JP4866416B2 - Heat exchanger - Google Patents

Description

  The present invention relates to a heat exchanger used in a refrigeration or cooling device.

  In the heat exchanger, in order to increase the heat exchange efficiency, it is important to evenly distribute the heat exchange medium supplied to the header to a plurality of tubes for heat exchange. However, in heat exchangers, in particular, evaporators (evaporators) and the like, generally, the inflowing heat exchange medium (refrigerant) is in a two-phase state including a gas phase and a liquid phase. For this reason, a liquid component having a large specific gravity and easily affected by gravity is separated from a gas component having a small specific gravity and hardly affected by gravity within the header, and refrigerant distribution to a plurality of tubes for heat exchange. Tends to be non-uniform. Such non-uniform distribution of the heat exchange medium is noticeable when the heat exchanger is used in such a posture that the header is in the vertical direction. For this reason, the heat exchanger which can make distribution with respect to the tube of heat exchange media, such as a refrigerant | coolant, more uniform is calculated | required.

  In order to improve the non-uniformity of refrigerant distribution, a heat exchanger is formed by bending a plurality of distribution pipes as introduced in Japanese Patent Publication No. 2004-317056 as a prior art into three different shapes. One with a distributor is known. In addition, this document discloses a heat exchanger in which a plurality of distribution pipes are concentrated on a part of an inlet header in which liquid refrigerant is accumulated.

  In a heat exchanger provided with a distributor as disclosed in this document, it is necessary to bend each of the plurality of distribution pipes into different shapes and in a three-dimensionally complicated shape. For this reason, there are many parts and the manufacturing cost tends to become high. Furthermore, since a space is required to arrange the distribution pipe having a three-dimensionally bent shape, the header and the heat exchanger are easily increased in size.

  Furthermore, the heat exchanger described in this document is provided with a refrigerant distribution means using flat distribution pipes, and the flat distribution pipes are concentrated on a part of the header, in particular, the lower part of the header where liquid refrigerant is liable to accumulate. The liquid refrigerant is caused to flow into the heat exchange part. In such a structure, the refrigerant state at the inlets of the plurality of flat distribution pipes approaches uniformly, but the difference in tube pressure loss due to the difference in tube length occurs, so the refrigerant distribution to the plurality of tubes is not necessarily uniform. I can't say. Furthermore, since it becomes the structure which arrange | positions the some flat distribution pipe | tube with a bending part, it is difficult to provide the heat exchanger of a simple structure.

  Japanese Patent Publication No. 2000-249428 includes an inlet header, an outlet header, a plurality of tubes extending between the headers, and a meandering fin interposed between adjacent tubes. An evaporator is disclosed. In this evaporator, a plurality of refrigerant injectors are provided at the inlet to the inlet header. Each of the plurality of refrigerant injectors has an injection orifice. As in the evaporator described in this document, even if an injection orifice is provided at the inlet to the header, it is difficult to inject the refrigerant so that the refrigerant is uniformly distributed throughout the header. Is susceptible to flow rate. It is difficult to incorporate into the header a configuration that allows appropriate distribution according to the flow rate by adjusting the arrangement and orientation of the orifices and the amount of protrusion of the tube into the header. Furthermore, it is difficult to obtain an appropriate refrigerant distribution with respect to fluctuations in conditions such as the flow rate, header direction, and tube internal pressure.

  One aspect of the present invention is a heat exchanger having a plurality of tubes, an inlet header for distributing the heat exchange medium to the plurality of tubes, and an outlet header for recovering the heat exchange medium from the plurality of tubes. It is. The inlet header of the heat exchanger is a circulation pipe through which at least a part of the heat exchange medium flowing into the inlet header can be circulated, and a plurality of tubes are connected to at least a part of the circulation pipe. The circulation pipe and the heat exchange medium are blown out in the axial direction of the circulation pipe to generate a differential pressure for forcibly circulating at least a part of the heat exchange medium flowing into the inlet header through the circulation pipe. Mechanism (differential pressure generating mechanism).

