CN216814403U - Air source heat pump system - Google Patents
Air source heat pump system Download PDFInfo
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- CN216814403U CN216814403U CN202220082710.3U CN202220082710U CN216814403U CN 216814403 U CN216814403 U CN 216814403U CN 202220082710 U CN202220082710 U CN 202220082710U CN 216814403 U CN216814403 U CN 216814403U
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Abstract
The utility model discloses an air source heat pump system, comprising: an outdoor unit including: an upper outdoor heat exchanger configured to exchange heat with the heat source side, and a lower outdoor heat exchanger configured to exchange heat with the heat source side and disposed below the upper outdoor heat exchanger in order in a height direction of the outdoor unit; in the heating mode, one of the upper outdoor heat exchanger and the lower outdoor heat exchanger is selectively supplied with a high-temperature refrigerant to melt a surface frost layer, and the other is heat-exchanged with the heat source side as an evaporator. When the air source heat pump system provided by the utility model is in defrosting operation, one of the upper outdoor heat exchanger and the lower outdoor heat exchanger can selectively introduce high-temperature refrigerant to melt surface frost layer, and the other one is used as an evaporator to perform heat exchange with the heat source side, so that one in a non-defrosting state can still be used as the evaporator, the indoor unit is kept in a heating and air supply state, and continuous heating operation is realized.
Description
Technical Field
The utility model belongs to the technical field of air conditioning, and particularly relates to an air source heat pump system.
Background
In an air-source heat pump system, one or more outdoor units are connected to one or more indoor units via pipes to form a refrigerant circuit of a refrigeration system. The common outdoor unit at least comprises a compressor, an outdoor heat exchanger, a reversing valve, an outdoor fan and a throttling element, and the indoor unit at least comprises an indoor heat exchanger and an indoor fan. The air source heat pump system realizes the switching of the refrigeration cycle and the heating cycle through the reversing valve. When the air source heat pump works in a heating mode, if the outdoor environment temperature is lower and the humidity is higher, the outer surface of the outdoor heat exchanger can frost, and the frost layer can cause the performance and the heat supply quantity of the air source heat pump system to be reduced. When the frosting is serious, the air source heat pump system automatically enters a defrosting mode.
Common defrosting modes of the air source heat pump system include two modes: the first is reverse defrost. After entering the defrosting mode, the air source heat pump system switches the self-heating mode to the refrigerating mode, namely the flowing direction of the refrigerant is changed, the outdoor heat exchanger is switched from the low-temperature low-pressure evaporator to the high-temperature high-pressure condenser, and the heat of the refrigerant discharged by the compressor is utilized to defrost the outdoor heat exchanger. The indoor heat exchanger is switched to a low-temperature low-pressure evaporator by a high-temperature high-pressure condenser, and the indoor unit fan is closed. The defrosting process absorbs heat from a room, so that the comfort of the room environment is poor, when the defrosting mode is switched to the heating mode again after the defrosting is finished, the temperature of a refrigerant liquid pipe on one side of the indoor unit is low, the indoor unit can be exhausted for heating after the heating temperature is recovered for a long time, so that the capacity of the indoor unit is slowly increased, and the cycle capacity is low. In the defrosting process, the indoor fan is turned off, so that more liquid refrigerant is reserved in the gas-liquid separator, and after defrosting, the liquid refrigerant can enter the compressor at the moment of starting, so that liquid impact can occur to reduce the stability of the system. The second is hot gas bypass defrost. The hot gas bypass defrosting does not change the refrigerant circulation, and a bypass branch is led out from the exhaust side of the compressor to one side of a main liquid pipe of the outdoor heat exchanger. In the defrosting process, the bypass branch is opened, the exhaust gas of the compressor directly enters the outdoor heat exchanger for defrosting, and the heat source for hot gas bypass defrosting is the compressor, so that the capacity of the compressor is insufficient to support the air outlet of the indoor unit for heating during defrosting, and the comfort of the indoor environment is reduced. When frost is more or the environmental temperature is lower, the defrosting time may be long, and even the reliability problems such as incomplete defrosting may occur.
