CN210165622U - Heat exchanger and air conditioning equipment - Google Patents
Heat exchanger and air conditioning equipment Download PDFInfo
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- CN210165622U CN210165622U CN201920871575.9U CN201920871575U CN210165622U CN 210165622 U CN210165622 U CN 210165622U CN 201920871575 U CN201920871575 U CN 201920871575U CN 210165622 U CN210165622 U CN 210165622U
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Abstract
The utility model provides an air conditioning equipment and heat exchanger thereof, the heat exchanger includes: the fin plates are arranged in a stacked mode and comprise a first fin plate and a second fin plate, outlet collecting holes are correspondingly formed in the first fin plate and the second fin plate, a plurality of inlet collecting holes are formed in the first fin plate, the inlet collecting holes comprise a first inlet collecting hole and a second inlet collecting hole, the first inlet collecting hole is communicated with the second inlet collecting hole through a first throttling channel formed in the fin plates, and the first inlet collecting hole is communicated with the outlet collecting hole through a refrigerant flow path formed in the first fin plate; the second fin is provided with a first inlet collecting hole and a second inlet collecting hole, and the first inlet collecting hole is communicated with the outlet collecting hole through a refrigerant flow path arranged in the second fin. The technical scheme provided by the utility model, when reaching and the refrigerant flow between the adaptation, be favorable to reducing the preparation cost of heat exchanger.
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 arrangement mode, the circular tube or flat tube portion adopts the mode of arranging along the horizontal direction, and the fin portion adopts the vertical direction setting, for the equipment, combine through the expand tube between the pipe of fin tube heat exchanger and the fin, the microchannel heat exchanger combines through the welding, the heat exchanger of above-mentioned structure still has following defect:
heat exchangers of different sizes need to be equipped for different refrigeration needs, resulting in increased manufacturing costs.
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 fin plates are arranged in a stacked mode and comprise a first fin plate and a second fin plate, outlet flow collecting holes are correspondingly formed in the first fin plate and the second fin plate, outlet flow collecting channels are correspondingly formed in the outlet flow collecting holes, a plurality of inlet flow collecting holes are formed in the first fin plate and comprise a first inlet flow collecting hole and a second inlet flow collecting hole, the first inlet flow collecting hole is communicated with the second inlet flow collecting hole through a first throttling channel formed in the fin plates, and the first inlet flow collecting hole is communicated with the outlet flow collecting holes through a refrigerant flow path formed in the first fin plate; the second fin is correspondingly provided with the first inlet collecting hole and the second inlet collecting hole, and the first inlet collecting hole is communicated with the outlet collecting hole through a refrigerant flow path arranged in the second fin; the first fins and the second fins are overlapped, so that the first inlet collecting holes correspond to form a first inlet collecting channel, the second inlet collecting holes correspond to form a second inlet collecting channel, and after a refrigerant flows into the second inlet collecting channel, the refrigerant flows into the first inlet collecting channel through the first throttling channel on the first fins and flows into the outlet collecting channel through the refrigerant flow path.
The utility model discloses the heat exchanger that technical scheme of first aspect provided, pile up the formation by at least two kinds of fins, at least two kinds of fins include first fin and second fin, first entry current collecting hole and second entry current collecting hole on the first fin, and through first throttle passageway intercommunication between first entry current collecting hole and the second entry current collecting hole, and be provided with second entry current collecting hole on the second fin at least, consequently pile up the back at first fin and second fin, the export current collecting channel that corresponds regional export current collecting hole and can construct and form the intercommunication, the second entry current collecting channel that the second entry current collecting hole that corresponds can form the intercommunication, with the refrigerant inlet channel who regards as the heat exchanger injectd in this application.
The second fin is constructed into a fin structure with two inlet collecting holes which are not communicated with each other, after the fins are stacked, the first inlet collecting holes in the second fin can be combined with the inlet collecting holes in the first fin to form communicated first inlet collecting holes, so that two-phase refrigerants throttled by the first throttling channel are uniformly mixed in the first throttling channel and then enter a refrigerant flow path, and further the refrigerant distribution uniformity is favorably improved.
Specifically, the refrigerant entering the second inlet collecting channel is throttled through the first 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, the inner wall of the rear end collecting pipe 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, the refrigerant distribution effect is guaranteed, heat exchange can be performed with external air in the flowing process, heat exchange operation is completed, and the refrigerant after heat exchange operation is discharged from the outlet collecting pipe.