  According to this heat exchanger, at least a part of the heat exchange medium that has flowed into (inflowed into) the inlet header (the heat exchange medium that is already present in the inlet header) is moved in the axial direction of the circulation line by the differential pressure generation mechanism. It is blown out and circulates forcibly in a circulation line communicating with a plurality of tubes. For this reason, the state of the heat exchange medium inside the circulation line constituting the inlet header can be made more uniform or nearly uniform. For example, even when a two-phase heat exchange medium including a gas phase and a liquid phase flows in, the heat exchange medium can be prevented from being separated into a liquid phase component and a gas phase component in the inlet header. For this reason, even if a plurality of tubes are connected in a state where the axial length of the inlet header is dispersed to a certain extent in the axial direction of the inlet header, a more uniform heat exchange medium is distributed to each tube. it can.

  According to this heat exchanger, it is possible to omit a distribution pipe that requires three-dimensional bending. Further, it is possible to omit bending the tube side in order to make the distribution of the heat exchange medium uniform. This does not exclude that the heat exchanger includes these three-dimensional piping and bent piping. However, this heat exchanger makes it possible to make the phase state and flow rate of the heat exchange medium distributed to each tube uniform or close to that with a simpler configuration. For this reason, a heat exchanger with good heat exchange efficiency can be provided at a relatively low cost.

  An example of the differential pressure generating mechanism is driven by external power such as a pump. In some cooling systems, the heat exchange medium flowing into the heat exchanger is decompressed or expanded in advance. In a heat exchanger applied to such a system, it is possible to drive the differential pressure generating mechanism using the energy of the heat exchange medium. In this case, since a new power source is not required in addition to the power source generally used for the heat exchanger, it is economical. That is, it is desirable that the differential pressure generating mechanism is driven by a heat exchange medium flowing into the inlet header. As the differential pressure generating mechanism, for example, a turbocharger such as a supercharger that rotates the turbine at the pressure of the driving portion and forcibly sucks the heat exchange medium at the differential pressure generating portion (pressurizing portion) such as a coaxial compressor. A configuration (approximate to the feeder) can be applied.

  The heat exchange medium flowing into the inlet header sucks at least a part of the heat exchange medium already flowed into the inlet header, and the heat exchange medium flowing into the inlet header and at least the heat exchange medium already flowed into the inlet header A mechanism for mixing and blowing out a part is more preferable as a differential pressure generating mechanism. An example of such a mechanism is an ejector. When the heat exchange medium is discharged from the ejector nozzle (orifice / throttle portion) at high speed (flows into the inlet header), the inside of the nozzle is decompressed. Due to this pressure reduction, at least a part of the heat exchange medium (existing heat exchange medium) that has flowed into the inlet header is sucked, and the heat exchange medium that flows into the inlet header and at least a part of the heat exchange medium that flows into the inlet header And the heat exchange medium flowing into the inlet header is forcibly circulated through the circulation line. In addition, the ejector includes a type in which the heat exchange medium in the inlet header is sucked and mixed using the pressure drop caused by blowing the heat exchange medium from the nozzle.

  At least a part of the circulation line of the inlet header can be constituted by a double pipe or a perforated pipe (multiple pipe, multi-flow pipe). It is preferable that a differential pressure generating mechanism is provided at one end of the double tube or multiple tube, and the other end of the double tube or multiple tube is communicated. In this way, at least a part of the double pipe or the multiple pipe can be used as a circulation line.

  It is possible to supply the differential pressure generating mechanism separately from the inlet header and / or the heat exchanger. Accordingly, another aspect of the present invention includes a plurality of tubes, an inlet header for distributing the heat exchange medium to the plurality of tubes, and an outlet header for recovering the heat exchange medium from the plurality of tubes. The inlet header is a circulation pipe through which at least a part of the heat exchange medium flowing into the inlet header can circulate, and a circulation pipe in which a plurality of tubes are connected to at least a part of the circulation pipe. Including a heat exchanger. Another aspect of the present invention is a header for distributing a heat exchange medium to a plurality of tubes. The header is a circulation conduit that can circulate at least a part of the heat exchange medium that has flowed into the header, and includes a circulation conduit in which a plurality of tubes are connected to at least a portion of the circulation conduit. Yes. This header can be provided with a differential pressure generating mechanism driven by the inflowing heat exchange medium. The differential pressure generating mechanism desirably blows the heat exchange medium from the differential pressure generating mechanism in the axial direction of the circulation pipe. Further, the differential pressure generating mechanism is an ejector for sucking and mixing at least a part of the heat exchange medium that has flowed into the header (already flowed) by the heat exchange medium flowing into the header and blows it out to the circulation pipe. It is desirable to do.

