uniformly to upside outflow portion 122 and downside outflow portion 222 the supply system cryogen.That is, because cold-producing medium inflow part 21B is outstanding in branch 23B, therefore, it is possible to reduce the front end of cold-producing medium inflow part 21B and the distance of impact portions 23a, thus more flow path resistance is increased.Therefore, it is possible to make cold-producing medium and impact portions 23a collide more effectively, thus the cold-producing medium comprising liquid refrigerant is disperseed up and down equably.
The effect of embodiment 2
In present embodiment 2, except there is the effect same with embodiment 1, also there is following effect.That is, because cold-producing medium inflow part 21B has protuberance 21B1, therefore, it is possible to reduce the front end of protuberance 21B1 and the distance of impact portions 23a.Cold-producing medium and impact portions 23a can be made thus more effectively to collide, thus the cold-producing medium comprising liquid refrigerant is disperseed up and down equably.
In present embodiment 2, cold-producing medium inflow part 21B, with branch 23B, upside outflow portion 122 and downside outflow portion 222 be formed as split.Therefore, in the shape suitably changing cold-producing medium inflow part 21B, when realizing the high performance of cold-producing medium inflow part 21B, cold-producing medium inflow part 21B part remaining with it is formed as split, therefore improves manufacturing.
Embodiment 3
Fig. 6 is the key diagram of the branched pipe 2C that the heat exchanger of present embodiment 3 has.In present embodiment 3, mark identical Reference numeral to embodiment 1,2 common structures, and be described centered by difference.In present embodiment 3, cold-producing medium inflow part 21B, branch 23C, upside outflow portion 122C and downside outflow portion 222C are formed as split respectively.And be not only cold-producing medium inflow part 21B, for upside outflow portion 122C and downside outflow portion 222C, also to be connected to branch 23C to outstanding mode in branch 23C.
Be formed with opening portion 21a at branch 23C, this opening portion 21a becomes the insertion section of inserting for cold-producing medium inflow part 21, and is formed with the opening portion 22a becoming and keep supplying the insertion section that side outflow portion 122C and downside outflow portion 222C inserts respectively.
Upside outflow portion 122C has protuberance 122C1 outstanding in branch 23C.In addition, downside outflow portion 222C has protuberance 222C1 outstanding in branch 23C.Upside outflow portion 122C and downside outflow portion 222C, such as, be fixed on branch 23C by welding etc.Wherein, for protuberance 122C1 and protuberance 222C1 to the overhang in branch 23C, can suitably set.
By adjusting this overhang, the flow path resistance in branch 23C can be increased, thus can more uniformly to upside outflow portion 122 and downside outflow portion 222 the supply system cryogen.That is, by making upside outflow portion 122C and downside outflow portion 222C outstanding in branch 23C, thus the cold-producing medium in branch 23C, become and be difficult to enter upside outflow portion 122C and downside outflow portion 222C.Therefore, after cold-producing medium (liquid refrigerant) is accumulated in branch 23C, upside outflow portion 122C and downside outflow portion 222C is flowed into.
The effect of embodiment 3
In present embodiment 3, except having except embodiment 1,2 same effects, also there is following effect.That is, because upside outflow portion 122C has protuberance 122C1, downside outflow portion 222C has protuberance 222C1, is therefore expelled to the cold-producing medium in branch 23C from cold-producing medium inflow part 21B, plays a role in the mode be accumulated in branch 23C.Therefore, in branch 23C, from downside to upside, be easily included liquid refrigerant fill up at interior cold-producing medium, thus the cold-producing medium comprising liquid refrigerant can be made to disperse equably up and down.
In present embodiment 3, although be illustrated the embodiment being provided with upside outflow portion 122C and downside outflow portion 222C at branched pipe 2C, be not limited thereto.Such as, with the heat pipe 7 of heat exchanger 1, upside outflow portion 122C and downside outflow portion 222C can also be replaced.When replacing with heat pipe 7, also at branch 23C, the opening portion 22a for inserting heat pipe 7 can be formed up and down, such as, be waited by welding and heat pipe 7 is fixed with branch 23C.