The arrangement proportion between the first fin and the second fin can be adjusted according to the refrigerant flow by arranging the first fin with the throttling channel and the second fin without the throttling channel, for example, for a heat exchanger needing higher heat exchange capacity, the required refrigerant flow is smaller, the arrangement proportion between the first fin and the second fin can be set to be a smaller value, and then the air conditioner with the same overall dimension and the same fin number can be met, the preparation requirement of the air conditioner shell with different refrigerating capacity can be set by adjusting the arrangement proportion between the first fin and the second fin, and the universality of the use of the fin structure limited in the application can be improved, the heat exchanger is adaptive to the flow of the refrigerant, and the preparation cost of the heat exchanger is reduced.
In the present application, the inlet manifold directly connected to the refrigerant flow path is referred to as a first inlet manifold, and the inlet manifold provided near the end portion is referred to as a second inlet manifold.
Additionally, the utility model provides an among the above-mentioned technical scheme heat exchanger can also have following additional technical characteristics:
in the above technical solution, optionally, on the first fin, an inlet of the first throttling channel is formed on an inner wall of the second inlet collecting hole, and an outlet of the first throttling channel is formed on an inner wall of the first inlet collecting hole; the cross-sectional area of the second inlet collecting channel is larger than or equal to the total inlet area of all the first throttling channels in the second inlet collecting channel.
And the cross-sectional area of the second inlet collecting channel is the same as that of the second inlet collecting hole.
In the technical scheme, 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, 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, under the condition, 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.
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, the first fins and the second fins are alternately stacked.
In the technical scheme, the first fins and the second fins are alternately overlapped, so that the flowing uniformity of the refrigerant flow paths from the first inlet collecting channel to the different fins can be improved, and the balance of the heat exchange capacity of the whole heat exchanger is further improved.
The first fins and the second fins are alternately stacked, and the first fins and the second fins may be alternately stacked, or a plurality of first fins may be used as a unit, the first fins and the second fins of one unit are alternately stacked, or a plurality of second fins may be used as a unit, and the first fins and the second fins of one unit are alternately stacked.
In any of the above technical solutions, optionally, the inner wall of the first inlet manifold is further provided with inlets of a plurality of refrigerant flow paths; the inner wall of the outlet collecting hole is provided with outlets of the multiple refrigerant flow paths, wherein 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.
The cross-sectional area of the outlet collecting channel is the same as that of the outlet collecting hole.
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, and at least comprises the following two setting modes: 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 the sum of the sectional areas of all the heat exchange tubes of the whole heat exchanger does not exceed the proportion.
The difference between the cross section area of the outlet collecting and flowing channel and the total outlet area of the refrigerant flow path is constructed 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 constructed, 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 constructing the relationship 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 flowing into the outlet collecting flow channel from the refrigerant flow channel without causing pressure shock, and the performance of the heat exchanger on the outlet side is further ensured.
In any of the above technical solutions, optionally, an included angle between a flow direction of the outlet of the first throttling passage and a tangential direction in which the outlet is located is smaller than or equal to a first angle threshold.
In the technical scheme, a throttling channel is arranged between adjacent inlet collecting pipes to be used as a throttling component, a two-phase state is formed when a refrigerant enters a second inlet collecting hole after passing through the throttling channel from a first inlet collecting hole, the outlet of the throttling channel, i.e. the outlet direction provided in the inner wall of the first inlet manifold has a small angle to the tangential direction of the outlet position, so that the refrigerant can rotate at high speed along the inner wall of the first inlet manifold hole after entering the first inlet manifold hole and form a vortex, even if the liquid refrigerant with high density whirls along the inner wall of the first inlet manifold, the middle area of the first inlet manifold is gas backflow, and then can further promote the even distribution of liquid refrigerant, prevented that some refrigerant flow paths only have gaseous refrigerant inflow's phenomenon to produce to solve the refrigerant uneven distribution problem that microchannel heat exchanger exists among the prior art.
In any of the above solutions, optionally, the first angle threshold is greater than or equal to 0 ° and less than or equal to 30 °.
In any of the above technical solutions, optionally, the plurality of fins are vertically arranged, so that an included angle between the refrigerant flow path and the gravity direction is smaller than a second angle threshold, and the first inlet collecting channel, the second inlet collecting channel, and the outlet collecting channel are all horizontally arranged.