  Furthermore, the present invention includes a heat exchange system including the heat exchanger of one embodiment of the present invention and an apparatus (medium supply system) that supplies a heat exchange medium to the heat exchanger. Such heat exchange systems or systems include refrigeration cycles or refrigeration cycles and refrigeration equipment including such cycles, cooling equipment, air conditioning equipment, storage, showcases, and the like. A system suitable as a refrigeration cycle or a refrigeration cycle uses the heat exchanger of one embodiment of the present invention as an evaporator, pressurizes the heat exchange medium recovered from the evaporator, and cools the pressurized heat exchange medium. System with a condenser.

  The ejector also functions as expansion means for reducing the pressure of the pressurized heat exchange medium and supplying it to the evaporator. Therefore, the inlet header includes a circulation pipe and an ejector for sucking and mixing at least a part of the heat exchange medium flowing into the inlet header and blowing out to the circulation pipe by the heat exchange medium flowing into the inlet header. The heat exchanger is suitable for a cycle and / or system in which refrigerant is circulated as a heat exchange medium. The system including the heat exchanger may include expansion means for decompressing the pressurized heat exchange medium and supplying it to the evaporator in the medium supply system, or may be omitted.

The figure which shows the outline of the heat exchange system containing a heat exchanger. The figure which shows the outline of the heat exchanger concerning 1st Embodiment. The figure which shows the outline of the heat exchanger concerning 2nd Embodiment. The figure which shows the outline of a part of heat exchanger concerning 3rd Embodiment. The figure which shows the outline of a part of heat exchanger concerning 4th Embodiment. The figure which shows the outline of the heat exchanger concerning 5th Embodiment. It is a figure which shows the example provided with the ejector from which a type differs. It is a figure which shows the outline of the heat exchanger concerning 6th Embodiment. It is a figure which shows the cross section of a header. It is a figure which expands and shows the structure of a header.

BEST MODE FOR CARRYING OUT THE INVENTION

  FIG. 1 shows a system 50 that includes a heat exchanger. This system (heat exchange system) 50 includes an air conditioning apparatus and a refrigeration apparatus, and includes other systems that have a heat exchange cycle and a heat exchange cycle called a cooling cycle or a refrigeration cycle. For example, when the system 50 is an air conditioning system, the system (heat exchange system) 50 includes a liquid heat exchange medium (hereinafter referred to as a refrigerant) R and an external fluid (for example, outdoor air) F. Exchange heat with. The system 50 exchanges heat between the evaporator (evaporator) 100 that cools the indoor air G by heat exchange with the refrigerant R, and the compressed gaseous refrigerant R and the external fluid F, thereby converting the refrigerant R into a liquid state. A condenser (condenser) 200 is provided.

  Further, as a medium supply system 55 that circulates the refrigerant R and supplies the refrigerant R to the evaporator 100, the system 50 includes a compressor 51 that pressurizes the refrigerant R in addition to the capacitor 200, and an accumulator 52 that temporarily stores the refrigerant R. And an apparatus such as an expansion valve 53 for expanding the refrigerant R supplied to the evaporator 100. In the system 50, the refrigerant R in the evaporator 100 flows out from the refrigerant outlet of the evaporator 100, passes through the accumulator 52, the compressor 51, the condenser 200, and the expansion valve 53, and again enters the evaporator 100 from the refrigerant inlet of the evaporator 100. It circulates so that it may flow into.

  FIG. 2 shows a heat exchanger 100a according to the first embodiment of the present invention. This heat exchanger 100 a can be used as the evaporator 100 of the system 50. The heat exchanger 100 a includes an inlet header 1 including a refrigerant inlet 6, an outlet header 2 including a refrigerant outlet 5, and a heat exchange unit 20. The inlet header 1 and the outlet header 2 extend in the vertical direction, and are arranged so as to be parallel to each other. The heat exchanging unit 20 is for exchanging heat between the refrigerant R and the air G to cool the air G and the like. The heat exchanging unit 20 includes a plurality of tubes 4 arranged in parallel to each other in the horizontal direction so that the inlet header 1 and the outlet header 2 communicate with each other, and fins 3 extending in the vertical direction perpendicular to the tubes 4. Yes.

