CN214701320U - Air source heat pump system - Google Patents
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- CN214701320U CN214701320U CN202120639335.3U CN202120639335U CN214701320U CN 214701320 U CN214701320 U CN 214701320U CN 202120639335 U CN202120639335 U CN 202120639335U CN 214701320 U CN214701320 U CN 214701320U
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Abstract
The utility model provides an air source heat pump system relates to heat pump system technical field, provides a new air source heat pump system that can slow down heat exchanger frosting. The air source heat pump system comprises more than two outdoor heat exchangers, wherein each outdoor heat exchanger is divided into a preheating heat exchanger and a common heat exchanger, one side of each preheating heat exchanger is connected with the corresponding indoor heat exchanger, refrigerant discharged by the corresponding indoor heat exchanger can directly flow to the preheating heat exchanger without throttling, the other side of each preheating heat exchanger is connected with the corresponding common heat exchanger, a throttling device is arranged between the other side of each preheating heat exchanger and the corresponding common heat exchanger, the preheating heat exchangers can heat air passing through the preheating heat exchangers, and the air after temperature rise can flow to the common heat exchangers. The utility model is used for slow down the frosting rate of air source heat pump system heat exchanger.
Description
Technical Field
The utility model belongs to the technical field of heat pump system technique and specifically relates to an air source heat pump system is related to.
Background
The air source heat pump system has the problem that an air side heat exchanger frosts, once the heat exchanger frosts, the heat exchange performance of the heat exchanger is reduced, so that the frosting rate of the heat exchanger is reduced or the frosting of the heat exchanger is inhibited, and the heat exchange performance of the heat exchanger can be improved.
The applicant has found that the prior art has at least the following technical problems:
when the outdoor heat exchangers are in multiple rows (more than three rows and including three rows), the frosting rates of the outdoor heat exchangers in different rows are different, and generally, the heat exchanger on the leeward side frosts firstly, then the heat exchanger on the middle part and the heat exchanger on the windward side frosts last. Because the degree and the rate of the frosting of the heat exchanger are related to factors such as air relative humidity, air temperature, inlet air speed, fin structure and the like, the specific expression is that the higher the relative humidity of inlet air is, the more easily frosting is, the higher the frosting rate of the inlet air temperature in the interval of 0-3 ℃, the higher the inlet air speed is, the less easily frosting is, and the larger the fin interval is, the less easily frosting is. The air flows from the windward side to the leeward side, the heat of the air flowing through the surface of the heat exchanger is taken away along with the continuous evaporation of the refrigerant in the heat exchanger, the temperature of the air can be reduced, the relative humidity can be increased, and therefore the heat exchanger on the leeward side is easier to frost.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide an air source heat pump system provides a new air source heat pump system that can slow down the heat exchanger and frost. The utility model provides a plurality of technical effects that preferred technical scheme among a great deal of technical scheme can produce see the explanation below in detail.
In order to achieve the above purpose, the utility model provides a following technical scheme:
the utility model provides a pair of air source heat pump system, including two above outdoor heat exchangers, wherein, outdoor heat exchanger divide into and preheats heat exchanger and ordinary heat exchanger, preheat one side of heat exchanger and be connected with indoor heat exchanger just indoor heat exchanger exhaust refrigerant can be direct flow direction not throttled preheat the heat exchanger, preheat the heat exchanger the opposite side with ordinary heat exchanger is connected and is provided with throttling arrangement between the two, preheat the heat exchanger can heat through its air and the air energy flow after heaing up to ordinary heat exchanger.
Furthermore, the outdoor heat exchanger is divided into a windward side heat exchanger, an intermediate heat exchanger and a leeward side heat exchanger, the intermediate heat exchanger is located between the windward side heat exchanger and the leeward side heat exchanger, the windward side heat exchanger and the leeward side heat exchanger are the common heat exchanger, and the preheating heat exchanger is the intermediate heat exchanger.
Furthermore, the number of the middle heat exchangers is one, and the middle heat exchanger, the windward side heat exchanger and the leeward side heat exchanger are sequentially connected.