Various uninterrupted heating and air conditioning devices are disclosed in the prior art, such as the technical scheme disclosed in chinese patent (CN 102272534A): an air conditioning apparatus in which an outdoor unit (51) and a plurality of indoor units (55) are connected by piping to form a refrigerant circuit, wherein the outdoor unit (51) has a compressor (1) that pressurizes and discharges a refrigerant, a plurality of outdoor heat exchangers (3) that exchange heat between outside air and the refrigerant, and a four-way valve (2) that switches flow paths based on the operation mode; the indoor unit (53) has an indoor heat exchanger (32) for exchanging heat between air in a space to be air-conditioned and a refrigerant, and an indoor throttle device (31), and the outdoor unit (51) has: a bypass pipe (10) for branching off the refrigerant discharged from the compressor (1) and allowing the refrigerant to flow into each of the outdoor heat exchangers (3) connected in parallel by a pipe; a plurality of outdoor side 3-th opening/closing valves 8 for passing or blocking the refrigerant from the bypass pipe 10 to the outdoor side heat exchangers 3; and a plurality of outdoor side 2-way opening/closing valves (7) for passing or cutting off the refrigerant from the indoor unit (53) to the respective outdoor side heat exchangers (3). The scheme is that the outdoor heat exchanger is divided into zones, a hot gas bypass branch is arranged at the refrigerant inlet of the outdoor heat exchanger corresponding to each zone, and throttling devices are respectively arranged at the inlet and the outlet of each outdoor heat exchanger. The scheme can realize defrosting of part of the heat exchangers, namely subarea defrosting, namely that the four-way valve is not reversed, a hot gas bypass branch valve corresponding to the outdoor heat exchanger for defrosting is opened, the exhaust of the compressor is directly utilized for defrosting, the defrosting pressure is controlled by the valve at the outlet of the defrosting heat exchanger and the hot gas bypass valve, and the outdoor heat exchanger in a non-defrosting state is still used as an evaporator, so that uninterrupted heating is realized.
Firstly, a plurality of outdoor heat exchangers work with the same outdoor fan, the wind fields are mixed, and obvious heat waste exists during defrosting, particularly at low ambient temperature; secondly, the pressure loss caused by the throttling device is large, and the system performance can be obviously influenced during normal heating or refrigeration; thirdly, the system adds more valves, but cannot realize the independent reversing of each outdoor heat exchanger and each indoor machine.
The above information disclosed in this background section is only for enhancement of understanding of the background of the application and therefore it may comprise prior art that does not constitute known to a person of ordinary skill in the art.
Disclosure of Invention
The utility model designs and provides an air source heat pump system aiming at the problems that in the prior art, in the defrosting process of the traditional reverse defrosting and hot gas bypass defrosting of an air source heat pump system, an indoor unit cannot keep an air supply state, so that the indoor temperature greatly fluctuates, the comfort is reduced, the air outlet speed is low when the air source heat pump system is started again after defrosting, the system response period is prolonged, and the reliability of a compressor and defrosting is difficult to guarantee.
In order to realize the purpose of the utility model, the utility model adopts the following technical scheme to realize:
an air-source heat pump system comprising: an outdoor unit comprising: an upper outdoor heat exchanger configured to exchange heat with a heat source side; and a lower outdoor heat exchanger configured to exchange heat with a heat source side and disposed below the upper outdoor heat exchanger in order in a height direction of the outdoor unit; in the heating mode, one of the upper outdoor heat exchanger and the lower outdoor heat exchanger is selectively supplied with a high-temperature refrigerant to melt a surface frost layer, and the other is heat-exchanged with a heat source side as an evaporator.
Compared with the prior art, the utility model has the advantages and positive effects that:
in the defrosting operation, one of the upper outdoor heat exchanger and the lower outdoor heat exchanger is selectively led with high-temperature refrigerant to melt the surface frost layer, and the other one is used as an evaporator to perform heat exchange with the heat source side, so that one in a non-defrosting state can still be used as the evaporator, the indoor unit is kept in a heating and air supplying state, and the continuous heating operation is realized.