  A typical tube 4 has a circular cross section, but it may be a flat tube with a flat cross section, or a perforated tube (multiple tube) in which the inside of the tube is divided into a plurality of portions. good. A typical fin 3 is a plurality of plate-like fins that are arranged in parallel to each other and attached so that the tube 4 passes therethrough. The fin 3 may be a corrugated fin that connects between the tubes 4 while meandering, a fin protruding from the tube 4 or a pin.

  The inlet header 1 has a function as a distributor for distributing the refrigerant R to the plurality of tubes 4 of the heat exchange unit 20. The outlet header 2 has a function of collecting the refrigerant R from each tube 4. Each tube 4 has one end connected to the inlet header 1 and the other end connected to the outlet header 2. The plurality of tubes 4 can increase the heat exchange area by the tubes themselves by adopting the flat tubes, and further increase the heat exchange area (contact area) with the air G by providing the fins 3. Heat exchange efficiency can be improved. In order to avoid the effects of icing, frosting, etc., fins may not be provided or the area occupied by the fins may be reduced.

  The inlet header 1 includes a circulation line 10 and a differential pressure generating mechanism 11 for forcibly circulating at least a part of the refrigerant R flowing into the inlet header 1. Circulation duct 10 includes a straight tubular forward path 10a and a substantially U-shaped return path 10b connected from one end of the forward path 10a to the other end. The forward path 10a guides the refrigerant R from the refrigerant inlet 6 at one end to the opposite end. On the contrary, the return path 10b guides the refrigerant from the opposite end of the forward path 10a to the refrigerant inlet 6. Therefore, at least a part of the refrigerant R flowing into the inlet header 1 can be circulated by the circulation pipe 10 including the forward path 10a and the return path 10b.

  The differential pressure generating mechanism 11 is an ejector that includes a throttle portion 7 and a suction portion 8, and is provided in the vicinity of the refrigerant inlet 6 of the inlet header 1. The return path 10 b of the circulation pipe 10 connects the vicinity of the rear end (upper end) 15, which is the opposite side of the refrigerant inlet 6 of the inlet header 1, and the suction part 8 of the differential pressure generating mechanism 11. Is provided. Therefore, the differential pressure generating mechanism 11 is driven by the refrigerant R flowing into the inlet header 1 and sucks and mixes at least a part of the refrigerant (existing refrigerant) R that has already flowed into the inlet header 1 through the return path 10b. It blows out to the outward path 10a. In the inlet header 1 of the heat exchanger 100a, a plurality of tubes 4 are connected to an outward path 10a that is a part of the circulation line 10. That is, a plurality of tubes 4 are connected at substantially equal intervals between the suction path 9 that is a branch of the return path 10 b of the circulation pipe 10 and the differential pressure generating mechanism 11.

  In the heat exchanger 100a applied as an evaporator of the heat exchange system 50, the refrigerant R in a two-phase state in which a gas and a liquid are mixed enters from the refrigerant inlet 6 by the action of the accumulator 52, the compressor 51, the expansion valve 53, and the like. Supplied to the header 1 and passes through the throttle part 7 of the suction part 8. When the refrigerant R flows into the inlet header 1 at a high speed via the throttle portion 7, the inside of the throttle portion 7 is decompressed. By this pressure reduction, at least a part of the existing refrigerant R that has flowed into the inlet header 1 through the suction portion 8 via the return path 10b is sucked. Then, the refrigerant R flowing into the inlet header 1 and at least a part of the refrigerant R flowing into the inlet header 1 are mixed, and the refrigerant R enters the inlet from the differential pressure generating mechanism 11 as indicated by arrows in FIG. It is ejected in the direction of the axis L of the circulation pipe line 10 into the header 1. And a part of it returns to the suction part 8 through the forward path 10a and the return path 10b again. For this reason, at least a part of the refrigerant R is forcibly circulated in the header 1, so that the state of the refrigerant R in the pipe-like inlet header 1 having a long axial length is uniform. . In other words, by giving a pressure difference that forcibly circulates the refrigerant R in the header 1, it is possible to prevent the occurrence of a state where the liquid phase and the gas phase are separated due to the head difference in a static state.