Furthermore, the number of the middle heat exchangers is one, and the middle heat exchanger, the leeward side heat exchanger and the windward side heat exchanger are sequentially connected.
Furthermore, the number of the intermediate heat exchangers is more than two, the outdoor heat exchangers are connected in series, and the common heat exchanger to which the refrigerant discharged from the preheating heat exchanger flows finally after throttling is the windward side heat exchanger or the leeward side heat exchanger or the intermediate heat exchanger.
Furthermore, the number of the intermediate heat exchangers is one; or the number of the intermediate heat exchangers is more than two, and air can sequentially pass through the windward side heat exchanger, the intermediate heat exchangers and the leeward side heat exchanger.
Further, the throttling device is an expansion valve.
Furthermore, a throttling device is arranged between the indoor heat exchanger and the preheating heat exchanger.
Further, a fan is arranged on one side of the leeward side heat exchanger or a fan is arranged on one side of the windward side heat exchanger.
Further, the air source heat pump system further comprises a compressor, a gas-liquid separator and a four-way change valve.
The air source heat pump system provided by the invention runs in a frost-inhibiting heating mode, low-temperature and high-pressure refrigerant discharged from an indoor heat exchanger flows to a preheating heat exchanger (at the moment, the preheating heat exchanger can be equivalent to a condenser), meanwhile, a throttling device is additionally arranged on the preheating heat exchanger and a common heat exchanger, the throttling device can be an expansion valve, the refrigerant discharged from the preheating heat exchanger is throttled by the throttling device to form low-temperature and low-pressure refrigerant to flow to the common heat exchanger (at the moment, the common heat exchanger is an evaporator), when the air passes through the preheating heat exchanger, the preheating heat exchanger can heat the air passing through the preheating heat exchanger, and the heated air can flow to the common heat exchanger (the common heat exchanger can be a heat exchanger which is relatively easy to frost in all outdoor heat exchangers), so that the temperature of the air blown through the common heat exchanger is increased, the relative humidity is reduced, it may be advantageous to slow the rate of heat exchanger frost formation.
The preferred technical scheme of the invention can at least produce the following technical effects:
since the frosting rate of the outdoor heat exchangers of different rows is different when the outdoor heat exchangers are in three rows, generally, the heat exchanger on the leeward side frosts first, then the heat exchanger on the middle part and the heat exchanger on the windward side frosts last. Therefore, the preheating heat exchanger is set as the intermediate heat exchanger, so that air is blown to the heat exchanger on the leeward side when passing through the preheating heat exchanger, and the frosting rate of the heat exchanger on the leeward side is reduced, so that the frosting rate of the whole heat exchanger is reduced;
the common heat exchanger in which the refrigerant discharged by the preheating heat exchanger flows finally is a leeward side heat exchanger, and the temperature of the refrigerant at the discharge port of the leeward side heat exchanger is relatively high, so that the frosting rate of the leeward side heat exchanger is favorably reduced.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a schematic wiring diagram of an air source heat pump system provided by an embodiment of the invention;
fig. 2 is a schematic wiring diagram of an air source heat pump system according to an embodiment of the present invention (illustrating a refrigerant direction in a cooling mode);
fig. 3 is a schematic wiring diagram of an air source heat pump system according to an embodiment of the present invention (illustrating a refrigerant direction in a heating mode);
fig. 4 is another schematic wiring diagram of the air source heat pump system provided by the embodiment of the invention.
FIG. 1-preheat heat exchanger; 2-a common heat exchanger; 3-indoor heat exchanger; 4-a throttling device; 41-first throttling means; 42-a second throttling device; 5-windward side heat exchanger; 6-intermediate heat exchanger; 7-a leeward side heat exchanger; 8-a fan; 9-a compressor; 10-a gas-liquid separator; 11-four-way change valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be described in detail below. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be derived by a person skilled in the art from the examples given herein without any inventive step, are within the scope of the present invention.
