Patent Application
20230235943
This application claims priority to Chinese Patent Application No. 202210079670.1, filed Jan. 24, 2022, and all the benefits accruing therefrom under 35 U.S.C. ยง 119, the contents of which in its entirety are herein incorporated by reference.
The present application relates to the field of air-conditioning equipment, and in particular to a heat pump system and a control method thereof.
As a highly mature device, heat pump systems are widely used in commercial buildings, household space and other places, which can provide relatively comfortable cooling/heating effect. However, engineers in this field are still working to optimize and improve various aspects, one of which is to provide directional defrosting for different locations of the components.
Defrosting mode is a common function for heat pump systems, which usually functions in winter when heat pump systems are used for heating. At this point, heat exchangers in the outdoor unit already in low temperature environment are still used to absorb heat to evaporate refrigerant in the pipes. Finned pipes on the outside surface of outdoor heat exchangers are prone to frosting in such low temperature and high humidity environments. Therefore, defrosting mode becomes an essential operation, i.e., a reversing operation is performed by switching the flow path switch valve, so that high-temperature gas-phase refrigerant discharged from the compressor flows directly into the outdoor heat exchangers and defrosts through heat dissipation of the high-temperature refrigerant.
However, defrosting mode of this type is usually performed on all pipes of a condenser. This is suitable for extremely harsh frosting environment. For normal frosting environment, however, different parts of the condenser may be more prone to frosting due to factors such as installation environment and wind direction. Of course, the aforementioned defrosting mode can still accomplish defrosting in this case. However, it can lead to interruption of the heating mode and unnecessary energy loss at the same time.
In addition, part of the heat in defrosting mode (e.g., about 25%) is lost. For example, a lot of the heat is lost in the air used in heat transfer, and a lot of the heat is lost in heating the metal components of the heat exchangers (e.g., heat-exchange copper tubes or fins).
The object of the present application is to provide a heat pump system and a control method thereof, so as to at least partially solve or alleviate the problems existing in the prior art.
To achieve at least one object of the present application, according to one aspect of the present application, a heat pump system is provided, comprising: a compressor having a suction port and an exhaust port; an indoor heat exchanger having a pipe connection configured to be disconnectable from the heat pump system; an outdoor heat exchanger configured as an interlaced heat exchanger having at least two refrigerant flow paths; a plurality of throttling elements respectively arranged between any two of the indoor heat exchanger and the at least two refrigerant flow paths of the outdoor heat exchanger; and a first type four-way valve and a second type four-way valve, with ports thereof respectively connected to the suction port and the exhaust port of the compressor and one of the at least two refrigerant flow paths of the outdoor heat exchanger; wherein, an unconnected port of the first type four-way valve is connected to the indoor heat exchanger, and an unconnected port of the second type four-way valve is connected to the port connected to the suction port through a capillary or an on-off valve. Wherein, in a local defrosting mode, refrigerant flows sequentially from the exhaust port of the compressor through at least one of the at least two refrigerant flow paths of the outdoor heat exchanger, the throttling element, at least another one of the at least two refrigerant flow paths of the outdoor heat exchanger and the suction port of the compressor.
In addition to one or more of the above features, or as an alternative, in another embodiment, the plurality of throttling element comprise a first throttling element and a second throttling element; a three-way intersection point is provided on connecting lines between the indoor heat exchanger and the two refrigerant flow paths of the outdoor heat exchanger. Wherein, the first throttling element is arranged on a first connecting line between the three-way intersection point and one of the at least two refrigerant flow paths of the outdoor heat exchanger or the indoor heat exchanger; the second throttling element is arranged on a second connecting line between the three-way intersection point and another one of the at least two refrigerant flow paths of the outdoor heat exchanger or the indoor heat exchanger.
In addition to one or more of the above features, or as an alternative, in another embodiment, the first throttling element is arranged on the first connecting line between the three-way intersection point and one of the at least two refrigerant flow paths of the outdoor heat exchanger; the second throttling element is arranged on the second connecting line between the three-way intersection point and another one of the at least two refrigerant flow paths of the outdoor heat exchanger.
In addition to one or more of the above features, or as an alternative, in another embodiment, the plurality of throttling element further comprise a first valve at least capable of controlling on-off of the flow path; wherein, the first valve is arranged on a third connecting line between the three-way intersection point and the indoor heat exchanger.
In addition to one or more of the above features, or as an alternative, in another embodiment, the first valve is configured as a third throttling element or a first solenoid valve.
In addition to one or more of the above features, or as an alternative, in another embodiment, when the first valve is configured as a third throttling element, in a local defrosting mode, refrigerant flows through two of the first throttling element, the second throttling element, and the third throttling element.
In addition to one or more of the above features, or as an alternative, in another embodiment, wherein, in a first local defrosting mode, refrigerant flows sequentially from the exhaust port of the compressor through at least a first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, the throttling element, at least a second flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor. Or, in a second local defrosting mode, refrigerant flows sequentially from the exhaust port of the compressor through at least the second flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, the throttling element, at least the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor. Or, in a combined defrosting mode, refrigerant flows sequentially from the exhaust port of the compressor through at least the second flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, the throttling element, at least the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor; and at the same time, refrigerant flows sequentially from the exhaust port of the compressor through the indoor heat exchanger, the throttling element, at least the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor.