In the technical scheme, a second angle threshold is used for describing a maximum included angle which can be generated between the refrigerant flow path and the vertical direction (or the gravity direction), and the smaller the second angle threshold is, the closer the direction of the refrigerant flow path is to the gravity direction is, so that the drainage of condensed water is facilitated.
In any of the above technical solutions, optionally, on the first fin, the outlet manifold holes include a first outlet manifold hole and a second outlet manifold hole, and a second throttling channel is further disposed between the first outlet manifold hole and the second outlet manifold hole to configure the first fin into a symmetrical structure; on the second fin, the outlet manifolds include a first outlet manifold and a second outlet manifold to configure the second fin in a symmetrical configuration.
In the technical scheme, the outlet current collecting holes can be arranged to be in a structure symmetrical to the two inlet current collecting holes, the throttling channels are also arranged between the two outlet current collecting holes on the first fin, the throttling channels are not arranged between the two outlet current collecting holes on the second fin, and the heat exchanger formed by overlapping the fins of the structure is adopted.
In any of the above solutions, optionally, the outer surface of the heat exchanger is coated with a hydrophilic coating or a super-hydrophobic coating.
In the technical scheme, the hydrophilic coating or the super-hydrophobic coating is coated on the outer surface of the heat exchanger, so that the water dipping amount of the outer surface of the heat exchanger is reduced, and the condensed water discharge efficiency 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 longitudinal sectional view of a heat exchanger according to the invention;
FIG. 2 shows a schematic view of a portion of the structure at A in FIG. 1;
fig. 3 shows a schematic structural view of a fin according to an embodiment of the invention;
fig. 4 shows a partial structural schematic of a fin according to an embodiment of the invention;
fig. 5 shows a partial structural schematic view of a fin according to another embodiment of the present invention;
fig. 6 shows a schematic structural view of a fin according to another embodiment of the present invention;
FIG. 7 is a first schematic graph comparing a heat exchanger of the present invention with a heat exchanger of the related art;
fig. 8 is a second graph schematically comparing a heat exchanger according to the present invention with a heat exchanger according to the related art;
fig. 9 is a third schematic diagram of a heat exchanger according to the present invention and a heat exchanger according to the related art.
Wherein, the correspondence between the reference numbers and the part names in fig. 1 to 6 is:
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 6.
As shown in fig. 1, the heat exchanger for air conditioning equipment of the embodiment of the present invention includes: the fin structure comprises a plurality of superposed fins, wherein the superposed fins comprise a first fin 10A and a second fin 10B.
The first fin 10A has at least the following three structural forms:
(1) one end of the first fin 10A is provided with a first inlet collecting hole 104 and a second inlet collecting hole 106, the first inlet collecting hole 104 is communicated with the second inlet collecting hole 106 through a first throttling channel 108 formed in the fin, and the other end of the second fin 10B is provided with a single outlet collecting hole 102;
(2) one end of the first fin 10A is provided with a first inlet collecting hole 104 and a second inlet collecting hole 106, the first inlet collecting hole 104 is communicated with the second inlet collecting hole 106 through a first throttling channel 108 formed in the fin, the other end of the second fin 10B is provided with two outlet collecting holes 102, and a throttling channel is not arranged between the two outlet collecting holes 102;
(3) one end of the first fin 10A is provided with a first inlet collecting hole 104 and a second inlet collecting hole 106, the first inlet collecting hole 104 is communicated with the second inlet collecting hole 106 through a first throttling channel 108 arranged in the fin, the other end of the second fin 10B is provided with two outlet collecting holes 102, and a throttling channel is arranged between the two outlet collecting holes 102, so that the first fin 10A forms a symmetrical structure.
The second fin 10B has at least the following three structural forms:
(1) one end of the second fin 10A is provided with a first inlet manifold 104 and a second inlet manifold 106 which are independent from each other, and the other end of the second fin 10B is provided with a single outlet manifold 102;
(2) one end of the second fin 10A is provided with a first inlet collecting hole 104 and a second inlet collecting hole 106 which are independent of each other, the other end of the second fin 10B is provided with two outlet collecting holes 102, and a throttling channel is not arranged between the two outlet collecting holes 102, so that the second fin 10B forms a symmetrical structure;
(3) one end of the second fin 10A is provided with a first inlet manifold 104 and a second inlet manifold 106 which are independent of each other, the other end of the second fin 10B is provided with two outlet manifolds 102, and a throttling channel is arranged between the two outlet manifolds 102.