Referring to fig. 1-4, the invention provides an air source heat pump system, which comprises more than two outdoor heat exchangers, wherein the outdoor heat exchangers are divided into a preheating heat exchanger 1 and a common heat exchanger 2, one side of the preheating heat exchanger 1 is connected with an indoor heat exchanger 3, a refrigerant discharged by the indoor heat exchanger 3 can directly flow to the preheating heat exchanger 1 without throttling, the other side of the preheating heat exchanger 1 is connected with the common heat exchanger 2, a throttling device 4 is arranged between the preheating heat exchanger 1 and the common heat exchanger 2, the preheating heat exchanger 1 can heat air passing through the preheating heat exchanger, and the air after temperature rise can flow to the common heat exchanger 2. When the refrigerant discharged from the indoor heat exchanger 3 flows to the preheating heat exchanger 1 after being throttled by the throttling device, the heat pump system operates in a heating mode, and the preheating heat exchanger 1 and the common heat exchanger 2 are both evaporators. When the refrigerant discharged from the indoor heat exchanger 3 flows to the preheat heat exchanger 1 without throttling (i.e. the throttling device between the indoor heat exchanger 3 and the preheat heat exchanger 1 does not throttle), at this time, the heat pump system operates in a frost-suppressing heating mode, the low-temperature and high-pressure refrigerant discharged from the indoor heat exchanger 3 flows to the preheat heat exchanger 1 (at this time, the preheat heat exchanger 1 can be equivalent to a "condenser"), meanwhile, the throttle device 4 is additionally arranged on the preheat heat exchanger 1 and the common heat exchanger 2, the throttle device 4 can be an expansion valve, the refrigerant discharged from the preheat heat exchanger 1 is throttled by the throttle device 4 to form a low-temperature and low-pressure refrigerant which flows to the common heat exchanger 2 (at this time, the common heat exchanger 2 is an evaporator), when the air passes through the preheat heat exchanger 1, the preheat heat exchanger 1 can heat the air passing through the air, and the warmed air can flow to the common heat exchanger 2 (here, the common heat exchanger 2 can be in all outdoor heat exchangers, a heat exchanger that is relatively prone to frost) so that, as the temperature of the air blown through the conventional heat exchanger 2 increases, the relative humidity decreases, which can be beneficial in slowing the rate of frost formation in the heat exchanger.
As an optional embodiment, the outdoor heat exchanger is divided into a windward side heat exchanger 5, an intermediate heat exchanger 6 and a leeward side heat exchanger 7, the intermediate heat exchanger 6 is located between the windward side heat exchanger 5 and the leeward side heat exchanger 7, the windward side heat exchanger 5 and the leeward side heat exchanger 7 are common heat exchangers 2, and the preheating heat exchanger 1 is the intermediate heat exchanger 6. Referring to fig. 1, the positional relationship among the windward side heat exchanger 5, the intermediate heat exchanger 6, and the leeward side heat exchanger 7 is illustrated, the heat exchanger to which air is blown first is the windward side heat exchanger 5, and the heat exchanger to which air is blown last is the leeward side heat exchanger 7. Since the frost formation rate of the outdoor heat exchangers of different rows is different when the outdoor heat exchangers are in three rows, usually the leeward side heat exchanger 7 is frosted first, then the heat exchanger in the middle part, and the windward side heat exchanger is frosted last. Therefore, the preheating heat exchanger 1 is the intermediate heat exchanger 6, so that air is blown to the leeward side heat exchanger 7 when passing through the preheating heat exchanger 1, and the frosting rate of the leeward side heat exchanger 7 is reduced, so that the frosting rate of the whole heat exchanger is reduced.
As an alternative embodiment, the number of the intermediate heat exchangers 6 is one, and the common heat exchanger 2, to which the refrigerant discharged from the preheat heat exchanger 1 flows finally after being throttled, is the leeward side heat exchanger 7 or the windward side heat exchanger 5. Referring to fig. 3, it is shown that the general heat exchanger 2 in which the refrigerant discharged from the preheat heat exchanger 1 finally flows is the leeward side heat exchanger 7, and if the frost suppression refrigeration mode is adopted, the temperature of the refrigerant at the discharge port of the leeward side heat exchanger 7 is relatively high, so that the frosting rate of the leeward side heat exchanger 7 is favorably reduced. Of course, as shown in fig. 4, the ordinary heat exchanger 2 in which the refrigerant discharged from the preheat heat exchanger 1 flows last may be the windward heat exchanger 5.