Embodiment 4
Fig. 7 A is the longitudinal section of the branched pipe 2D that the heat exchanger of present embodiment 4 has.Fig. 7 B is the sectional view of the branched pipe 2D at the A-A place shown in Fig. 7 A.In present embodiment 4, identical Reference numeral is marked to the structure common with embodiment 1 ~ 3, and is described centered by difference.In present embodiment 4, except the structure of embodiment 3, upside outflow portion 122D and downside outflow portion 222D is made the flat tube being formed as flat.In addition as flat tube, the flat perforated pipe that the mode that can adopt to divide multiple refrigerant flow path is formed, the flat tube being formed with a refrigerant flow path also can be adopted.In present embodiment 4, flat perforated pipe is described.
Multiple refrigerant flow path Q is formed at upside outflow portion 122D.Equally, multiple refrigerant flow path Q is also formed with at downside outflow portion 222D.Wherein, cold-producing medium inflow part 21 is formed as: its flow path area is less than the area of the summation of following arbitrary flow path area, that is: the area of the summation of the flow path area of the area of the summation of the flow path area of the refrigerant flow path Q of upside outflow portion 122D and the refrigerant flow path Q of downside outflow portion 222D.Like this, by the internal diameter of cold-producing medium inflow part 21 is suppressed less, thus this partial response the trend of the cold-producing medium of discharging from cold-producing medium inflow part 21 to branch 23 is strengthened, thus the cold-producing medium in branch 23 can be made, flow into upside outflow portion 122D and downside outflow portion 222D equably.
The effect of embodiment 4
In present embodiment 4, except there is the effect same with embodiment 1 ~ 3, also there is following effect.That is, even if when the heat pipe 7 of heat exchanger 1 is flat tube, also branched pipe 2D can be connected with heat pipe 7.
Embodiment 5
Fig. 8 A is the longitudinal section of the branched pipe 2E that the heat exchanger of present embodiment 5 has.Fig. 8 B is the sectional view of the branched pipe 2E at the A-A place shown in Fig. 8 A.In present embodiment 5, identical Reference numeral is marked to the structure common with embodiment 1 ~ 4, and is described centered by difference.In embodiment 1 grade, it is the embodiment in the face parallel with the Z-direction becoming long side direction upside outflow portion 122 and downside outflow portion 222 being inserted in branch 23, but in present embodiment 5, become embodiment upside outflow portion 122E and downside outflow portion 222E being inserted in the face parallel with short side direction (X-direction).Therefore, in present embodiment 5, the width of the short transverse of branch 23E can be suppressed.
In the upper surface part of branch 23E, being formed with the opening portion 22Ea for being inserted by upside outflow portion 122E, being formed with the opening portion 22Ea for being inserted by downside outflow portion 222E in lower surface portion.Like this, due to the opening portion of inserting is formed at the face parallel with short side direction (X-direction), therefore this partial response ground can suppress the width of the short transverse of branch 23E.
Upside outflow portion 122E and downside outflow portion 222E is flat tube.And upside outflow portion 122E is from the side be connected with branch 23E to after upside extends, and is bent to form, and extends in the horizontal direction.In addition, downside outflow portion 222E, from the side be connected with branch 23E to after downside extends, is bent to form, and extends in the horizontal direction.In addition, in Fig. 8 A and Fig. 8 B, although illustrate that upside outflow portion 122E and downside outflow portion 222E is bent to the situation at right angle, be not limited to this.
The effect of embodiment 5
In present embodiment 5, except there is the effect same with embodiment 1 ~ 4, also there is following effect.That is, the width of the short transverse of branch 23E can be suppressed, therefore become and easily the cold-producing medium in branch 23E is stirred.Thus can evenly cold-producing medium heat conductive pipes 7 be distributed.
In addition, in present embodiment 5, being illustrated, being not limited thereto although the situation that above side outflow portion 122E and downside outflow portion 222E is flat tube is example, such as, also can be circular pipe.
In present embodiment 5, although the situation of outflow portion 122E and downside outflow portion 222E is illustrated on the upside of having for branch 23E, also can be the embodiment without upside outflow portion 122E and downside outflow portion 222E.In this case, the heat pipe 7 as flat tube is bent to form in the same manner as upside outflow portion 122E and downside outflow portion 222E, and with replacement upside outflow portion 122E and downside outflow portion 222E.Even if like this, also the effect same with present embodiment 5 can be obtained.
