CN210165621U - Heat exchanger and air conditioning equipment - Google Patents
Heat exchanger and air conditioning equipment Download PDFInfo
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- CN210165621U CN210165621U CN201920870673.0U CN201920870673U CN210165621U CN 210165621 U CN210165621 U CN 210165621U CN 201920870673 U CN201920870673 U CN 201920870673U CN 210165621 U CN210165621 U CN 210165621U
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Abstract
The utility model provides an air conditioning equipment and heat exchanger thereof, the heat exchanger includes: the plurality of superposed first-shaped fins comprise first inlet collecting holes and second inlet collecting holes, the first inlet collecting holes are communicated with the second inlet collecting holes through throttle channels arranged in the first-shaped fins, the inner walls of the second inlet collecting holes are provided with inlets of the throttle channels, and the inner walls of the first inlet collecting holes are provided with outlets of the throttle channels; the inner wall of the first inlet collecting hole is also provided with a plurality of inlets of the refrigerant flow paths so as to form a plurality of refrigerant flow paths by extending towards the other end of the first-shaped fin, the plurality of first inlet collecting holes form a first inlet collecting channel along the thickness direction, and the cross-sectional area of the first inlet collecting channel is larger than or equal to the total area of the inlets of the plurality of throttling channels on the inner wall of the first inlet collecting channel. The utility model provides a heat exchanger is favorable to promoting the efficiency of gas-liquid mixture to reach the probability that promotes refrigerant distribution in a plurality of refrigerant flow paths.
Description
Technical Field
The utility model relates to an air conditioning equipment technical field particularly, relates to a heat exchanger and contain air conditioning equipment of this heat exchanger.
Background
In the related art, the heat exchanger includes a fin tube heat exchanger and a microchannel heat exchanger, wherein, for the layout, the circular tube or flat tube portion adopts the mode of laying along the horizontal direction, and the fin portion adopts the vertical direction setting, and for the equipment, the tube and the fin of the fin tube heat exchanger are combined through the expand tube, and the microchannel heat exchanger is combined through welding, and the heat exchanger of the above-mentioned structure has the following defects:
the circular tubes or flat tubes placed in the horizontal direction have a problem of difficult refrigerant distribution due to a large number of circular tubes or flat tubes affected by gravity.
SUMMERY OF THE UTILITY MODEL
In order to solve at least one of the above technical problems, an object of the present invention is to provide a heat exchanger.
Another object of the utility model is to provide an air conditioning equipment including above-mentioned heat exchanger.
In order to achieve the above object, the present invention provides a heat exchanger for an air conditioner, including: the first-shaped fins are stacked, one ends of the first-shaped fins are provided with a plurality of inlet current collecting holes which are formed in the thickness direction side by side, the first-shaped fins at least comprise first inlet current collecting holes and second inlet current collecting holes, the first inlet current collecting holes and the first-second inlet current collecting holes are communicated through throttle channels formed in the first-shaped fins, the inner walls of the second inlet current collecting holes are provided with inlets of the throttle channels, and the inner walls of the first inlet current collecting holes are provided with outlets of the throttle channels; the inner wall of the first inlet collecting hole is further provided with a plurality of inlets of refrigerant flow paths, so that the refrigerant flow paths are constructed by extending towards the other ends of the first shape fins, wherein the first shape fins are overlapped to enable a plurality of second inlet collecting holes to construct a first inlet collecting channel along the thickness direction, the first inlet collecting holes construct a first inlet collecting channel along the thickness direction, and for the whole heat exchanger, the cross sectional area of the second inlet collecting channel is larger than or equal to the total inlet area of all throttling channels in the second inlet collecting channel.
The utility model discloses technical scheme of first aspect provides a heat exchanger, including two at least entry mass flow passageways, the refrigerant gets into the back from the entry mass flow passageway of front end, throttle through the throttle passageway, form the double-phase refrigerant of gas-liquid, the refrigerant gets into the entry mass flow passageway of rear end with double-phase form, set up the entry of refrigerant flow path on the inner wall of rear end mass flow passageway, so that the double-phase refrigerant of gas-liquid gets into the refrigerant flow path, and then can promote the refrigerant and get into every refrigerant flow path homogeneity, in order to guarantee refrigerant distribution effect, can carry out the heat transfer with the outside air at the flow in-process, in order to accomplish the heat transfer operation, the refrigerant of accomplishing the heat transfer operation is discharged from export.
Further, by limiting the relationship between the cross-sectional area of the second inlet collecting channel and the total inlet area of the throttling channels on the inner wall of the second inlet collecting channel, that is, the cross-sectional area of the second inlet collecting channel is greater than or equal to the total inlet area of the throttling channels on the inner wall of the second inlet collecting channel, under such a condition, the pressure of the refrigerant in the second inlet collecting channel can be increased, so that the gas-liquid mixing efficiency is improved, and the probability of refrigerant distribution in a plurality of refrigerant flow paths is improved.
Specifically, the throttle passage is a passage of a constant sectional area, and therefore the inlet area of the throttle passage is the sectional area of the throttle passage.