In addition, when the number of the intermediate heat exchangers 6 is more than two, the outdoor heat exchangers are connected in series, and the common heat exchanger 2 in which the refrigerant discharged from the preheating heat exchanger 1 flows last may be the intermediate heat exchanger 6, the leeward side heat exchanger 7 or the windward side heat exchanger 5.
As an optional embodiment, the number of the intermediate heat exchangers 6 is one, and air can sequentially pass through the windward side heat exchanger 5, the intermediate heat exchanger 6 and the leeward side heat exchanger 7; alternatively, the number of the intermediate heat exchangers 6 is two or more and the air can sequentially pass through the windward side heat exchanger 5, each intermediate heat exchanger 6, and the leeward side heat exchanger 7. Referring to fig. 1, it is illustrated that one side of the leeward side heat exchanger 7 is provided with a fan 8. That is, due to the arrangement of the outdoor heat exchangers, all the outdoor heat exchangers can share one fan 8.
A method for slowing down the frosting rate of an air source heat pump system is characterized in that a refrigerant discharged by an indoor heat exchanger 3 directly flows to a preheating heat exchanger 1 without throttling, the refrigerant flowing out of the preheating heat exchanger 1 flows to a common heat exchanger 2 after throttling, the preheating heat exchanger 1 heats air passing through the preheating heat exchanger, and the air after temperature rise can flow to the common heat exchanger 2. The working modes of the air source heat pump system comprise a cooling mode and a heating mode, and the frosting condition of the heat exchanger is easy to occur in the heating mode, so that the heating mode is divided into a common heating mode and a frost-inhibiting heating mode, and in the frost-inhibiting heating mode, the method for slowing down the frosting rate is as follows: the low-temperature high-pressure refrigerant discharged from the indoor heat exchanger 3 flows to the preheating heat exchanger 1 (at this time, the preheating heat exchanger 1 can be equivalent to a 'condenser'), the refrigerant discharged from the preheating heat exchanger 1 is throttled by the throttling device 4 to form a low-temperature low-pressure refrigerant flowing to the common heat exchanger 2 (at this time, the common heat exchanger 2 is an evaporator), when the air passes through the preheating heat exchanger 1, the preheating heat exchanger 1 can heat the air passing through the preheating heat exchanger, and the heated air can flow to the common heat exchanger 2 (the common heat exchanger 2 can be a heat exchanger which is relatively easy to frost in all outdoor heat exchangers), so that the temperature of the air blown through the common heat exchanger 2 is increased, the relative humidity is reduced, and the frosting rate of the heat exchanger can be favorably reduced.
As an optional embodiment, the outdoor heat exchanger is divided into a windward side heat exchanger 5, an intermediate heat exchanger 6 and a leeward side heat exchanger 7, the intermediate heat exchanger 6 is located between the windward side heat exchanger 5 and the leeward side heat exchanger 7, the preheating heat exchanger 1 is the intermediate heat exchanger 6, when the number of the intermediate heat exchangers 6 is one, the refrigerant discharged by the indoor heat exchanger 3 directly flows to the intermediate heat exchanger 6 without throttling, then flows to the windward side heat exchanger 5 and the leeward side heat exchanger 7 in sequence after throttling, and the preheating heat exchanger 1 heats the air passing through the preheating heat exchanger and the air after temperature rise can flow to the leeward side heat exchanger 7. The concrete description is as follows:
when the air source heat pump system is in the cooling mode, referring to fig. 2, the flow direction of the refrigerant is as follows: after the high-temperature high-pressure gaseous refrigerant at the exhaust end of the compressor 9 is reversed by the four-way reversing valve 11, the discharged high-temperature high-pressure gaseous refrigerant sequentially enters the leeward side heat exchanger 7, the windward side heat exchanger 5 and the intermediate heat exchanger 6, and at the moment, the second throttling device 42 is in a fully open state, namely, no throttling occurs when the refrigerant passes through the second throttling device 42. The refrigerant is condensed by the outdoor heat exchanger to release heat, then changed into a low-temperature high-pressure liquid refrigerant, flows out of the intermediate heat exchanger 6, flows to the first throttling device 41, is throttled by the first throttling device 41, then is changed into a low-temperature low-pressure gas-liquid two-phase state from the low-temperature high-pressure liquid state, enters the indoor heat exchanger 3 to be evaporated and absorb heat, is changed into a low-temperature low-pressure gas state from the low-temperature low-pressure gas-liquid two-phase state after being evaporated and absorbed heat, then enters the gas-liquid separator 10 through the reversing of the four-way reversing valve 11, and finally enters the compressor 9 to complete the whole refrigeration cycle.