Other features and advantages of the present invention will become more apparent from the following detailed description of the utility model when taken in conjunction with the accompanying drawings.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
FIG. 1 is a block diagram schematically illustrating the construction of an outdoor unit in an air-source heat pump system according to the present invention;
FIG. 2 is a schematic block diagram of another configuration of an outdoor unit in an air-source heat pump system according to the present invention;
FIG. 3 is a schematic view of a refrigeration cycle of a first embodiment of an air-source heat pump system provided by the present invention;
FIG. 4 is a schematic diagram of a refrigeration cycle of a second embodiment of an air source heat pump system provided by the present invention;
fig. 5 is a P-h diagram (pressure-specific enthalpy diagram) of the air source heat pump system shown in fig. 4 when operating in the full heating defrost mode;
fig. 6 is a graph showing a capacity change of an indoor unit when the air source heat pump system shown in fig. 4 is operated in a full heating defrost mode;
fig. 7 is a graph showing a temperature change of an indoor unit when the air source heat pump system shown in fig. 4 is operated in a full heating defrost mode;
fig. 8 is a P-h diagram (pressure-specific enthalpy diagram) of the air source heat pump system shown in fig. 4 when operating in the main heating defrost mode.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the accompanying drawings and examples.
It should be noted that in the description of the present invention, the terms of direction or positional relationship indicated by the terms "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, which are merely for convenience of description, and do not indicate or imply that the device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
When the outdoor environment temperature is low and the humidity is high, the problem of frosting on the surface of the outdoor heat exchanger exists in the air source heat pump system during heating, when frost layers are accumulated, the refrigerant in the outdoor heat exchanger cannot perform sufficient heat exchange with air, so that the capacity of an outdoor unit is reduced, and further the heating capacity of an indoor unit cannot be fully exerted. When the frosting is serious, the air source heat pump system needs to execute the defrosting operation. The utility model designs and provides an air source heat pump system in order to solve the problems that in the defrosting process of the traditional reverse defrosting and hot gas bypass defrosting, the indoor temperature is greatly fluctuated due to the fact that an indoor unit cannot keep an air supply state, the comfort is reduced, the air outlet speed is low when the system is started again after defrosting, the response period of the system is prolonged, and the reliability of a compressor and defrosting is difficult to guarantee. Fig. 1 shows a block schematic diagram of the structure of an outdoor unit in one particular embodiment of an air-source heat pump system. As shown in fig. 1, the outdoor unit 100 specifically includes an upper outdoor heat exchanger 101 and a lower outdoor heat exchanger 102, each of the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102 being configured to exchange heat source-side heat. The heat source includes, but is not limited to, air in an outdoor environment. The lower outdoor heat exchanger 102 is disposed below the upper outdoor heat exchanger 101 in order in the height direction of the outdoor unit 100. In the heating mode, when the defrosting condition is satisfied, one of the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102 selectively passes a high-temperature refrigerant to melt a surface frost layer, and the other exchanges heat with the heat source side as an evaporator. By dividing the outdoor heat exchanger into an upper outdoor heat exchanger 101 and a lower outdoor heat exchanger 102. In the defrosting operation, the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102 are selectively switched, one of the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102 in the non-defrosting state can still be used as an evaporator, and the indoor unit maintains a heating and air-out state, thereby realizing a continuous heating operation. The upper and lower outdoor heat exchangers 101 and 102 disposed in the height direction of the outdoor unit 100 can also reduce the overall width of the outdoor unit 100 to facilitate piping. Because the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102 can be independently reversed, the air source heat pump system can execute a more flexible and fine heat recovery function or cope with small fluctuation of air conditioning load, and the optimal control of the air source heat pump system is realized.