  Therefore, in this heat exchanger 100a, a plurality of tubes 4 are connected at approximately equal intervals in the middle of the forward path 10a through which the refrigerant R flows from the bottom to the top. A part of the refrigerant R is distributed from the inlet header 1 to each tube 4, and the state of the refrigerant R distributed to each tube 4 can be made uniform. Further, since the state of the refrigerant R in the forward path 10a is homogenized including the state of gas-liquid mixing, the amount of the refrigerant R distributed to each tube 4 can be made uniform.

  The refrigerant R uniformly distributed to the respective tubes 4 in this way exchanges heat with the air G and the like via the plurality of tubes 4 and the plurality of fins 3 and is output to the outlet header 2, and is supplied from the refrigerant outlet 5 to the system. It flows out into 50 systems. Therefore, the heat exchange load in each tube 4 is made uniform, and the heat exchanger 100a with favorable heat exchange efficiency is obtained. Furthermore, it is not necessary to bend two or three-dimensionally into different shapes in order to distribute the refrigerant uniformly to each tube, and the heat exchange efficiency is good with a simple and compact configuration. Can be provided at a relatively low cost. Moreover, since the shape of each tube 4 can be made the same, generation | occurrence | production of the pressure loss difference in each tube 4 can be prevented, and a heat exchange efficiency can be improved also in this point.

  Further, according to the heat exchanger 100a, it is possible to prevent phase separation from occurring due to a head difference in the inlet header 1. For this reason, the arrangement direction (direction) of the inlet header 1 of the heat exchanger 100a can be freely set. Therefore, the heat exchanger 100a may be used in a posture in which the inlet header 1 is arranged in the horizontal direction, or may be used in a posture in which the inlet header 1 is arranged in the vertical direction. Further, when the inlet header 1 is used in the vertical direction, the refrigerant R may flow from the lower side of the inlet header 1 or the refrigerant R may flow from the upper side of the inlet header 1. Furthermore, unlike these postures, the heat exchanger 100a can be used in various postures including the oblique arrangement of the inlet header 1, and when the heat exchanger 100a is used in those postures, a plurality of tubes 4 are filled with refrigerant. R can be distributed uniformly.

  Furthermore, since the heat exchanger 100a can be easily downsized, the cooling system 50 including the heat exchanger 100a can be arranged in a compact manner. Further, since the heat exchanger 100a employs the differential pressure generating mechanism 11 using the ejector effect, a new power source is used in addition to the power source generally used in the heat exchanger, for example, the power of the compressor 51. Do not need. Therefore, it is economical. In addition, by assigning a part of the pressure loss due to the expansion valve 53 to the ejector 11 that is the differential pressure generating mechanism, it is possible to improve the heat exchange efficiency without impairing the economy of the system 50. Further, if the expansion (pressure loss) by the ejector 11 is sufficient, the expansion valve 53 can be omitted.

  FIG. 3 shows a heat exchanger 100b according to the second embodiment of the present invention. This heat exchanger 100b can also be used as the evaporator 100 of the heat exchange system 50 as described above. In this heat exchanger 100b, a plurality of tubes 4 are connected to the return path 10b of the circulation pipe 10 of the inlet header 1 at substantially equal intervals. In the circulation line 10 where at least a part of the refrigerant R is forcibly circulated, the state of the refrigerant R is substantially constant not only in the forward path 10a but also in the return path 10b. Therefore, even if each tube 4 is connected to the return path 10b, the refrigerant R can be distributed almost uniformly to each tube 4. Further, the phase state of the refrigerant R sucked and mixed is more likely to be stable at a position slightly away from the throttle portion 7 than the position immediately after the throttle portion 7 of the ejector 11, for example, the return path 10b. In this heat exchanger 100b, since each tube 4 is connected to the return path 10b, the ejector 11 having the throttle portion 7 and each tube 4 are separated from each other. Therefore, the refrigerant R having a stable phase state can be distributed to each tube 4.