When the air source heat pump system is in the ordinary heating mode, referring to fig. 3, after the high-temperature gaseous refrigerant at the exhaust end of the compressor 9 is reversed by the four-way reversing valve 11, the refrigerant coming out enters the indoor heat exchanger 3 to be condensed and released heat, the liquid refrigerant which is changed into low-temperature and high-pressure refrigerant after being condensed and released heat flows out of the indoor heat exchanger 3, then flows to the first throttling device 41, the refrigerant is changed into a low-temperature low-pressure gas-liquid two-phase state from a low-temperature high-pressure liquid state after being throttled by the first throttling device 41, the low-temperature low-pressure gas-liquid two-phase state refrigerant sequentially enters the intermediate heat exchanger 6, the windward side heat exchanger 5 and the leeward side heat exchanger 7, the refrigerant is changed into a low-temperature low-pressure gaseous state refrigerant after being evaporated and absorbed heat by the outdoor heat exchanger and flows out of the leeward side heat exchanger 7, then enters a gas-liquid separator 10 through the reversing of a four-way reversing valve 11, and finally enters a compressor 9, thus completing the whole common heating cycle.
When the air source heat pump system is in the frost suppression and heating mode, referring to fig. 3, after the high-temperature gaseous refrigerant at the exhaust end of the compressor 9 is firstly reversed by the four-way reversing valve 11, the discharged refrigerant enters the indoor heat exchanger 3 to be condensed and released, the condensed and released refrigerant becomes low-temperature high-pressure liquid refrigerant and flows out of the indoor heat exchanger 3, and then flows to the first throttling device 41, at this time, the first throttling device 41 is in a fully open state, namely, the refrigerant is not throttled when passing through the first throttling device 41, then the low-temperature high-pressure liquid refrigerant enters the intermediate heat exchanger 6 to be condensed continuously, and then flows to the second throttling device 42, the refrigerant is changed into low-temperature low-pressure gas-liquid two-phase state from the low-temperature high-pressure liquid state after being throttled by the second throttling device 42, the low-temperature low-pressure gas-liquid two-phase refrigerant sequentially enters the windward side heat exchanger 5 and the leeward side heat exchanger 7, and the refrigerant is changed into low-temperature low-pressure gas-liquid two-phase state after being evaporated and absorbed by the windward side heat exchanger 5 and the leeward side heat exchanger 7 Flows out of the leeward side heat exchanger 7, enters a gas-liquid separator 10 through the reversing of a four-way reversing valve 11, and finally enters a compressor 9 to finish the whole frost-inhibiting heating cycle.
In addition, the connection order of the windward heat exchanger 5, the intermediate heat exchanger 6, and the leeward heat exchanger 7 may be as follows: the refrigerant discharged from the indoor heat exchanger 3 directly flows to the intermediate heat exchanger 6 without being throttled, then flows to the leeward side heat exchanger 7 and the windward side heat exchanger 5 in sequence after being throttled, and the preheating heat exchanger 1 heats the air passing through the preheating heat exchanger so that the heated air flows to the leeward side heat exchanger 7. Referring to fig. 4, the connection relationship of the air source heat pump system is illustrated.