In the air source heat pump system provided in the present embodiment, the upper outdoor heat exchanger 101 is provided with the upper outdoor fan 103, and the lower outdoor heat exchanger 102 is provided with the lower outdoor fan 104, so that a vertically partitioned wind field is formed near the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102. In the defrosting operation, the upper outdoor fan 103 and the lower outdoor fan 104 are driven by switching to selectively match the operating states of the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102. Specifically, the upper outdoor fan 103 is configured to stop operating when the upper outdoor heat exchanger 101 is fed with high-temperature refrigerant to melt a surface frost layer, and is configured to start operating when the upper outdoor heat exchanger 101 performs heat exchange with the heat source side as an evaporator. Correspondingly, the lower outdoor fan 104 is configured to stop operating when the lower outdoor heat exchanger 102 is fed with high-temperature refrigerant to melt the surface frost layer, and is configured to start operating when the lower outdoor heat exchanger 102 exchanges heat with the heat source side as an evaporator. When the upper outdoor heat exchanger 101 performs defrosting operation, the upper outdoor fan 103 stops operating, the heat of the high-temperature refrigerant can be fully used for defrosting and cannot be taken away by air flow, the lower outdoor heat exchanger 102 keeps the working state of the evaporator, and the lower outdoor fan 104 normally operates, so that the air source heat pump system can be ensured to have certain air conditioning capacity, and the temperature of an air-conditioned room cannot fluctuate violently.
In the present embodiment, the blowing port of the outdoor unit 100 is formed at one side of the outdoor unit 100, and the upper outdoor fan 103 and the lower outdoor fan 104 are sequentially disposed from top to bottom in the height direction of the outdoor unit 100. An air field isolation plate 105 is installed between the upper outdoor fan 103 and the lower outdoor fan 104. The wind field isolation plate 105 may prevent the air flow generated when the upper and lower outdoor fans 103 and 104 are operated at the start from heat exchanging with the adjacent lower or upper outdoor heat exchanger 102 or 101 performing the defrosting operation, resulting in heat loss. The width of the wind field isolation plate 105 is preferably maintained to be identical to that of the outdoor unit 100, i.e., to completely separate the upper and lower wind fields.
Preferably, an upper drain 106 is provided below the upper outdoor heat exchanger 101, and a lower drain 107 is provided below the lower outdoor heat exchanger 102. With this configuration, after the defrosting operation of the upper outdoor heat exchanger 101 is completed, the water generated during the defrosting operation can be discharged in time through the upper drain 106. It will be understood that, when the upper outdoor heat exchanger 101 is defrosted, the surface thereof is in a frosted state and the temperature is low because the lower outdoor heat exchanger 102 is still operating in an evaporator state. If the water generated during defrosting is not discharged in time, it is more likely that the water will generate an ice layer on the surface of the lower outdoor heat exchanger 102, which may worsen the frosting condition of the lower outdoor heat exchanger 102 and increase the energy consumption of the lower outdoor heat exchanger 102 during defrosting. If the lower outdoor heat exchanger 102 is defrosted first and then the upper outdoor heat exchanger 101 is defrosted, if the water generated during defrosting is not discharged in time, the water covers the surface of the lower outdoor heat exchanger 102, and the lower outdoor heat exchanger 102 may be frosted again due to low outdoor temperature and high humidity. The separate arrangement of the upper drain 106 and the lower drain 107 solves this problem by draining in time to avoid increased defrosting power consumption. An alternative would be to replace the lower drain 107 with a conventional drip tray, not having the upper drain 106, and by controlling the number of defrost cycles and defrost sequence during the defrost cycle. The upper drain 106 and the lower drain 107 include, but are not limited to, a water receiving container, a water pipe, and the like. In a special use scenario, the drainage device may also comprise a water pump.
From the structural point of view, the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102 may be the upper and lower heat exchange areas of the same heat exchanger, for example, the upper and lower heat exchange areas of the same fin-and-tube heat exchanger. Two heat exchangers, for example, two fin-and-tube heat exchangers, may be installed in sequence from top to bottom in the height direction of the outdoor unit 100.
It may be set that one defrosting operation is performed for each of the upper and lower outdoor heat exchangers 101 and 102 in one defrosting cycle. Specifically, when the defrosting operation is performed on the upper outdoor heat exchanger 101, the upper outdoor fan 103 is turned off, the upper outdoor heat exchanger 101 performs the defrosting operation, moisture generated during the defrosting process is discharged through the upper drain 106, the lower outdoor fan 104 is operated, and the lower outdoor heat exchanger 102 is used as an evaporator. When the defrosting operation is performed on the lower outdoor heat exchanger 102, the lower outdoor fan 104 is turned off, the lower outdoor heat exchanger 102 performs the defrosting operation, moisture generated during the defrosting process is discharged through the lower drain 107, the upper outdoor heat exchanger 101 is used as an evaporator, and the upper outdoor fan 103 is operated. With this arrangement, in any defrosting cycle, one of the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102 is used as an evaporator, and the indoor unit can be maintained in a high-pressure or heating state, thereby realizing an uninterrupted heating function.