Example one
Specifically, outlet collecting holes 102 are correspondingly formed in the first fin 10A and the second fin 10B, as shown in fig. 4, a plurality of inlet collecting holes are formed in the first fin 10A, each inlet collecting hole includes a first inlet collecting hole 104 and a second inlet collecting hole 106, the first inlet collecting hole 104 is communicated with the second inlet collecting hole 106 through a first throttling channel 108 formed in the fin, and the first inlet collecting hole 104 is communicated with the outlet collecting hole 102 through a refrigerant flow path 110 formed in the first fin 10A; as shown in fig. 5, the second fin 10B is provided with the first inlet manifold 104 and the second inlet manifold 106, and the first inlet manifold 104 and the outlet manifold 102 are communicated with each other through a refrigerant passage 110 formed in the second fin 10B; the first fins 10A and the second fins 10B are stacked, so that the first inlet collecting holes 104 form a first inlet collecting channel 20 correspondingly, the second inlet collecting holes form a second inlet collecting channel 30 correspondingly, and after flowing into the second inlet collecting channel 30, a refrigerant flows into the first inlet collecting channel 20 through the first throttling channel 108 on the first fin 10A, and then flows into the outlet collecting channel 40 through the refrigerant flow path 110.
As shown in fig. 6, each of the first and second fins is configured such that a first inlet manifold hole 104, a second inlet manifold hole 106, a throttle channel, and a refrigerant flow path 110 are formed on a plate body 112, wherein the throttle channel and the refrigerant flow path are formed by a structure protruding from a surface of the plate body 112.
The embodiment of the utility model provides a heat exchanger, pile up the formation by at least two kinds of fins, at least two kinds of fins include first fin 10A and second fin 10B, first entry collecting port 104 and second entry collecting port 106 on first fin 10A, and through first throttle passageway 108 intercommunication between first entry collecting port 104 and the second entry collecting port 106, and be provided with second entry collecting port 106 on the second fin 10B at least, consequently pile up the back at first fin 10A and second fin 10B, the export collecting port 102 that corresponds the region can construct the export collecting channel 40 that forms the intercommunication, the second entry collecting port 106 that corresponds can form the second entry collecting channel 30 of intercommunication, with the refrigerant inlet channel who is the heat exchanger prescribed a limit to in this application.
By configuring the second fin 10B into a fin structure having two inlet collecting holes that are not communicated with each other, after the fins are stacked, the first inlet collecting hole 104 on the second fin 10B can be combined with the inlet collecting hole on the first fin 10A to form a communicated first inlet collecting hole 104, so that two-phase refrigerant throttled by the first throttling channel 108 uniformly mixes in the first throttling channel 108 and then enters the refrigerant flow path 110, thereby facilitating the improvement of the refrigerant distribution uniformity.
Specifically, the refrigerant entering the second inlet collecting channel 30 is throttled through the first throttling channel 108 to form a gas-liquid two-phase refrigerant, the refrigerant enters the inlet collecting pipe at the rear end in a two-phase manner, an inlet of the refrigerant flow path 110 is formed in the inner wall of the rear end collecting pipe, so that the gas-liquid two-phase refrigerant enters the refrigerant flow path 110, the uniformity of the refrigerant entering each refrigerant flow path 110 can be improved, the refrigerant distribution effect is ensured, heat exchange with outside air can be performed in the flowing process, the heat exchange operation is completed, and the refrigerant after the heat exchange operation is discharged from the outlet collecting pipe.
By arranging the first fin 10A with the throttling channel and the second fin 10B without the throttling channel, the setting proportion between the first fin 10A and the second fin 10B can be adjusted according to the refrigerant flow, for example, for a heat exchanger needing higher heat exchange capacity, a larger refrigerant flow is needed at the same time, under the condition, the setting proportion between the first fin 10A and the second fin 10B can be set to be a larger value, for a heat exchanger needing lower heat exchange requirement, the required refrigerant flow is also smaller, at the moment, the setting proportion between the first fin 10A and the second fin 10B can be set to be a smaller value, and further, the air conditioners with the same appearance size and the same number of fins can be met, the preparation requirements in the air conditioner shells with different refrigerating capacities can be set by adjusting the setting proportion between the first fin 10A and the second fin 10B, thereby can promote the commonality that the fin structure who restricts in this application used, when reaching and refrigerant flow between, be favorable to reducing the preparation cost of heat exchanger.