  FIG. 4 shows a heat exchanger 100c according to the third embodiment of the present invention. This heat exchanger 100c can also be used as the evaporator 100 of the heat exchange system 50 as described above. In this heat exchanger 100 c, the inlet header 1 includes a U-shaped pipe including two straight pipe portions, and the U-shaped open side is connected by a suction path 9. Therefore, the inlet header 1 includes a circulation pipe (circulation circuit) 10, and a plurality of tubes 4 are connected to both the forward path 10 a and the return path 10 b of the circulation pipe 10. Therefore, it becomes possible to supply the refrigerant R in a substantially uniform state to the plurality of tubes 4 arranged in two rows of the forward path 10a and the backward path 10b. According to the heat exchanger 100c, the heat exchange rate in the heat exchange unit 20 can be further increased without changing the plane area (projected area) of the heat exchange unit 20.

  FIG. 5 shows a heat exchanger 100d according to the fourth embodiment of the present invention. The heat exchanger 100d includes two heat exchange units 20a and 20b, and can be used as the evaporator 100 of the heat exchange system 50 as described above. In this heat exchanger 100d, the heat exchange units 20a and 20b are provided with a common inlet header 1, and the plurality of tubes 4 of one heat exchange unit 20a are connected to the forward path 10a of the circulation line 10 of the header 1, A plurality of tubes 4 of the other heat exchange part 20b are connected to the return path 10b. Therefore, the refrigerant | coolant R can be equally distributed using the one inlet header 1 with respect to each of the tube 4 of the some heat exchange parts 20a and 20b. There may be three or more heat exchange units connectable to one inlet header.

  FIG. 6 shows a heat exchanger 100e according to the fifth embodiment of the present invention. This heat exchanger 100e can also be used as the evaporator 100 of the heat exchange system 50 as described above. The inlet header 1 of the heat exchanger 100 e includes a double pipe 12, and a differential pressure generating mechanism (ejector) 11 is provided at the lower end of the double pipe 12. Further, the upper end portion of the double pipe 12 communicates with the inner pipe 12a and the outer pipe 12b. In the inlet header 1, an ejector 11 is installed so as to blow out the refrigerant R in the axial direction of the inner pipe 12 a inside the double pipe 12. Accordingly, the inner pipe 12a of the double pipe 12 forms the forward path, and the outer pipe 12b forms the return path, and the circulation pipe 10 is configured by them. And the some tube 4 is connected to the outer tube | pipe 12b which is a return path. In this heat exchanger 100a, since the circulation line 10 can be configured in one pipe, a heat exchanger having a more compact and simple appearance can be provided. In order to realize the circulation pipe 10 with an integral pipe, not only a double pipe but also a multiple pipe (perforated pipe) having an appropriate number of partition walls inside may be used.

  FIG. 7 shows a different example of the differential pressure generating mechanism 11. The differential pressure generating mechanism 11 of each of the above embodiments is an ejector in which a suction part 8 is provided in the throttle part 7 of the venturi tube. On the other hand, the differential pressure generating mechanism 11 shown in FIG. 7 is a spray type ejector. This differential pressure generating mechanism 11 includes a suction nozzle 17 for generating a differential pressure for suction in the vicinity of the refrigerant inlet 6 of the header 1, and reduces the refrigerant R flowing into the header 1 to circulate the pipeline. Blow out in the axial direction of the forward path 10a. In the vicinity of the suction nozzle 17 in the forward path 10a, a suction hole 18 is provided for sucking the existing refrigerant R that has already flowed into the header 1 from the return path 10b. For this reason, due to the pressure drop due to the refrigerant R blown from the suction nozzle 17, the refrigerant R flowing into the header 1 from the return path 10b is sucked into the forward path 10a and blown out in the axial direction of the forward path 10a. For this reason, the refrigerant R is forcibly circulated through the circulation line 10 constituting the header 1 by the differential pressure generating mechanism 11.