It is also possible to set the defrosting operation to be performed once for the upper outdoor heat exchanger 101 and twice for the lower outdoor heat exchanger 102 in one defrosting cycle, respectively, which is particularly suitable for the case where a drain pan is used as the lower drain 107. Specifically, the lower outdoor heat exchanger 102 is first subjected to a defrosting operation, the lower outdoor fan 104 is turned off, the upper outdoor fan 103 is operated, the upper outdoor heat exchanger 101 operates as an evaporator, water generated during defrosting of the lower outdoor heat exchanger 102 is discharged in time through the lower drain 107, defrosting reliability is ensured, the indoor unit maintains a high-pressure operating state and an air blowing operation can be realized. Then, the defrosting operation is performed on the upper outdoor heat exchanger 101, the upper outdoor fan 103 is turned off, the lower outdoor fan 104 is operated, and the lower outdoor heat exchanger 102 operates as an evaporator, and at this time, the lower outdoor heat exchanger 102 can secure the blowing function of the indoor unit and maintain the heating capacity due to the fact that the defrosting operation is just completed. Finally, the lower outdoor heat exchanger 102 is subjected to the secondary defrosting operation, the lower outdoor fan 104 is turned off, the upper outdoor fan 103 is kept running, and the upper outdoor heat exchanger 101 is operated as an evaporator. After the second defrosting operation is completed, the water generated in the latter two processes is once discharged through the lower drain 107.
The defrost cycle is initiated and terminated using the defrost conditions and the exit defrost conditions customary in the art. This is well known to those skilled in the art and includes temperature, pressure or a combination of temperature and pressure as the determination conditions. The defrost cycle and defrost conditions are not the point of protection for the present invention and will not be described further herein.
In the present invention, different operation states of the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102, i.e., one of them can selectively let in high-temperature refrigerant to melt a surface frost layer, and the other as an evaporator and heat source side heat exchange are realized by a combination of a plurality of valves. The plurality of valves comprise a first reversing valve 108, indoor expansion valves (201-; the indoor expansion valves (201 and 201-2) are arranged corresponding to the indoor heat exchangers (200 and 1 and 200-2); the bypass expansion valve 202 is provided between the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102, and the bypass expansion valve 202 is connected to the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102, respectively; the upper expansion valve 203 is provided corresponding to the upper outdoor heat exchanger 101; the lower expansion valve 204 is provided corresponding to the lower outdoor heat exchanger 102; the first expansion valve 205 is connected to the discharge side of the compressor 109, the first expansion valve 205 is preferably an electronic expansion valve, and controls the defrosting pressure by adjusting the opening degree of the valve to realize the pressure-controlled defrosting process, and the first expansion valve 205 may also be a throttle capillary tube; one port of the second direction valve 206 is connected to the upper outdoor heat exchanger 101, and the other port is connected to the discharge side of the compressor 109 via the first expansion valve 205; one port of the third direction valve 207 is connected to the lower outdoor heat exchanger 102, and the other port is connected to the discharge side of the compressor 109 via the first expansion valve 205.
The refrigeration cycle of the first embodiment of the air-source heat pump system 10 is described with reference to fig. 3; wherein the upper outdoor heat exchanger 101 is supplied with a high temperature refrigerant through the selectively conducted first defrosting passage D10 to melt the surface frost layer; as shown in fig. 3, the first defrost path D10 includes the discharge side of the compressor 109, the first expansion valve 205, the second direction change valve 206, the upper outdoor heat exchanger 101, and the bypass expansion valve 202, which are connected in this order; one path of the inlet of the lower outdoor heat exchanger 102 is connected with a lower expansion valve 204, and the other path is connected with a bypass expansion valve 202; the refrigerant discharged from the discharge side of the compressor 109 enters the lower outdoor heat exchanger 102 via the first direction changing valve 108, the indoor heat exchangers (200-; the refrigerant discharged from the upper outdoor heat exchanger 101 enters the lower outdoor heat exchanger 102 through the bypass expansion valve 202, and the refrigerant discharged from the lower outdoor heat exchanger 102 enters the suction side of the compressor 109 through the third direction changing valve 207 to form a first refrigerant circuit F10 that can be selectively switched on; the lower outdoor heat exchanger 102 operates as an evaporator in the first refrigerant circuit F10.