In the present application, the inlet manifold directly connected to the refrigerant flow path 110 is referred to as a first inlet manifold 104, and the inlet manifold provided near the end is referred to as a second inlet manifold 106.
In any of the above embodiments, optionally, the first fins 10A and the second fins 10B are alternately stacked.
In this embodiment, the first fins 10A and the second fins 10B are alternately stacked, so that the uniformity of the flow of the refrigerant from the first inlet collecting channel 20 to the refrigerant flow paths 110 on different fins can be improved, and the balance of the heat exchange capacity of the whole heat exchanger can be improved.
As can be understood by those skilled in the art, the first fins 10A and the second fins 10B are alternately stacked, and may be single first fins 10A and single second fins 10B, or multiple first fins 10A may be taken as a unit, and a unit of first fins 10A and a unit of second fins 10B are alternately stacked, or multiple second fins 10B may be taken as a unit, and a unit of first fins 10A and a unit of second fins 10B are alternately stacked, as shown in fig. 2.
In any of the above embodiments, optionally, on the first fin 10A, the outlet manifold 102 includes a first outlet manifold 102 and a second outlet manifold 102, and a second throttling channel is further opened between the first outlet manifold 102 and the second outlet manifold 102, so as to configure the first fin 10A into a symmetrical structure; on said second fin 10B, said outlet manifolds 102 comprise a first outlet manifold 102 and a second outlet manifold 102, so as to configure said second fin 10B in a symmetrical configuration.
In this embodiment, outlet collecting holes 102 may also be set to be a structure symmetrical to two inlet collecting holes, a throttling channel is also provided between two outlet collecting holes 102 on the first fin 10A, and a throttling channel is not provided between two outlet collecting holes 102 on the second fin 10B.
Example two
The relationship between the cross-sectional area of the second inlet collecting channels 30 and the total inlet area of the first throttling channels 108 is further defined below.
On the first fin 10A, an inlet of the first throttling channel 108 is formed on an inner wall of the second inlet manifold 106, and an outlet of the first throttling channel 108 is formed on an inner wall of the first inlet manifold 104; the cross-sectional area of the second inlet collecting channel 30 is greater than or equal to the total inlet area of all of the first throttling channels 108 in the second inlet collecting channel 30.
In this embodiment, by defining the relationship between the cross-sectional area of the second inlet collecting channel 30 and the total inlet area of the throttling channels on the inner wall of the second inlet collecting channel 30, that is, the cross-sectional area of the second inlet collecting channel 30 is greater than or equal to the total inlet area of the plurality of throttling channels on the inner wall of the second inlet collecting channel 30, under such a condition, the pressure of the refrigerant in the second inlet collecting channel 30 can be increased, so as to improve the efficiency of gas-liquid mixing and achieve the effect of improving the probability of refrigerant distribution in the plurality of refrigerant flow paths 110.
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 cooling medium flow path 110 are opened between the upper surface and the lower surface of the fin, and the size of the cross section of the throttling channel and the cooling medium flow path 110 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 30 is larger than the total inlet area of the plurality of throttle channels on the inner wall of the second inlet collecting channel 30.
In this embodiment, by setting the cross-sectional area of the second inlet collecting channel 30 to be larger than the total inlet area of all the throttle channels on the inner wall of the second inlet collecting channel 30, the effect of gas-liquid mixing can be further enhanced.
EXAMPLE III
The relationship between the cross-sectional area of the outlet collecting channel 40 and the total area of the cross-sectional area of the refrigerant flow path 110 is further defined below.
In any of the above embodiments, optionally, the inner wall of the first inlet manifold 104 is further provided with inlets of a plurality of refrigerant flow paths 110; the inner wall of the outlet collecting hole 102 is provided with outlets of the plurality of refrigerant flow paths 110, wherein the sum of the cross sections of all the refrigerant flow paths 110 in the heat exchanger is determined as a first area, the cross section of the outlet collecting channel 40 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.
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, and at least comprises the following two setting modes: 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 the sum of the sectional areas of all the heat exchange tubes of the whole heat exchanger does not exceed the proportion.
The difference between the cross-sectional area of the outlet collecting and flowing channel and the total outlet area of the refrigerant flow path 110 is configured by the preset area difference value and is not too large.