  8, FIG. 9 and FIG. 10 show a configuration in the vicinity of the header 1 of the heat exchanger 100f according to the sixth embodiment of the present invention. This heat exchanger 100f can also be used as the evaporator 100 of the heat exchange system 50 as described above. The inlet header 1 of the heat exchanger 100f is composed of a double pipe 12 having an inner pipe 12a and an outer pipe 12b, and the inner pipe 12a and the outer pipe 12b communicate with each other at the upper part of the header 1. More specifically, the outer tube 12b is composed of two members 13a and 13b having a semicircular cross section formed by extrusion and cutting. A plurality of flat tubes 14 are attached to the inner member 13b, and these flat tubes 14 are connected to an outlet header (not shown). A member 15 having a semicircular cross section is attached to the outer member 13a to form an inner tube 12a. Both ends of the two members 13a and 13b constituting the outer tube 12b are closed with caps 16. A nozzle 17 is attached to the lower end of the inner pipe 12a, and the refrigerant R flowing into the header 1 is blown out into the inner pipe 12a. The nozzle 17 serves as a differential pressure generating mechanism 11, and the existing (inflowed) refrigerant R from the outer pipe 1b is moved under the inner pipe 12a by the suction force of the refrigerant R blown upward from the lower side of the inner pipe 12a. It is sucked into the inner tube 12a through the gap 18 on the side.

  Also in this heat exchanger 100f, the header 1 includes the inner pipe 12a and the outer pipe 12b, and includes the circulation path 10 communicating with the tube 14, and the refrigerant R is forcibly circulated through the circulation path 10. For this reason, the state of the refrigerant R inside the header 1 can be made even more uniform, and a heat exchanger with high heat exchange efficiency can be provided.

  In the first to sixth embodiments, the heat exchanger used in the posture in which the header is arranged along the vertical direction has been described as an example. However, the heat exchanger has a posture in which the header is arranged along the horizontal direction. It is also possible to use it.

  In the first to sixth embodiments, the differential pressure generating mechanism driven by the heat exchange medium flowing into the header and the circulation pipe for circulating at least a part of the heat exchange medium flowed into the header However, the circulation means is not limited to this. The circulating means may be any means that forcibly circulates at least a part of the heat exchange medium (refrigerant) flowing into the header.

  The differential pressure generating mechanism including an ejector nozzle (orifice / throttle portion) is a preferred example of the present invention, and is provided in the vicinity of the refrigerant inlet of the header, whereby the refrigerant that has flowed into the inlet header by the refrigerant flowing into the inlet header. At least a part of the refrigerant can be sucked and mixed, and the mixed refrigerant can be blown out to the header. Therefore, it is suitable for a system including a cycle and a cycle of circulating the refrigerant as described above, in which the internal pressure of the heat exchanger is set low.

  Another example of the differential pressure generating mechanism driven by the refrigerant flowing into the header is that the turbine is rotated by the pressure of the driving part, and the heat exchange medium is supplied by the differential pressure generating part (pressurizing part) such as a coaxial compressor. It is a supercharger-like configuration. In a configuration similar to this supercharger, there is a configuration in which a drive portion and a differential pressure generating portion (pressurizing portion) are separated and mechanically connected. Furthermore, it is possible to employ a differential pressure generating mechanism such as a pump that operates with separate power. That is, the differential pressure generating mechanism may be a mechanism that sends out the refrigerant circulating in the inlet header without being mixed with the refrigerant flowing into the inlet header. A differential pressure generating mechanism such as a pump pressurizes the refrigerant in the inlet header to forcibly circulate, and the differential pressure generating mechanism may not be provided near the refrigerant inlet of the header. Such a differential pressure generating mechanism may be provided in the middle of the circulation pipe, for example, a pipe not connected to the header in the forward path or the return path, a connection path of these pipes, and the like. It is also possible to adopt a configuration in which the differential pressure generating mechanism can be attached to and detached from the circulation line of the header.

  Furthermore, a heat exchanger and a heat exchange included in the embodiment of the present invention are provided by additionally installing a pipe line functioning as an outward path or a return path and an appropriate differential pressure generating mechanism with respect to a header that does not circulate refrigerant. It is also possible to configure the system.

  In the present embodiment, the heat exchanger having the plate-like fins as the heat exchanger has been described as an example, but the fin shape is not limited to the plate shape. Moreover, the heat exchange part should just be able to perform heat exchange between refrigerant | coolants (heat exchange medium) and external fluids, such as air, and the shape and structure of a heat exchange part are also limited to these. It is not something.

  The system of the present invention is not limited to air conditioning, but includes devices and systems that include various types of heat exchange as part of their functions, such as radiators, various cooling devices, and various refrigeration devices.