Similarly, the lower outdoor heat exchanger 102 is supplied with a high-temperature refrigerant through a second defrosting passage (not shown) selectively opened to melt the surface frost layer; the second defrost path includes the discharge side of the compressor 109, the first expansion valve 205, the third direction changing valve 207, the lower outdoor heat exchanger 102, and the bypass expansion valve 202, which are sequentially communicated. One path of the inlet of the upper outdoor heat exchanger 101 is connected with an upper expansion valve 203, and the other path is connected with a bypass expansion valve 202; the refrigerant discharged from the discharge side of the compressor 109 enters the upper outdoor heat exchanger 101 via the first direction changing valve 108, the indoor heat exchangers (200-; the refrigerant discharged from the lower outdoor heat exchanger 102 enters the upper outdoor heat exchanger 101 through the bypass expansion valve 202, and the refrigerant discharged from the upper outdoor heat exchanger 101 enters the suction side of the compressor 109 through the second direction changing valve 206 to form a second refrigerant circuit selectively opened; the upper outdoor heat exchanger 101 operates as an evaporator in the second refrigerant circuit.
A refrigeration cycle of a second embodiment of the air source heat pump system 10 is shown in fig. 4. The air source heat pump system 10 using the refrigeration cycle can work in a full heating state or a main heating state, and can realize effective defrosting and uninterrupted heating in both states. In contrast to the first embodiment, the indoor heat exchangers (200-) 1, 200-2) include at least the first indoor heat exchanger 200-1 operating as a condenser and the second indoor heat exchanger 200-2 operating as an evaporator in the main heating state. In order to realize heating and cooling operation at the same time, the air-source heat pump system 10 further comprises a first valve 209-1 and a second valve 301-1, wherein one valve port of the first valve 209-1 is connected with the first indoor heat exchanger 200-1, and the other valve port is connected with the discharge side of the compressor 109; one port of the second valve 301-1 is connected to the second indoor heat exchanger 200-2, and the other port is connected to the suction side of the compressor 109. Since the first indoor heat exchanger 200-1 can also operate as an evaporator and the second indoor heat exchanger 200-2 can also operate as a condenser, another set of corresponding first and second valves 209-2 and 301-2 is provided.
The operation of the air-source heat pump system 10 during a defrost cycle in the full heat mode will now be described in detail with reference to fig. 4. In the heating only state, in the outdoor unit 100, both the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102 operate as evaporators. When the ambient temperature is low and the humidity is high, frost layers appear on the surfaces of the upper outdoor heat exchanger 101 and the lower outdoor heat exchanger 102, the air source heat pump system 10 starts a defrosting cycle, at this time, the indoor heat exchanger still works as a condenser, and the indoor unit is in a heating or heating air supply state. A shift defrosting operation is performed, preferably defrosting the upper outdoor heat exchanger 101 first, and the lower outdoor heat exchanger 102 is kept operating as an evaporator. The upper outdoor heat exchanger 101 is supplied with high-temperature refrigerant through the selectively-conducted first defrosting passage D10 to melt the surface frost layer; the first defrost path D10 includes the discharge side of the compressor 109, the first expansion valve 205, the second direction change valve 206, the upper outdoor heat exchanger 101, and the bypass expansion valve 202, which are connected in this order; one path of the inlet of the lower outdoor heat exchanger 102 is connected with a lower expansion valve 204, and the other path is connected with a bypass expansion valve 202; the refrigerant discharged from the discharge side of the compressor 109 enters the lower outdoor heat exchanger 102 via the first direction changing valve 108, the indoor heat exchangers (200-; the refrigerant discharged from the upper outdoor heat exchanger 101 enters the lower outdoor heat exchanger 102 through the bypass expansion valve 202, and the refrigerant discharged from the lower outdoor heat exchanger 102 enters the suction side of the compressor 109 through the third direction changing valve 207 to form a first refrigerant circuit F10 selectively conducting; the lower outdoor heat exchanger 102 operates as an evaporator in the first refrigerant circuit F10. The lower outdoor heat exchanger 102 may also perform a similar defrosting process, which is not repeated here.