Embodiment 6
Fig. 9 is the longitudinal section of the branched pipe 2F that the heat exchanger of present embodiment 6 has.In present embodiment 6, become the impact portions 23a of the branch 23 illustrated in embodiment 1, be formed with the embodiment of the conical surface, this cone-shaped becomes and extends up and down.
Being formed at the impact portions 23Fa of opposed locations of cold-producing medium inflow part 21, be formed with conical surface 23Fa1, lower conical surface 23Fa2 and top 23Fa3.
Upper conical surface 23Fa1 is formed as: the refrigerant outflow port O side on the upside of refrigerant inflow port I side direction extends.That is, upper conical surface 23Fa1 is formed as: from upside outflow portion 122 and downside outflow portion 222 side, more tends to cold-producing medium inflow part 21 side and rolls downwards tiltedly.
Lower conical surface 23Fa2 is formed as: the refrigerant outflow port O side on the downside of refrigerant inflow port I side direction extends.That is, lower conical surface 23Fa2 is formed as: from cold-producing medium inflow part 21 side, and more trend upside outflow portion 122 and downside outflow portion 222 side roll downwards tiltedly.The lower end of upper conical surface 23Fa1, is connected to the upper end of lower conical surface 23Fa2.This link position is corresponding with top 23Fa3.The forming position of top 23Fa3 is the opposed locations of cold-producing medium inflow part 21.
The effect of embodiment 6
In present embodiment 6, except there is the effect same with embodiment 1, also there is following effect.That is, in embodiment 6, branch 23F has: upper conical surface 23Fa1, lower conical surface 23Fa2 and top 23Fa3.Therefore the cold-producing medium in inflow branch 23F and impact portions 23Fa can not only be made to collide and be stirred, can also by the cold-producing medium in branch 23F, promptly upwards side outflow portion 122 and downside outflow portion 222 guide.
Embodiment 7
Figure 10 is the longitudinal section of the branched pipe 2G that the heat exchanger of present embodiment 7 has.In present embodiment 7, become the impact portions 23a of the branch 23 illustrated in embodiment 1, be formed with the embodiment of protuberance 70.
Protuberance 70 is formed with in the opposed locations of cold-producing medium inflow part 21 at branch 23G.Therefore flow into the cold-producing medium in branch 23G from cold-producing medium inflow part 21, by colliding with protuberance 70, and become and be easier to disperse up and down and be stirred.In addition, protuberance 70 can be single, also can be formed as multiple.
The effect of embodiment 7
In present embodiment 7, except there is the effect same with embodiment 1, also there is following effect.That is, in embodiment 7, owing to being formed with protuberance 70 at branch 23G, thus from the cold-producing medium that cold-producing medium inflow part 21 flows into, becoming and be easy to collide with protuberance 70 and disperse up and down.Therefore the easier cold-producing medium to flowing into branch 23G from cold-producing medium inflow part 21 stirs.
The branched pipe 2 illustrated in embodiment 1 ~ 7, the structure of 2B ~ 2G, also can suitably combine.
Claims (17)
1. a heat exchanger, is characterized in that, has:
Multiple fin, they are row arrangement also;
Multiple heat pipe, they are thermally connected to described fin; And
Branched pipe, it has refrigerant inflow port and multiple refrigerant outflow port, and multiple described refrigerant outflow port is connected to each heat pipe, and the cold-producing medium flowed into from described refrigerant inflow port distributes to multiple described heat pipe by this branched pipe,
Described branched pipe has impact portions, and this impact portions is formed at the opposed locations of the opening surface of described refrigerant inflow port, for the cold-producing medium collision flowed into from described refrigerant inflow port.
2. heat exchanger according to claim 1, is characterized in that,
Described branched pipe is formed as: make the internal diameter of described refrigerant inflow port less than the internal diameter of described refrigerant outflow port.
3. heat exchanger according to claim 1 and 2, is characterized in that,
Described branched pipe has:
Cold-producing medium inflow part, its one end is connected to distributor via throttling arrangement, and has described refrigerant inflow port; With
Branch, it is connected with the other end of described cold-producing medium inflow part, and is formed with described impact portions in the opposed locations of the opening surface of described cold-producing medium inflow part.