As can be understood by those skilled in the art, the throttling channel and the refrigerant flow path are formed between the upper surface and the lower surface of the fin, and the size of the cross section of the throttling channel and the refrigerant flow path is related to the thickness of the fin plate, for example, when the thickness of the fin plate is smaller, the height of the corresponding cross section is relatively smaller.
Further, the cross-sectional area of the second inlet collecting channel is larger than the total inlet area of the plurality of throttle channels on the inner wall of the second inlet collecting channel.
In the technical scheme, the cross sectional area of the second inlet collecting channel is set to be larger than the total inlet area of all throttling channels on the inner wall of the second inlet collecting channel, so that the gas-liquid mixing effect can be further improved.
In any of the above technical solutions, optionally, an outlet collecting hole is formed in the other end of the first-shaped fin along the thickness direction, and a plurality of outlet collecting holes are stacked to construct an outlet collecting channel along the thickness direction; the inner wall of the outlet collecting hole is provided with outlets of the plurality of refrigerant flow paths, so that the outlet collecting hole is communicated with the first inlet collecting hole through the plurality of refrigerant flow paths, the sum of the sectional areas of all the refrigerant flow paths in the heat exchanger is determined as a first area, the sectional area of the outlet collecting channel is determined as a second area, and the ratio of the first area to the second area is greater than or equal to 0.8 and less than or equal to 1.
Namely, the sum of the sectional areas of all the heat exchange tubes of the whole heat exchanger is approximately equal to the sectional area of the outlet collecting pipe, or the sectional area of the outlet collecting pipe is slightly larger than the sum of the sectional areas of all the heat exchange tubes of the whole heat exchanger, but not exceeding the proportion range.
The difference between the cross-sectional area of the outlet collecting and flowing channel and the total outlet area of the refrigerant flow path is limited by the preset area difference value and cannot be too large.
In the technical scheme, the relationship between the cross-sectional area of the outlet collecting channel and the total outlet area of the refrigerant flow path is further defined, namely the cross-sectional area of the outlet collecting channel is slightly larger than the total outlet area of the refrigerant flow path, but the difference value between the cross-sectional area and the total outlet area is not too large, so that the performance deterioration of the heat exchanger on the refrigerant outlet side is prevented.
Specifically, by limiting the relation between the cross-sectional area of the outlet collecting flow channel and the total outlet area of the refrigerant flow channel, the refrigerant can be prevented from causing pressure shock when flowing into the outlet collecting flow channel from the refrigerant flow channel, and the performance of the heat exchanger on the outlet side is further ensured.
In any of the foregoing technical solutions, optionally, the first inlet manifold includes a first inlet manifold opening formed in the first fin, and a first tube segment disposed at the first inlet manifold opening; the second inlet collecting hole comprises a second inlet collecting port formed in the first fin and a second pipe section arranged at the second inlet collecting port; the outlet collecting hole comprises an outlet collecting port formed in the first fin and a fifth third pipe section arranged at the outlet collecting port.
In this technical scheme, set up the current collecting port through the plate body at the fin, the structure of current collecting hole is constructed to the form of the integrated pipe section on current collecting port, form the structure of mass flow passageway through the fin of adjacent current collecting hole butt joint or concatenation form from the fin of head end to the fin of tail end, in order to constitute the heat exchanger of integrative structure, on the one hand, in the complexity that is favorable to reducing the preparation, also be favorable to promoting the heat exchange efficiency of heat exchanger, on the other hand, for the fin tubular heat exchanger among the correlation technique, because do not need pipe and fin to carry out the contact equipment, promote the heat exchange efficiency of fin.
In any of the above technical solutions, optionally, the first tube segment includes a first tube segment and a second tube segment disposed on two sides of the first inlet manifold, the second tube segment includes a third tube segment and a fourth tube segment disposed on two sides of the second inlet manifold, the third tube segment includes a fifth tube segment and a sixth tube segment disposed on two sides of the outlet manifold, two adjacent first fins are sleeved with each other through the first tube segment of one of the fins and the second tube segment of another fin, the third tube segment of one of the fins and the fourth tube segment of another fin are sleeved with each other, and the fifth tube segment of one of the fins and the sixth tube segment of another upper fin are sleeved with each other.
In the technical scheme, as an assembling mode of an integrated structure, the adjacent sub-pipe sections can be assembled in a mode of mutually sleeving, and further, the sub-pipe sections mutually sleeved can be in interference fit, so that the assembling strength is ensured, and the refrigerant leakage can be prevented.
In any of the above technical solutions, optionally, the first inlet collecting channel, the second inlet collecting channel, and the outlet collecting channel are all disposed along a horizontal direction, one end of the first shaped fin is defined as a high-position end, and the other end is defined as a low-position end, so that a refrigerant flows from the high-position end to the low-position end or from the low-position end to the high-position end in the refrigerant flow path.
In this technical scheme, to the heat exchanger that this application was injectd, entry mass flow channel sets up with export mass flow channel level, can guarantee the smoothness nature of refrigerant input and output, furtherly, locate different high departments with export mass flow hole and entry mass flow hole respectively, make the refrigerant flow direction low level or from the low bit to high level from the high position, thereby can be unanimous with the direction of gravity or keep less angle, compare with the mode that refrigerant flow path level among the correlation technique was laid, on the one hand, when using the heat transfer as the evaporimeter, can promote the emission effect of comdenstion water, with the loss of pressure that reduces the air side, on the other hand, the influence of the gravity that receives when can reducing the refrigerant distribution, and then promote the homogeneity of two-phase refrigerant distribution.