In this embodiment, the heat exchanger is prevented from performance deterioration on the refrigerant outlet side by further configuring the relationship between the cross-sectional area of the outlet collecting channel 40 and the total outlet area of the refrigerant flow path 110, that is, the cross-sectional area of the outlet collecting channel 40 is slightly larger than the total outlet area of the refrigerant flow path 110, but the difference between the cross-sectional area and the total outlet area is not excessively large.
Specifically, by configuring the relationship between the cross-sectional area of the outlet collecting flow channel and the total outlet area of the refrigerant flow channel 110, the refrigerant flowing from the refrigerant flow channel 110 into the outlet collecting flow channel 40 can be prevented from causing a sudden pressure change, thereby ensuring the performance of the heat exchanger on the outlet side.
Example four
The inflow direction of the refrigerant into the first inlet collecting channel 20 is further defined as follows.
In any of the above embodiments, as shown in fig. 6, optionally, an angle α between the flow direction of the outlet of the first throttling channel 108 and the tangential direction at which the outlet is located is less than or equal to the first angle threshold.
In this embodiment, a throttling channel is provided between adjacent inlet collecting pipes as a throttling component, and when the refrigerant passes through the throttling channel from the first inlet collecting hole 104 to the second inlet collecting hole 106, a two-phase state is formed, and the outlet of the throttling channel, i.e. the outlet direction provided into the inner wall of the first inlet manifold 104 has a small angle to the tangential direction of the outlet position, so that the refrigerant can rotate at a high speed along the inner wall of the first inlet manifold 104 after entering the first inlet manifold 104, and form a vortex, even if the liquid refrigerant with high density swirls along the inner wall of the first inlet manifold 104, the middle region of the first inlet manifold 104 is gas backflow, further, the uniform distribution of the liquid refrigerant can be further improved, and the phenomenon that only the gaseous refrigerant flows into a part of the refrigerant flow path 110 is prevented, so that the problem of uneven refrigerant distribution of the microchannel heat exchanger in the prior art is solved.
In any of the above embodiments, optionally, the first angle threshold is greater than or equal to 0 ° and less than or equal to 30 °.
EXAMPLE five
The arrangement of the fins is further defined below.
In any of the above embodiments, optionally, the plurality of fins are vertically arranged, so that an included angle between the refrigerant flow path 110 and the gravity direction is smaller than a second angle threshold, and the first inlet collecting channel 20, the second inlet collecting channel 30, and the outlet collecting channel 40 are all horizontally arranged.
In this embodiment, a second angle threshold is used to describe a maximum included angle that can be generated between the refrigerant flow path 110 and the vertical direction (or the gravity direction), and a smaller second angle threshold indicates that the direction of the refrigerant flow path 110 is closer to the gravity direction, thereby being more beneficial to discharging condensed water.
In any of the above embodiments, optionally, the outer surface of the heat exchanger is coated with a hydrophilic coating or a superhydrophobic coating.
In the embodiment, the hydrophilic coating or the super-hydrophobic coating is coated on the outer surface of the heat exchanger, so that the water dipping amount of the outer surface of the heat exchanger is reduced, and the condensed water discharging efficiency is improved.
The advantageous effects of the heat exchanger defined in the present application will be described further below with reference to fig. 7 to 9.
Specifically, the heat exchanger is calculated according to equation (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)o：
ho＝(Ap+η·Af)/Ao×ha(3)
Specifically, Q: amount of heat exchange, hw: refrigerant side heat conductivity, Ao: air side heat transfer area, ho: 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) can know, this heat exchanger's fin, heat exchange tube (refrigerant flow path promptly), 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, fin efficiency η's promotion 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 7 and figure 8 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. 9 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.
To sum up, the heat exchanger and the air conditioning equipment provided by the present invention can adjust the setting ratio between the first fin and the second fin according to the refrigerant flow by arranging the first fin having the throttling channel and the second fin not having the throttling channel, for example, for the heat exchanger requiring higher heat exchange capacity, a larger refrigerant flow is required, in this case, the setting ratio between the first fin and the second fin can be set to a larger value, for the heat exchanger requiring lower heat exchange, the required refrigerant flow is also smaller, at this time, the setting ratio between the first fin and the second fin can be set to a smaller value, and further, the air conditioner having the same external dimension and the same number of fins can be satisfied, the preparation requirements in the air conditioner housing having different refrigeration capacities can be set by adjusting the setting ratio between the first fin and the second fin, thereby can promote the commonality that the fin structure who restricts in this application used, when reaching and refrigerant flow between, be favorable to reducing the preparation cost of heat exchanger.