The refrigeration system will be described with reference to the first indoor heat exchanger 200-1 operating as a condenser and the second indoor heat exchanger 200-2 operating as an evaporator in a main heating state, as an example. The first indoor heat exchanger 200-1 is correspondingly provided with a first indoor expansion valve 201-1, and the second indoor heat exchanger 200-2 is correspondingly provided with a second indoor expansion valve 201-2. The main heating state is different from the full heating state in that the third refrigerant circuit F30 is also formed. The refrigerant flowing out of the first indoor heat exchanger is divided into two paths, one of which flows along the flow path of the first refrigerant circuit F10, the other of which enters the second indoor heat exchanger 200-2 via the second indoor expansion valve 201-2 corresponding to the second indoor heat exchanger 200-2, is evaporated into a low-temperature and low-pressure gaseous refrigerant, and cools the refrigerant, and the cooled refrigerant enters the suction side of the compressor 109 via the corresponding second valve 301-1, namely, returns to the compressor 109 through the gas-liquid separator 208 and is compressed again. The first defrost passage D10 and the first refrigerant circuit F10 in the main heating state coincide with the full heating state, and thus, no detailed description thereof will be given.
In the present invention, the first direction valve 108, the second direction valve 206, and the third direction valve 207 may be a four-way direction valve, a pilot type three-way valve, or other low resistance three-way valve. The states of the first reversing valve 108, the second reversing valve 206 and the third reversing valve 207 can be switched to a refrigeration mode and a main refrigeration mode.
The above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions.
Claims (10)
1. An air-source heat pump system, comprising:
an outdoor unit comprising:
an upper outdoor heat exchanger configured to exchange heat with a heat source side; and
a lower outdoor heat exchanger configured to exchange heat with a heat source side and disposed below the upper outdoor heat exchanger in order in a height direction of the outdoor unit;
in the heating mode, one of the upper outdoor heat exchanger and the lower outdoor heat exchanger is selectively supplied with a high-temperature refrigerant to melt a surface frost layer, and the other is heat-exchanged with a heat source side as an evaporator.
2. The air-source heat pump system of claim 1,
the outdoor unit further includes:
an upper outdoor fan disposed at one side of the upper outdoor heat exchanger; the upper outdoor fan is configured to stop operating when the upper outdoor heat exchanger is supplied with high-temperature refrigerant to melt a surface frost layer, and configured to start operating when the upper outdoor heat exchanger is heat-exchanged with a heat source side as an evaporator; and
a lower outdoor fan disposed at one side of the lower outdoor heat exchanger; the lower outdoor fan is configured to stop operating when the lower outdoor heat exchanger is supplied with a high-temperature refrigerant to melt a surface frost layer, and configured to start operating when the lower outdoor heat exchanger is heat-exchanged with the heat source side as an evaporator.
3. The air-source heat pump system of claim 2,
the upper outdoor fan and the lower outdoor fan are sequentially arranged from top to bottom along the height direction of the outdoor unit.
4. The air source heat pump system according to claim 3,
the outdoor unit further includes:
and the wind field isolation plate is arranged between the upper outdoor fan and the lower outdoor fan.
5. The air-source heat pump system of claim 1,
the outdoor unit further includes:
an upper drain disposed below the upper outdoor heat exchanger; and/or
A lower drain disposed below the lower outdoor heat exchanger.
6. The air-source heat pump system of claim 1,
the upper outdoor heat exchanger and the lower outdoor heat exchanger are upper and lower heat exchange areas of the same heat exchanger; or the upper outdoor heat exchanger and the lower outdoor heat exchanger are two heat exchangers which are sequentially installed from top to bottom along the height direction of the outdoor unit.