In any of the above technical solutions, optionally, the refrigerant flow path includes a first section flow path communicated with the first inlet manifold, a second section flow path communicated with the outlet manifold, and a third section flow path disposed between the first section flow path and the second section flow path, where the first section flow path is configured as an arc-shaped flow path, the second section flow path is configured as an arc-shaped flow path, and the third section flow path is configured as a straight-shaped flow path.
In the technical scheme, as a setting mode of the refrigerant flow path, a first section of flow path communicated with the first inlet collecting hole is set to be an arc-shaped flow path, so that two-phase refrigerant forming vortex can uniformly enter different refrigerant flow paths under the action of centrifugal force, and in addition, a second section of flow path communicated with the outlet collecting hole is also set to be an arc-shaped flow path, so that the refrigerant after heat exchange can directly enter the outlet collecting hole, and is conveniently discharged from the heat exchanger.
In any of the above technical solutions, optionally, the third section of flow path is a linear flow path, and an included angle between the linear flow path and the gravity direction is smaller than an angle threshold.
The angle threshold value represents the inclination of the third-stage flow path with respect to the direction of gravity, and may range from 0 ° or more to 15 ° or less.
In the technical scheme, the third section of flow path is defined as the linear flow path extending along the gravity direction, so that on one hand, the flowing fluency of the refrigerant in the refrigerant flow path can be improved to ensure the heat exchange effect, and on the other hand, the third section of flow path is vertically arranged, so that the path length difference of each refrigerant flow path is relatively small, and the refrigerant distribution uniformity is ensured in the aspect of the path length.
In any of the above technical solutions, optionally, the cross section of the throttling channel is circular or polygonal; and/or the cross section of the refrigerant flow path is circular or polygonal.
In any of the above solutions, optionally, the second inlet manifold is disposed near an end of the first-shaped fin opposite to the first inlet manifold.
In the technical scheme, the fins are arranged to be of a long strip-shaped structure, the second inlet collecting hole, the throttling channel, the first inlet collecting hole, the refrigerant flow path and the outlet collecting hole are sequentially arranged from one end (inlet end) to the other end (outlet end) of each fin, and the refrigerant flows into and flows out of the heat exchanger along the flow direction, so that the heat exchange efficiency is guaranteed.
In any of the above technical solutions, optionally, the method further includes: a plurality of second shaped fins, said second shaped fins being opposite to said first shaped fins, said throttling passage not being provided, said plurality of second shaped fins being stacked with said plurality of first shaped fins to construct said heat exchanger.
In the technical scheme, the second type of fins without throttling channels are arranged, so that the number of the fins can be increased on the premise that the cross-sectional area of the first inlet collecting pipe is larger than or equal to the total inlet area of the throttling channels on the inner wall of the first inlet collecting pipe, and the number of refrigerant flow paths is increased.
In any of the above technical solutions, optionally, the second shaped fins and the first shaped fins are alternately stacked to construct the heat exchanger.
In the technical scheme, the first-shaped fins and the second-shaped fins are alternately overlapped, so that the refrigerant distribution uniformity during arrangement of the second-shaped fins is improved.
The utility model discloses the air conditioning equipment that technical scheme of second aspect provided, because of including any one in the first aspect technical scheme the heat exchanger, therefore have all beneficial effects that any one of above-mentioned technical scheme had, no longer describe here.
The air conditioning equipment can be an integral air conditioner, and the heat exchanger is arranged in the integral air conditioner.
The air conditioning equipment can also be a split air conditioner which comprises an indoor unit and an outdoor unit, and the heat exchanger is arranged in the indoor unit and/or the outdoor unit.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
fig. 1 shows a schematic structural view of a fin according to an embodiment of the invention;
fig. 2 shows a partial structural schematic of a fin according to an embodiment of the invention;
fig. 3 shows a schematic cross-sectional view of a heat exchanger according to the present invention along the longitudinal direction and a schematic partial view at a;
fig. 4 shows an indicative plot of the cross-sectional area of the second inlet collecting channel versus the cross-sectional area of the throttling channel in fig. 3;
FIG. 5 shows a schematic cross-sectional view of the heat exchanger of FIG. 3 taken horizontally and then in the longitudinal direction, and a partial schematic view at B;
fig. 6 shows an indication diagram of the cross-sectional area of the outlet collecting channel and the cross-sectional area of the refrigerant flow path in fig. 5;
fig. 7 is a schematic structural view of a single structure of the fin according to some embodiments of the present invention and a partial structural view at C;
fig. 8 is a partial schematic structural view of a fin according to some embodiments of the present invention and a partial schematic structural view at D;
fig. 9 is a first schematic comparison graph of a heat exchanger of the present invention and a heat exchanger of the related art;
fig. 10 is a second graph schematically comparing a heat exchanger according to the present invention with a heat exchanger according to the related art;
fig. 11 is a third schematic comparison graph of the heat exchanger of the present invention and the heat exchanger of the related art.