4. heat exchanger according to claim 3, is characterized in that,
Described heat pipe is configured with multiple in mode side by side along the vertical direction,
Described branched pipe has:
Upside outflow portion, its one end is connected to the upside side surface part of described branch, and the other end is connected to the end of described heat pipe, and is formed with described refrigerant outflow port; With
Downside outflow portion, its one end is connected to the downside side surface part of described branch, and the other end is connected to the end of the end described heat pipe be on the lower positioned at than the described heat pipe being connected with described upside outflow portion, and is formed with described refrigerant outflow port,
At described branch, at the link position than described upside outflow portion on the lower and than the link position top side place of described downside outflow portion, be formed with described impact portions.
5. heat exchanger according to claim 4, is characterized in that,
In the mode making described cold-producing medium inflow part, described upside outflow portion and described downside outflow portion parallel, connect described cold-producing medium inflow part, described upside outflow portion and described downside outflow portion at described branch.
6. heat exchanger according to claim 3, is characterized in that,
Described heat pipe is configured with multiple in mode side by side along the vertical direction,
Described branched pipe has:
Upside outflow portion, its one end is connected to the upper surface part of described branch, and the other end is connected to the end of described heat pipe, and is formed with described refrigerant outflow port; With
Downside outflow portion, its one end is connected to the lower surface portion of described branch, and the other end is connected to the end of the end described heat pipe be on the lower positioned at than the described heat pipe being connected with described upside outflow portion, and is formed with described refrigerant outflow port,
At described branch, at the link position than described upside outflow portion on the lower and than the link position top side place of described downside outflow portion, be formed with described impact portions.
7. heat exchanger according to claim 6, is characterized in that,
Described upside outflow portion extends from the link position with described branch to upside, and be bent to form and with horizontal direction parallel extend,
Described downside outflow portion extends from the link position with described branch to downside, and be bent to form and with horizontal direction parallel extend.
8. heat exchanger according to claim 4, is characterized in that,
Described cold-producing medium inflow part, than the position of described downside outflow portion near outflow portion side, described upside, is connected to described branch.
9. heat exchanger according to claim 3, is characterized in that,
Described cold-producing medium inflow part connects in mode outstanding in branch described in other end side direction.
10. heat exchanger according to claim 4, is characterized in that,
Described upside outflow portion and described downside outflow portion connect to outstanding mode in described branch with end side.
11. heat exchangers according to claim 4, is characterized in that,
Described heat pipe is flat tube,
The described upside outflow portion of described branched pipe and described downside outflow portion, be formed as flat accordingly with described heat pipe.
12. heat exchangers according to claim 11, is characterized in that,
Described upside outflow portion and described downside outflow portion are the flat perforated pipes being formed with multiple refrigerant flow path,
The internal diameter of described cold-producing medium inflow part is less than the summation of following arbitrary flow path area, that is: the summation of the flow path area of the summation of the flow path area of multiple refrigerant flow paths of described upside outflow portion and multiple refrigerant flow paths of described downside outflow portion.
13. heat exchangers according to claim 1 and 2, is characterized in that,
When observing from horizontal profile, the inner surface of the side that described branched pipe is opposed with described impact portions is formed as arc-shaped.
14. heat exchangers according to claim 1 and 2, is characterized in that,
Described impact portions has:
The upper conical surface, its described refrigerant outflow port side be formed as on the upside of described refrigerant inflow port side direction extends;
The lower conical surface, its described refrigerant outflow port side be formed as on the downside of described refrigerant inflow port side direction extends; And
Top, it is formed at the link position of the lower end of the described upper conical surface and the upper end of the described lower conical surface.
15. heat exchangers according to claim 1 and 2, is characterized in that,
In the opposed part of described refrigerant inflow port, protuberance is formed with in described impact portions.
16. heat exchangers according to claim 3, is characterized in that,
At described branch and in top and bottom, be formed with the opening portion that the end for described heat pipe connects respectively.