7. The air source heat pump system according to any one of claims 1 to 6,
the air-source heat pump system further comprises:
a first direction valve, one valve port of which is connected with the discharge side of the compressor, and the other valve port of which is connected with a plurality of indoor heat exchangers respectively;
an indoor expansion valve provided corresponding to the plurality of indoor heat exchangers;
a bypass expansion valve disposed between the upper outdoor heat exchanger and the lower outdoor heat exchanger, the bypass expansion valve being connected to the upper outdoor heat exchanger and the lower outdoor heat exchanger, respectively;
an upper expansion valve disposed corresponding to the upper outdoor heat exchanger;
a lower expansion valve provided corresponding to the lower outdoor heat exchanger;
a first expansion valve connected to a discharge side of the compressor;
a second direction valve having one port connected to the upper outdoor heat exchanger and the other port connected to a discharge side of the compressor via the first expansion valve; and
and a third direction valve having one port connected to the lower outdoor heat exchanger and the other port connected to a discharge side of the compressor via the first expansion valve.
8. The air source heat pump system of claim 7,
the upper outdoor heat exchanger is introduced with high-temperature refrigerant through a first defrosting passage which is selectively conducted to melt a surface frost layer; the first defrosting passage comprises a compressor discharge side, a first expansion valve, a second reversing valve, an upper outdoor heat exchanger and a bypass expansion valve which are sequentially communicated;
one path of the inlet of the lower outdoor heat exchanger is connected with the lower expansion valve, and the other path of the inlet of the lower outdoor heat exchanger is connected with the bypass expansion valve; the refrigerant discharged from the discharge side of the compressor enters the lower outdoor heat exchanger through a first direction changing valve, an indoor heat exchanger, an indoor expansion valve, and a lower expansion valve; the refrigerant discharged from the upper outdoor heat exchanger enters a lower outdoor heat exchanger through the bypass expansion valve, and the refrigerant discharged from the lower outdoor heat exchanger enters a suction side of the compressor through the third reversing valve to form a first refrigerant circuit capable of being selectively conducted; the lower outdoor heat exchanger operates as an evaporator in the first refrigerant circuit.
9. The air source heat pump system of claim 8,
the lower outdoor heat exchanger is introduced with high-temperature refrigerant through a second defrosting passage which is selectively conducted so as to melt a surface frost layer; the second defrosting passage comprises a compressor discharge side, a first expansion valve, a third reversing valve, a lower outdoor heat exchanger and a bypass expansion valve which are sequentially communicated;
one path of the inlet of the upper outdoor heat exchanger is connected with the upper expansion valve, and the other path of the inlet of the upper outdoor heat exchanger is connected with the bypass expansion valve; the refrigerant discharged from the discharge side of the compressor enters the upper outdoor heat exchanger through a first direction changing valve, an indoor heat exchanger, an indoor expansion valve, and an upper expansion valve; the refrigerant discharged from the lower outdoor heat exchanger enters an upper outdoor heat exchanger through the bypass expansion valve, and the refrigerant discharged from the upper outdoor heat exchanger enters a second refrigerant circuit which is formed on the suction side of the compressor through the second reversing valve and can be selectively conducted; the upper outdoor heat exchanger operates as an evaporator in the second refrigerant circuit.
10. The air source heat pump system according to claim 7,
the indoor heat exchanger includes at least a first indoor heat exchanger operating as a condenser and a second indoor heat exchanger operating as an evaporator;
the air-source heat pump system further comprises:
a first valve having one port connected to the first indoor heat exchanger and the other port connected to a discharge side of a compressor; and
and a second valve having one port connected to the second indoor heat exchanger and the other port connected to a suction side of the compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220082710.3U CN216814403U (en) | 2022-01-13 | 2022-01-13 | Air source heat pump system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220082710.3U CN216814403U (en) | 2022-01-13 | 2022-01-13 | Air source heat pump system |
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| CN216814403U true CN216814403U (en) | 2022-06-24 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202220082710.3U Active CN216814403U (en) | 2022-01-13 | 2022-01-13 | Air source heat pump system |
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| Country | Link |
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| CN (1) | CN216814403U (en) |
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