Wherein, the correspondence between the reference numbers and the component names in fig. 1 to 8 is:
| marking | Name of component | Marking | Name of |
|
| 1 | |
10 | First shaped |
|
| 102 | |
104 | |
|
| 106 | |
108 | |
|
| 110 | |
108A | First |
|
| 108B | Second |
108C | Third |
|
| 112 | |
20 | |
|
| 30 | Outlet |
| Throttling groove | |
| 108D | Refrigerant flow channel groove |
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention more clearly understood, the present invention will be described in further detail with reference to the accompanying drawings and detailed description. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.
A heat exchanger and an air conditioner according to some embodiments of the present invention will be described with reference to fig. 1 to 8.
The utility model discloses a heat exchanger for air conditioning equipment of embodiment, include: as shown in fig. 3 and 5, each fin has a plurality of inlet collecting holes, a plurality of refrigerant channels, and a plurality of outlet collecting holes, and a throttling channel is disposed between two adjacent inlet collecting holes.
As shown in fig. 1, specifically, for a plurality of first-shaped fins 10 arranged in an overlapping manner, one fin 10 includes a plate body 112, as shown in fig. 2, one end of the first-shaped fin is provided with a plurality of inlet collecting holes arranged side by side in the thickness direction, and at least includes a second inlet collecting hole 102 and a first inlet collecting hole 104, the second inlet collecting hole 102 is communicated with the first inlet collecting hole 104 by arranging a throttling channel 106 in the first-shaped fin, an inlet of the throttling channel 106 is arranged on an inner wall of the second inlet collecting hole 102, and an outlet of the throttling channel 106 is arranged on an inner wall of the first inlet collecting hole 104; the inner wall of the first inlet manifold 104 is further provided with a plurality of inlets of the refrigerant flow path 108, so as to construct the plurality of refrigerant flow paths 108 by extending to the other end of the first shaped fin, wherein the plurality of first shaped fins are stacked, so that the plurality of second inlet manifold 102 construct the first inlet manifold channel 20 along the thickness direction, and the plurality of first inlet manifold 104 construct the second inlet manifold channel 20 along the thickness direction.
As shown in fig. 4, the cross-sectional area E of the second inlet collecting channel 20 is greater than or equal to the total inlet area of all the throttling channels 106 on the inner wall of the second inlet collecting channel 20 (i.e. the cross-sectional area F of each throttling channel 106 multiplied by the number of inlets) for the entire heat exchanger.
The utility model discloses the embodiment of the first aspect provides a heat exchanger 1, including two at least entry mass flow channels 20, as shown in fig. 2, the refrigerant gets into the back from the entry mass flow channel 20 of front end, throttle through throttle passageway 106, form the double-phase refrigerant of gas-liquid, the refrigerant gets into the entry mass flow channel 20 of rear end with double-phase form, set up the entry of refrigerant flow path 108 on the inner wall of rear end mass flow channel, so that the double-phase refrigerant of gas-liquid gets into refrigerant flow path 108, and then can promote the refrigerant and get into every refrigerant flow path 108 homogeneity, with guarantee refrigerant distribution effect, can carry out the heat transfer with the outside air in the flow process, in order to accomplish heat transfer operation, the refrigerant of accomplishing heat transfer operation is discharged from export mass flow channel 30.
Further, by defining the relationship between the cross-sectional area of the second inlet collecting channel 20 and the total inlet area of the throttling channels 106 on the inner wall of the second inlet collecting channel 20, that is, the cross-sectional area of the second inlet collecting channel 20 is greater than or equal to the total inlet area of the plurality of throttling channels 106 on the inner wall of the second inlet collecting channel 20, under such a condition, the pressure of the refrigerant in the second inlet collecting channel 20 can be increased, so as to improve the efficiency of gas-liquid mixing and achieve the purpose of improving the probability of refrigerant distribution in the plurality of refrigerant flow paths 108.
Specifically, the throttle passage 106 is a passage of a constant sectional area, and therefore the inlet area of the throttle passage 106 is the sectional area of the throttle passage 106.
As can be understood by those skilled in the art, the throttling channel 106 and the cooling medium flow path 108 are opened between the upper surface and the lower surface of the fin, and the size of the cross section of the throttling channel 106 and the cooling medium flow path 108 is related to the plate thickness of the fin plate.
Further, the cross-sectional area of the second inlet collecting channel 20 is larger than the total inlet area of the plurality of throttle channels 106 on the inner wall of the second inlet collecting channel 20.
In this embodiment, by setting the cross-sectional area of the second inlet collecting channel 20 to be larger than the total inlet area of all the throttle channels 106 on the inner wall of the second inlet collecting channel 20, the effect of gas-liquid mixing can be further enhanced.
In any of the above embodiments, optionally, the other end of the first-shaped fin is provided with an outlet collecting hole 110 along the thickness direction, and a plurality of the first-shaped fins are stacked, so that a plurality of the outlet collecting holes 110 construct an outlet collecting channel 30 along the thickness direction; the inner wall of the outlet manifold 110 is opened with outlets of the plurality of refrigerant channels 108, so that the outlet manifold 110 is communicated with the first inlet manifold 104 through the plurality of refrigerant channels 108.