As an optional embodiment, the outdoor heat exchanger is divided into a windward side heat exchanger 5, an intermediate heat exchanger 6 and a leeward side heat exchanger 7, the intermediate heat exchanger 6 is located between the windward side heat exchanger 5 and the leeward side heat exchanger 7, the preheating heat exchanger 1 is the intermediate heat exchanger 6, the number of the intermediate heat exchangers 6 is more than two, the outdoor heat exchangers are connected in series, a refrigerant discharged by the indoor heat exchanger 3 directly flows to the intermediate heat exchanger 6 without throttling, then flows to the common heat exchangers 2 in sequence after throttling, and the preheating heat exchanger 1 heats air passing through the preheating heat exchanger and heats the air flow to one side of the leeward side heat exchanger 7.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and the changes or substitutions should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the appended claims.
Claims (10)
1. An air source heat pump system is characterized by comprising more than two outdoor heat exchangers,
the outdoor heat exchanger is divided into a preheating heat exchanger (1) and a common heat exchanger (2), one side of the preheating heat exchanger (1) is connected with an indoor heat exchanger (3), refrigerant discharged by the indoor heat exchanger (3) can directly flow to the preheating heat exchanger (1) without throttling, the other side of the preheating heat exchanger (1) is connected with the common heat exchanger (2) and a throttling device (4) is arranged between the preheating heat exchanger and the common heat exchanger (2), the preheating heat exchanger (1) can heat air passing through the preheating heat exchanger and the air after temperature rise can flow to the common heat exchanger (2).
2. The air-source heat pump system according to claim 1, wherein the outdoor heat exchanger is divided into a windward side heat exchanger (5), an intermediate heat exchanger (6) and a leeward side heat exchanger (7), the intermediate heat exchanger (6) is located between the windward side heat exchanger (5) and the leeward side heat exchanger (7), the windward side heat exchanger (5) and the leeward side heat exchanger (7) are the common heat exchanger (2), and the preheating heat exchanger (1) is the intermediate heat exchanger (6).
3. The air-source heat pump system according to claim 2, wherein the number of the intermediate heat exchangers (6) is one, and the intermediate heat exchanger (6), the windward side heat exchanger (5) and the leeward side heat exchanger (7) are connected in sequence.
4. The air-source heat pump system according to claim 2, wherein the number of the intermediate heat exchangers (6) is one, and the intermediate heat exchanger (6), the leeward side heat exchanger (7) and the windward side heat exchanger (5) are connected in sequence.
5. The air-source heat pump system according to claim 2, wherein the number of the intermediate heat exchangers (6) is two or more, the outdoor heat exchangers are connected in series, and the common heat exchanger (2) to which the refrigerant discharged from the preheating heat exchanger (1) flows finally after throttling is the windward side heat exchanger (5) or the leeward side heat exchanger (7) or the intermediate heat exchanger (6).
6. The air-source heat pump system according to claim 2, wherein the number of intermediate heat exchangers (6) is one; or the number of the intermediate heat exchangers (6) is more than two, and air can sequentially pass through the windward side heat exchanger (5), each intermediate heat exchanger (6) and the leeward side heat exchanger (7).
7. The air-source heat pump system according to any of claims 1-6, wherein the throttling device (4) is an expansion valve.
8. Air-source heat pump system according to any of claims 1-6, characterized in that a throttle device (4) is arranged between the indoor heat exchanger (3) and the preheat heat exchanger (1).
9. An air-source heat pump system according to claim 2, characterized in that one side of the leeward side heat exchanger (7) is provided with a fan (8) or one side of the windward side heat exchanger (5) is provided with a fan (8).
10. The air-source heat pump system according to any one of claims 1-6, further comprising a compressor (9), a gas-liquid separator (10), and a four-way change valve (11).
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| CN202120639335.3U CN214701320U (en) | 2021-03-29 | 2021-03-29 | Air source heat pump system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112944709A (en) * | 2021-03-29 | 2021-06-11 | 珠海格力电器股份有限公司 | Air source heat pump system and method for slowing down frosting rate |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112944709A (en) * | 2021-03-29 | 2021-06-11 | 珠海格力电器股份有限公司 | Air source heat pump system and method for slowing down frosting rate |
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