Claims (9)

Multiple tubes,
An inlet header for distributing the heat exchange medium to the plurality of tubes;
An outlet header for recovering the heat exchange medium from the plurality of tubes,
The inlet header is
A circulation conduit in which at least a part of the heat exchange medium flowing into the inlet header can circulate, comprising a forward passage and a return passage, and at least a circulation conduit in which the plurality of tubes are connected to the return passage;
A differential pressure generating mechanism for blowing out the heat exchange medium in the axial direction of the circulation pipe and forcibly circulating at least a part of the heat exchange medium flowing into the inlet header through the circulation pipe. A differential pressure generating mechanism that sucks and mixes at least a part of the heat exchange medium flowing into the inlet header with the heat exchange medium flowing into the inlet header, and blows out to the forward path of the circulation pipe,
The inlet header is disposed along the vertical direction with the differential pressure generating mechanism down, and a heat exchange medium is blown out from the bottom upward by the differential pressure generating mechanism.   2. The heat exchanger according to claim 1, wherein the differential pressure generating mechanism is driven by a heat exchange medium flowing into the inlet header. 3. The inlet header according to claim 1, wherein the inlet header includes a double pipe or a multiple pipe constituting at least a part of the circulation pipe, and the differential pressure generating mechanism is one end of the double pipe or the multiple pipe. The heat exchanger which is provided in the section and communicates with the other end of the double pipe or the multiple pipe. A system comprising: the heat exchanger according to claim 1; and a medium supply system that supplies a heat exchange medium to the heat exchanger. 5. The system according to claim 4 , wherein the medium supply system includes a device that pressurizes the heat exchange medium recovered from the heat exchanger, and a condenser that cools the pressurized heat exchange medium. Multiple tubes,
An inlet header for distributing the heat exchange medium to the plurality of tubes;
An outlet header for recovering the heat exchange medium from the plurality of tubes,
The inlet header is
A circulation conduit in which at least a part of the heat exchange medium that has flowed into the inlet header is circulated, comprising a forward passage and a return passage, and at least a circulation conduit in which the plurality of tubes are connected to the return passage;
An ejector for sucking and mixing at least a part of the heat exchange medium flowing into the inlet header and blowing it out to the forward path of the circulation pipe by the heat exchange medium flowing into the inlet header;
The said inlet header is arrange | positioned so that the said ejector may be followed along a perpendicular direction, and a heat exchange medium is blown out from the bottom upwards by the said ejector. The heat exchanger according to claim 6 , and a medium supply system that supplies a heat exchange medium using the heat exchanger as an evaporator,
The said medium supply system is a heat exchange system provided with the apparatus which pressurizes the heat exchange medium collect | recovered from the said evaporator, and the condenser which cools the pressurized heat exchange medium. A header for distributing a heat exchange medium to a plurality of tubes,
A circulation conduit that can circulate at least a part of the heat exchange medium that has flowed into the header, includes a forward path and a return path, and an inlet of the heat exchange medium is provided at one end of the forward path, and at least the return path A circulation line to which the plurality of tubes are connected,
A differential pressure generating mechanism that generates a differential pressure for blowing out the heat exchange medium including at least a part of the heat exchange medium flowing into the header in the axial direction of the circulation pipe by the heat exchange medium flowing into the header. A suction pressure mixing mechanism that sucks and mixes at least a part of the heat exchange medium that has flowed into the header with the heat exchange medium that flows into the header, and blows out to the forward path of the circulation pipe;
A header that is arranged along the vertical direction with the differential pressure generating mechanism facing down, and a heat exchange medium is blown out from below to above by the differential pressure generating mechanism. A header for distributing a heat exchange medium to a plurality of tubes,
A circulation conduit that can circulate at least a part of the heat exchange medium that has flowed into the header, includes a forward path and a return path, and an inlet of the heat exchange medium is provided at one end of the forward path, and at least the return path A circulation line to which the plurality of tubes are connected,
The heat exchange medium flowing into the header has an ejector for sucking and mixing at least a part of the heat exchange medium flowing into the header and blowing it out to the forward path of the circulation pipe,
The header which is arrange | positioned so that the said ejector may be followed along a perpendicular direction, and a heat exchange medium is blown out upwards from the bottom by the said ejector.

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