The heat exchanger comprises a heat exchanger body, an outlet collecting channel, a heat exchanger, wherein the sum of the sectional areas of all refrigerant flow paths in the heat exchanger heat.
As shown in fig. 6, the cross-sectional area G of the outlet collecting channel 30 is greater than or equal to the total outlet area of the plurality of refrigerant flow paths 108 on the inner wall of the outlet collecting channel 30 (i.e. the product of the cross-sectional area H of the refrigerant flow paths 108 and the number of the refrigerant flow paths 108), and the difference between the cross-sectional area of the outlet collecting channel 30 and the total outlet area is smaller than the predetermined area difference.
Wherein, the difference between the cross-sectional area of the outlet collecting flow passage and the total outlet area of the refrigerant flow path 108 is limited by the preset area difference value and is not too large.
In this embodiment, the heat exchanger 1 is prevented from performance deterioration on the refrigerant outlet side by further defining the relationship between the cross-sectional area of the outlet collecting channel 30 and the total outlet area of the refrigerant flow path 108, that is, the cross-sectional area of the outlet collecting channel 30 is slightly larger than the total outlet area of the refrigerant flow path 108, but the difference between the cross-sectional area and the total outlet area is not too large.
Specifically, by defining the relationship between the cross-sectional area of the outlet collecting flow channel and the total outlet area of the refrigerant flow channel 108, the refrigerant can be prevented from flowing into the outlet collecting flow channel 30 from the refrigerant flow channel 108 without causing a pressure shock, thereby ensuring the performance of the heat exchanger 1 on the outlet side.
In any of the above embodiments, optionally, the first inlet manifold 104 includes a first inlet manifold opening on the first shaped fin, and a first tube segment disposed at the first inlet manifold; the second inlet manifold 102 comprises a second inlet manifold opening formed in the first fin, and a second tube segment arranged at the second inlet manifold opening; the outlet manifold 110 includes an outlet manifold opening in the first fin and a third tube segment disposed at the outlet manifold opening.
In this embodiment, a plate body of each fin is provided with a flow collecting port, a structure of a flow collecting hole is constructed in a form of a pipe section integrated on the flow collecting port, and a structure of a flow collecting channel is formed from the fin at the head end to the fin at the tail end in a form of butt joint or splicing of adjacent flow collecting holes, so as to form the heat exchanger 1 in an integrated structure.
In any of the above embodiments, optionally, the first pipe segment includes a first sub pipe segment and a second sub pipe segment disposed on two sides of the first inlet manifold, the second pipe segment includes a third sub pipe segment and a fourth sub pipe segment disposed on two sides of the second inlet manifold, the third pipe segment includes a fifth sub pipe segment and a sixth sub pipe segment disposed on two sides of the outlet manifold, two adjacent first fins are sleeved with each other by the first sub pipe segment of one of the first fins and the second sub pipe segment of the other of the first fins, the third sub pipe segment of one of the first fins and the fourth sub pipe segment of the other of the first fins are sleeved with each other, and the fifth sub pipe segment of one of the first fins and the sixth sub pipe segment of the other of the first fins are assembled with each other.
In this embodiment, as an assembly manner of an integrated structure, the adjacent sub-pipe sections may be assembled by being sleeved with each other, and further, the sub-pipe sections sleeved with each other may be in an interference fit, so as to ensure the assembly strength and prevent the refrigerant from leaking.
In any of the above embodiments, optionally, the first inlet collecting channel, the second inlet collecting channel, and the outlet collecting channel are all disposed along a horizontal direction, one end of the first shaped fin is defined as a high-position end, and the other end is defined as a low-position end, so that a refrigerant flows from the high-position end to the low-position end or from the low-position end to the high-position end in the refrigerant flow path.
In this embodiment, for the heat exchanger 1 defined in the present application, the inlet collecting channel 20 and the outlet collecting channel 30 are horizontally disposed, and can ensure smoothness of refrigerant input and output, and further, the outlet collecting hole 110 and the inlet collecting hole are respectively disposed at different heights, so that the refrigerant flows from a high position to a low position or from a low position to a high position, and thus can be consistent with the direction of gravity or keep a smaller angle, compared with the manner in which the refrigerant flow path 108 in the related art is horizontally disposed, on one hand, when heat exchange is used as an evaporator, the discharging effect of condensed water can be improved, so as to reduce the pressure loss on the air side, and on the other hand, the influence of gravity on refrigerant distribution can be reduced, and further, the uniformity of two-phase refrigerant distribution can be improved.
In any of the above embodiments, optionally, the refrigerant flow path 108 includes a first section flow path 108A communicated with the second inlet manifold 102, a second section flow path 108B communicated with the outlet manifold 110, and a third section flow path 108C disposed between the first section flow path 108A and the second section flow path 108B, where the first section flow path 108A is configured as an arc-shaped flow path, the second section flow path 108B is configured as an arc-shaped flow path, and the third section flow path 108C is configured as a straight-shaped flow path.