17. 1 kinds of refrigerating circulatory devices, is characterized in that,
There is the heat exchanger described in any one of claim 1 ~ 16.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-136818 | 2014-07-02 | ||
| JP2014136818A JP2016014504A (en) | 2014-07-02 | 2014-07-02 | Heat exchanger, and refrigeration cycle device with the same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204648760U true CN204648760U (en) | 2015-09-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520235255.6U Expired - Fee Related CN204648760U (en) | 2014-07-02 | 2015-04-17 | Heat exchanger and possess the refrigerating circulatory device of this heat exchanger |
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| Country | Link |
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| JP (1) | JP2016014504A (en) |
| CN (1) | CN204648760U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108844393A (en) * | 2018-05-10 | 2018-11-20 | 哈尔滨理工大学 | A kind of micro-channel heat exchanger with part flow arrangement, Thermal Performance of Micro Channels device assembly |
| CN112567193A (en) * | 2018-08-22 | 2021-03-26 | 三菱电机株式会社 | Heat exchanger and air conditioner |
| CN112880432A (en) * | 2021-02-02 | 2021-06-01 | 格力电器（武汉）有限公司 | Heat exchange tube assembly, micro-channel heat exchanger, air conditioning system and heat exchanger design method |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017109065B4 (en) * | 2017-04-27 | 2019-06-06 | Miele & Cie. Kg | Connection system for gas- and fluid-tight connection of a condenser of a heat pump with a heat pump evaporator |
| JP6843256B2 (en) * | 2017-09-25 | 2021-03-17 | 三菱電機株式会社 | Refrigerant distributor and air conditioner |
| WO2023152789A1 (en) * | 2022-02-08 | 2023-08-17 | 三菱電機株式会社 | Heat exchanger |
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| JPS5933819B2 (en) * | 1979-03-27 | 1984-08-18 | 富士電機株式会社 | Cooling system |
| JPH0544653Y2 (en) * | 1987-07-24 | 1993-11-12 | ||
| JP2746681B2 (en) * | 1989-08-18 | 1998-05-06 | 松下冷機株式会社 | Refrigerant flow divider |
| JPH08200886A (en) * | 1995-01-25 | 1996-08-06 | Yanmar Diesel Engine Co Ltd | Heat exchanger air conditioning |
| JP3390565B2 (en) * | 1995-03-15 | 2003-03-24 | 郷商事株式会社 | Refrigerant flow divider |
| JPH09159320A (en) * | 1995-12-05 | 1997-06-20 | Matsushita Electric Ind Co Ltd | Refrigerant distributor |
| JPH10132427A (en) * | 1996-10-30 | 1998-05-22 | Daikin Ind Ltd | Heat-exchanger |
| JP2004044747A (en) * | 2002-07-15 | 2004-02-12 | Denso Corp | Branching pipe and method for manufacture the same |
| JP2007155308A (en) * | 2005-11-09 | 2007-06-21 | Fujitsu General Ltd | Flow divider and refrigeration cycle device using the same |
| JP5030932B2 (en) * | 2008-12-10 | 2012-09-19 | 三菱電機株式会社 | Heat exchanger and air-conditioning refrigeration system |
| EP2853843B1 (en) * | 2012-04-26 | 2020-03-11 | Mitsubishi Electric Corporation | A refrigerant distributing device, and heat exchanger equipped with such a refrigerant distributing device |
| EP2955464A4 (en) * | 2013-01-22 | 2016-11-09 | Mitsubishi Electric Corp | Refrigerant distributor and heat pump device using refrigerant distributor |
-
2014
- 2014-07-02 JP JP2014136818A patent/JP2016014504A/en active Pending
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- 2015-04-17 CN CN201520235255.6U patent/CN204648760U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108844393A (en) * | 2018-05-10 | 2018-11-20 | 哈尔滨理工大学 | A kind of micro-channel heat exchanger with part flow arrangement, Thermal Performance of Micro Channels device assembly |
| CN112567193A (en) * | 2018-08-22 | 2021-03-26 | 三菱电机株式会社 | Heat exchanger and air conditioner |
| CN112567193B (en) * | 2018-08-22 | 2022-06-03 | 三菱电机株式会社 | Heat exchanger and air conditioner |
| CN112880432A (en) * | 2021-02-02 | 2021-06-01 | 格力电器（武汉）有限公司 | Heat exchange tube assembly, micro-channel heat exchanger, air conditioning system and heat exchanger design method |
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| Publication number | Publication date |
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| JP2016014504A (en) | 2016-01-28 |
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