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 (12)
1. A heat exchanger, comprising: a plurality of fins which are arranged in a stacked manner, wherein the plurality of fins which are arranged in a stacked manner comprise a first fin and a second fin, outlet collecting holes are correspondingly arranged on the first fin and the second fin, a plurality of outlet collecting holes correspondingly construct outlet collecting channels,
the first fin is provided with a plurality of inlet collecting holes, the inlet collecting holes comprise a first inlet collecting hole and a second inlet collecting hole, the first inlet collecting hole is communicated with the second inlet collecting hole through a first throttling channel arranged in the fin, and the first inlet collecting hole is communicated with the outlet collecting hole through a refrigerant flow path arranged in the first fin;
the second fin is correspondingly provided with the first inlet collecting hole and the second inlet collecting hole, and the first inlet collecting hole is communicated with the outlet collecting hole through a refrigerant flow path arranged in the second fin;
the first fins and the second fins are overlapped, so that the first inlet collecting holes correspond to form a first inlet collecting channel, the second inlet collecting holes correspond to form a second inlet collecting channel, and after a refrigerant flows into the second inlet collecting channel, the refrigerant flows into the first inlet collecting channel through the first throttling channel on the first fins and flows into the outlet collecting channel through the refrigerant flow path.
2. The heat exchanger of claim 1,
on the first fin, the inner wall of the second inlet collecting hole is provided with an inlet of the first throttling channel, and the inner wall of the first inlet collecting hole is provided with an outlet of the first throttling channel;
the cross-sectional area of the second inlet collecting channel is larger than or equal to the total inlet area of all the first throttling channels in the second inlet collecting channel.
3. The heat exchanger of claim 2,
the first fins and the second fins are alternately stacked.
4. The heat exchanger of claim 2,
the inner wall of the first inlet collecting hole is also provided with a plurality of inlets of refrigerant flow paths;
the inner wall of the outlet collecting hole is provided with outlets of 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.
5. The heat exchanger of claim 2,
an included angle between the flow direction of the outlet of the first throttling channel and the tangential direction of the outlet is smaller than or equal to a first angle threshold value.
6. The heat exchanger of claim 5,
the first angle threshold is greater than or equal to 0 ° and less than or equal to 30 °.
7. The heat exchanger of claim 5,
the fins are vertically arranged, so that an included angle between the refrigerant flow path and the gravity direction is smaller than a second angle threshold, and the first inlet collecting channel, the second inlet collecting channel and the outlet collecting channel are horizontally arranged.
8. The heat exchanger according to any one of claims 1 to 7,
on the first fin, the outlet collecting holes comprise a first outlet collecting hole and a second outlet collecting hole, and a second throttling channel is further formed between the first outlet collecting hole and the second outlet collecting hole so as to construct the first fin into a symmetrical structure;
on the second fin, the outlet manifolds include a first outlet manifold and a second outlet manifold to configure the second fin in a symmetrical configuration.
9. The heat exchanger according to any one of claims 1 to 7,
the outer surface of the heat exchanger is coated with a hydrophilic coating or a super-hydrophobic coating.
10. An air conditioning apparatus, characterized by comprising:
a heat exchanger as claimed in any one of claims 1 to 9.
11. Air conditioning apparatus according to claim 10,
the air conditioning equipment is an integral air conditioner, and the heat exchanger is arranged in the integral air conditioner.
12. Air conditioning apparatus according to claim 10,
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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920871575.9U CN210165622U (en) | 2019-06-11 | 2019-06-11 | Heat exchanger and air conditioning equipment |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920871575.9U CN210165622U (en) | 2019-06-11 | 2019-06-11 | Heat exchanger and air conditioning equipment |
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| CN210165622U true CN210165622U (en) | 2020-03-20 |
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Cited By (2)
| 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 |
| CN114543578A (en) * | 2020-11-25 | 2022-05-27 | 广州华凌制冷设备有限公司 | Heat exchanger, fins thereof, heat exchange equipment and air conditioner |
-
2019
- 2019-06-11 CN CN201920871575.9U patent/CN210165622U/en active Active
Cited By (2)
| 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 |
| CN114543578A (en) * | 2020-11-25 | 2022-05-27 | 广州华凌制冷设备有限公司 | Heat exchanger, fins thereof, heat exchange equipment and air conditioner |
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