In this embodiment, as a way of arranging the refrigerant flow path 108, the first-stage flow path 108A communicated with the first inlet manifold 104 is arranged as an arc-shaped flow path, so that the two-phase refrigerant forming a vortex can relatively uniformly enter different refrigerant flow paths 108 under the action of centrifugal force, and the second-stage flow path 108B communicated with the outlet manifold 110 is also arranged as an arc-shaped flow path, so that the refrigerant after heat exchange can directly enter the outlet manifold 110, so as to be conveniently discharged from the heat exchanger 1.
In any of the above embodiments, optionally,
the third section of flow path is a linear flow path, and an included angle between the linear flow path and the gravity direction is smaller than an angle threshold value.
The range of the angle threshold may be greater than or equal to 0 ° and less than or equal to 10 °.
In this embodiment, the third-stage flow path 108C is defined as a linear flow path extending along the gravity direction, on one hand, the smoothness of the refrigerant flowing in the refrigerant flow path 108 can be improved to ensure the heat exchange effect, and on the other hand, the third-stage flow path 108C is vertically arranged to enable the path length difference of each refrigerant flow path 108 to be relatively small, so as to ensure the uniformity of the refrigerant distribution in terms of the path length.
In any of the above embodiments, optionally, the first shaped fin includes a first monolithic structure and a second monolithic structure, the first monolithic structure and the second monolithic structure are as shown in fig. 7, and assuming that fig. 7 shows the first monolithic structure, a first throttling groove 106A is formed between the second inlet collecting hole 102 and the first inlet collecting hole 104, and a first refrigerant flow channel groove 108D is formed between the first inlet collecting hole 104 and the outlet collecting hole 110; in the second monolithic structure, a second throttling groove 106A is formed between the second inlet collecting hole 102 and the first inlet collecting hole 104, and a second refrigerant flow channel groove 108D is formed between the first inlet collecting hole 104 and the outlet collecting hole 110, wherein the first throttling groove 106A and the second throttling groove 106A are butted to form the throttling channel 106, and the first refrigerant flow channel groove 108D and the second refrigerant flow channel groove 108D are butted to form the refrigerant flow channel 108 by the relative joint assembly of the first monolithic structure and the second monolithic structure.
The first monolithic structure is attached to the second monolithic structure to form the structure shown in fig. 8.
In any of the above embodiments, optionally, the cross section of the throttling channel 106 is circular or polygonal; and/or the cross section of the refrigerant flow path 108 is circular or polygonal.
In any of the above embodiments, optionally, the second inlet manifold 102 is disposed proximate an end of the first shaped fin opposite the first inlet manifold 104.
In this embodiment, the fins are arranged in a long strip shape, and a first inlet collecting hole 104, a throttling channel 106, a second inlet collecting hole 102, a refrigerant flow path 108 and an outlet collecting hole 110 are sequentially arranged from one end (inlet end) to the other end (outlet end) of the fin, and the refrigerant flows into and flows out of the heat exchanger 1 along the above flow direction, which is beneficial to ensuring the heat exchange efficiency.
In any of the above embodiments, optionally, the method further includes: a plurality of second shaped fins (not shown) which are not provided with the throttle passage 106 opposite to the first shaped fins and which are stacked together with the plurality of first shaped fins to construct the heat exchanger 1.
In this embodiment, by providing the second type of fins without the throttling channels 106, on the premise that the cross-sectional area of the first inlet header is greater than or equal to the total inlet area of the plurality of throttling channels 106 on the inner wall of the first inlet header, the number of the fins can be increased, and thus the number of the refrigerant flow paths 108 can be increased.
In any of the above embodiments, optionally, the second shaped fins are alternately stacked with the first shaped fins to construct the heat exchanger 1.
In this embodiment, the first shape fins and the second shape fins are alternately stacked, so that the refrigerant distribution uniformity when the second shape fins are arranged can be improved.
Specifically, it can be calculated according to formula (1)
Q＝K·A0·ΔT (1)
Wherein the overall heat transfer coefficient K is calculated according to formula (2):
calculating the air side heat exchange coefficient h according to the formula (3)0：
ho＝(Ap+η·Af)/Ao×ha(3)
Specifically, Q: amount of heat exchange, hw: refrigerant side heat conductivity, A0: air side heat transfer area, h0: air side heat conductivity, Ap: heat transfer area of the tube, ha: fin portion air side conductivity, Api: refrigerant side heat transfer area, Af: heat conducting area of fin portion, AcoContact area of fins with tubes, η Fin efficiency, hc: conductivity of fin-to-tube contact, Δ T: the temperature difference.
Based on heat transfer volume's computational formula (3), the fin of this heat exchanger, the heat exchange tube (being refrigerant flow path), pressure manifold formula structure as an organic whole, consequently, can reduce thermal contact resistance, correspondingly can effectual promotion fin efficiency η, based on formula (2) can know, the promotion of fin efficiency η is favorable to improving total heat transfer coefficient K, furthermore, based on formula (1), through improving total heat transfer coefficient K, reach the purpose of promoting the heat transfer volume, figure 9 and figure 10 have compared the heat exchanger that this application limited and the fin tubular heat exchanger in the correlation technique respectively, and the heat transfer volume and the air side heat transfer coefficient of microchannel heat exchanger under the same operating mode, show that the heat exchanger of injecing in this application has better heat transfer ability.
FIG. 11 also compares the air side pressure loss for the heat exchanger defined herein with the finned tube heat exchanger of the related art, and the microchannel heat exchanger under the same operating conditions, and shows that the heat exchanger defined herein has superior windage performance compared to the finned tube heat exchanger, while the heat exchanger defined herein has a simpler construction and superior process manufacturability relative to the microchannel heat exchanger.
According to the utility model discloses an air conditioning equipment of embodiment, because of including the heat exchanger of any one of the first aspect embodiment, therefore have all beneficial effects that any one of the above-mentioned embodiments had, no longer describe herein.
The air conditioning equipment can be an integral air conditioner, and the heat exchanger is arranged in the integral air conditioner.
The air conditioning equipment can also be a split air conditioner which comprises an indoor unit and an outdoor unit, and the heat exchanger is arranged in the indoor unit and/or the outdoor unit.
The air conditioning apparatus provided in the present application will be described in detail below by taking a cabinet air conditioner as an example, and comparing with the prior art.
Heat exchangers in the current market mainly comprise fin tube type heat exchangers and micro-channel type heat exchangers, and the fin tube type heat exchangers and the micro-channel type heat exchangers have the following problems: the pipe diameter arranged horizontally is large, so that condensate water is easy to be discharged smoothly, and the air side pressure loss is large; the thermal contact resistance between the tubes and the fins is large, resulting in low fin efficiency; the pipe or the flat tube that the horizontal direction was placed because a large amount to receive the influence of gravity, consequently there is the refrigerant and distributes the difficult problem, and based on above problem, this application has injectd following structure:
(1) under the condition that the relation between the cross sectional area of the second inlet collecting channel and the total inlet area of the throttling channels on the inner wall of the second inlet collecting channel is limited, namely the cross sectional area of the second inlet collecting channel is larger than or equal to the total inlet area of the throttling channels on the inner wall of the second inlet collecting channel, the pressure of the refrigerant in the second inlet collecting channel can be increased, the gas-liquid mixing efficiency is further improved, and the probability of refrigerant distribution in a plurality of refrigerant flow paths is improved.
(2) The refrigerant enters from the inlet collecting pipe at the front end and then is throttled through the throttling channel to form a gas-liquid two-phase refrigerant, the refrigerant enters the inlet collecting pipe at the rear end in a two-phase mode, and the inner wall of the collecting pipe at the rear end is provided with an inlet of a refrigerant flow path, so that the gas-liquid two-phase refrigerant enters the refrigerant flow path, the uniformity of the refrigerant entering each refrigerant flow path can be improved, and the refrigerant distribution effect is ensured.
(3) The refrigerant flow path is directly arranged in the fin, and compared with the fin tube type heat exchanger in the related technology, the fin tube type heat exchanger does not need to be assembled in a contact mode through tubes and fins, and therefore heat exchange efficiency of the fins can be obviously improved.
(4) The outlet of the throttling channel, namely the outlet direction arranged on the inner wall of the first inlet collecting hole and the tangential direction of the outlet position form a smaller angle, so that the refrigerant can rotate at a high speed along the inner wall of the first inlet collecting hole after entering the first inlet collecting hole, and a vortex is formed, even if the high-density liquid refrigerant circles round along the inner wall of the first inlet collecting hole, the middle area of the first inlet collecting hole is in gas backflow, and further the uniform distribution of the liquid refrigerant can be further improved, the phenomenon that only gaseous refrigerant flows into part of refrigerant flow paths is prevented, and the problem that the refrigerant distribution is uneven in the microchannel heat exchanger in the prior art is solved.
(5) The fin structure is vertically placed to can be unanimous with the direction of gravity or keep less angle, compare with the mode that refrigerant flow path level among the correlation technique laid, on the one hand, when using the heat transfer as the evaporimeter, can promote the drainage effect of comdenstion water, with the loss of pressure who reduces the air side, on the other hand, can reduce the influence of the gravity that receives when the refrigerant distributes, and then promote the homogeneity of two-phase refrigerant distribution.
In the present application, the terms "first", "second", "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; the term "plurality" means two or more unless expressly limited otherwise. The terms "mounted," "connected," "fixed," and the like are to be construed broadly, and for example, "connected" may be a fixed connection, a removable connection, or an integral connection; "coupled" may be direct or indirect through an intermediary. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.
In the description of the present invention, it should be understood that the terms "upper", "lower", "left", "right", "front", "back", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the device or unit indicated must have a specific direction, be constructed and operated in a specific orientation, and therefore, should not be construed as limiting the present invention.
In the description of the present specification, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (15)
1. A heat exchanger, comprising: a plurality of first-shaped fins which are arranged in a stacked manner,
one end of the first-shaped fin is provided with a plurality of inlet flow collecting holes which are arranged side by side along the thickness direction, and at least comprises a first inlet flow collecting hole and a second inlet flow collecting hole, the first inlet flow collecting hole and the second inlet flow collecting hole are communicated through a throttling channel arranged in the first-shaped fin, the inner wall of the second inlet flow collecting hole is provided with an inlet of the throttling channel, and the inner wall of the first inlet flow collecting hole is provided with an outlet of the throttling channel;
the inner wall of the first inlet collecting hole is also provided with a plurality of inlets of the refrigerant flow paths so as to construct the plurality of refrigerant flow paths by extending towards the other end of the first-shaped fin,
and a plurality of first shape fins are overlapped, so that a plurality of second inlet collecting holes construct a second inlet collecting channel along the thickness direction, a plurality of first inlet collecting holes construct a first inlet collecting channel along the thickness direction, and the cross section area of the second inlet collecting channel is larger than or equal to the total inlet area of all throttling channels in the second inlet collecting channel.
2. The heat exchanger of claim 1,
outlet current collecting holes are formed in the other ends of the first-shaped fins along the thickness direction, and a plurality of outlet current collecting holes are overlapped to form an outlet current collecting channel along the thickness direction;
the inner wall of the outlet collecting hole is provided with outlets of the plurality of refrigerant flow paths so as to enable the outlet collecting hole to be communicated with the first inlet collecting hole through the plurality of refrigerant flow paths,
the heat exchanger comprises a heat exchanger body, an outlet collecting channel, a heat exchanger, wherein the sum of the sectional areas of all refrigerant flow paths in the heat exchanger heat.
3. The heat exchanger of claim 2,
the first inlet collecting hole comprises a first inlet collecting port formed in the first fin and a first pipe section arranged at the first inlet collecting port;
the second inlet collecting hole comprises a second inlet collecting port formed in the first fin and a second pipe section arranged at the second inlet collecting port;
the outlet collecting hole comprises an outlet collecting port formed in the first fin and a third pipe section arranged at the outlet collecting port.
4. The heat exchanger of claim 3,
the first pipe section comprises a first sub pipe section and a second sub pipe section which are arranged on two sides of the first inlet collecting port, the second pipe section comprises a third sub pipe section and a fourth sub pipe section which are arranged on two sides of the second inlet collecting port, the third pipe section comprises a fifth sub pipe section and a sixth sub pipe section which are arranged on two sides of the outlet collecting port, the first shape fins are adjacent to each other, the first shape fins are sleeved with the second sub pipe sections through one of the first shape fins, the third shape fins are sleeved with the fourth shape fins through the other shape fins, the fifth shape fins are sleeved with the sixth shape fins through one of the fifth shape fins, and the sixth shape fins are arranged on the fifth shape fins and the other shape fins to form the heat exchanger.
5. The heat exchanger of claim 2,
the first inlet collecting channel, the second inlet collecting channel and the outlet collecting channel are all arranged along the horizontal direction, one end of the first-shaped fin is limited to be a high-position end, and the other end of the first-shaped fin is limited to be a low-position end, so that a refrigerant flows from the high-position end to the low-position end or from the low-position end to the high-position end in the refrigerant flow path.
6. The heat exchanger according to any one of claims 2 to 5,
the refrigerant flow path comprises a first section of flow path communicated with the second inlet collecting hole, a second section of flow path communicated with the outlet collecting hole, and a third section of flow path arranged between the first section of flow path and the second section of flow path,
wherein the first stage flow path is configured as an arcuate flow path, the second stage flow path is configured as an arcuate flow path, and the third stage flow path is configured as a linear flow path.
7. The heat exchanger of claim 6,
the third section of flow path is a linear flow path, and an included angle between the linear flow path and the gravity direction is smaller than an angle threshold value.
8. The heat exchanger according to any one of claims 1 to 5,
the cross section of the throttling channel is circular or polygonal; and/or
The cross section of the refrigerant flow path is circular or polygonal.
9. The heat exchanger according to any one of claims 1 to 5,
the second inlet manifold is disposed adjacent an end of the first shaped fin opposite the first inlet manifold.
10. The heat exchanger of any one of claims 1 to 5, further comprising:
a plurality of second shaped fins provided with no throttle passage with respect to the first shaped fins,
the plurality of second shaped fins is stacked with the plurality of first shaped fins to construct the heat exchanger.
11. The heat exchanger of claim 10,
and the second shaped fins and the first shaped fins are alternately superposed to construct the heat exchanger.
12. The heat exchanger according to any one of claims 1 to 5,
the outer surface of the heat exchanger is coated with a hydrophilic coating or a super-hydrophobic pattern layer.
13. An air conditioning apparatus, characterized by comprising:
a heat exchanger as claimed in any one of claims 1 to 12.
14. Air conditioning apparatus according to claim 13,
the air conditioning equipment is an integral air conditioner, and the heat exchanger is arranged in the integral air conditioner.
15. Air conditioning apparatus according to claim 13,
the air conditioning equipment is a split air conditioner, the split air conditioner comprises an indoor unit and an outdoor unit, and the heat exchanger is arranged in the indoor unit and/or the outdoor unit.
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|---|---|---|---|
| CN201920870673.0U CN210165621U (en) | 2019-06-11 | 2019-06-11 | Heat exchanger and air conditioning equipment |
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| CN201920870673.0U CN210165621U (en) | 2019-06-11 | 2019-06-11 | Heat exchanger and air conditioning equipment |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114076544A (en) * | 2020-08-21 | 2022-02-22 | 广东美的制冷设备有限公司 | Heat exchanger and air conditioner |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114076544A (en) * | 2020-08-21 | 2022-02-22 | 广东美的制冷设备有限公司 | Heat exchanger and air conditioner |
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