In addition to one or more of the above features, or as an alternative, in another embodiment, the outdoor heat exchanger is configured to comprise a plurality of refrigerant flow paths, and a plurality of the first type four-way valves and/or the second type four-way valves are provided. Wherein, each of the first type four-way valves and/or each of the second type four-way valves connect to a refrigerant flow path respectively. Wherein, in a local defrosting mode, refrigerant flows sequentially from the exhaust port of the compressor through a part of the plurality of refrigerant flow paths of the outdoor heat exchanger connected to the first type four-way valve or the second type four-way valve, the throttling element, another part of the plurality of refrigerant flow paths of the outdoor heat exchanger connected to the second type four-way valve or the first type four-way valve, and the suction port of the compressor.
To achieve at least one object of the present application, according to one aspect of the present application, a control method for the aforementioned heat pump system is provided, comprising: a first local defrosting mode, in which pipe connections between the first type four-way valve and the second type four-way valve are switched over, so that the exhaust port of the compressor is connected with at least the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger through a capillary or an on-off valve, at least the second flow path of the at least two refrigerant flow paths of the outdoor heat exchanger is connected with the suction port of the compressor, and the pipe connection of the indoor heat exchanger in the heat pump system is disconnected; wherein, refrigerant flows sequentially from the exhaust port of the compressor through the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, the throttling element, the second flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor; and/or a second local defrosting mode, in which pipe connections between the first type four-way valve and the second type four-way valve are switched over, so that the exhaust port of the compressor is connected with at least the second flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, at least the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger is connected with the suction port of the compressor, and the pipe connection of the indoor heat exchanger is disconnected at the same time; wherein, refrigerant flows sequentially from the exhaust port of the compressor through the second flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, the throttling element, the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor; and/or a combined defrosting mode, in which pipe connections between the first type four-way valve and the second type four-way valve are switched over, so that the exhaust port of the compressor is respectively connected with at least the second flow path of the at least two refrigerant flow paths of the outdoor heat exchanger and the indoor heat exchanger, and at least the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger is connected with the suction port of the compressor; wherein, refrigerant flows sequentially from the exhaust port of the compressor through the second flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, the throttling element, the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor; and at the same time, refrigerant flows sequentially from the exhaust port of the compressor through the indoor heat exchanger, the throttling element, at least the first flow path of the at least two refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor.
In addition to one or more of the above features, or as an alternative, in another embodiment, the control method further comprises: a cooling mode or an overall defrosting mode, in which pipe connections between the first type four-way valve and the second type four-way valve are switched over, so that the exhaust port of the compressor is respectively connected with all refrigerant flow paths of the outdoor heat exchanger, and the indoor heat exchanger is connected with the suction port of the compressor; wherein, refrigerant flows sequentially from the exhaust port of the compressor through all refrigerant flow paths of the outdoor heat exchanger, the throttling element, the indoor heat exchanger, and the suction port of the compressor.
In addition to one or more of the above features, or as an alternative, in another embodiment, the control method further comprises: a heating mode, in which pipe connections between the first type four-way valve and the second type four-way valve are switched over, so that the exhaust port of the compressor is connected with the indoor heat exchanger, and all refrigerant flow paths of the outdoor heat exchanger are connected with the suction port of the compressor; wherein, refrigerant flows sequentially from the exhaust port of the compressor through the indoor heat exchanger, the throttling element, all refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor.
In addition to one or more of the above features, or as an alternative, in another embodiment, the heat pump system comprises a three-way intersection point on the connecting lines between the indoor heat exchanger and the two refrigerant flow paths of the outdoor heat exchanger, and the heat pump system further comprises a third throttling element or a first solenoid valve capable of controlling the on-off of the flow path, wherein the third throttling element or the first solenoid valve is arranged on a third connecting line between the three-way intersection point and the indoor heat exchanger. Wherein, in a second local defrosting mode, the first solenoid valve is closed and periodically opened; or the third throttling element maintains a minimum opening or is periodically opened.
The heat pump system according to the present application, by using an interlaced heat exchanger having at least two refrigerant flow paths as an outdoor heat exchanger and conducting at least one of the refrigerant flow paths, makes it possible for the heat pump system to achieve local defrosting. In addition, through the flow path design of the system, the heating mode can still be maintained in operation at least when the heat pump system is in the local defrosting mode, thus avoiding frequent interruptions of heating mode and improving the user experience. Furthermore, due to the structural characteristics of the interlaced heat exchanger, the heat losing in the heat transfer air media and heat transfer metal components can be reduced, thus improving the heat utilization efficiency in the defrosting mode. And, coupled with the corresponding control method, the heat pump system can carry out various local defrosting modes. As a result, pointing defrosting can be performed on some heat exchangers with more severe frosting in outdoor units, which also reduces energy loss.
The present application will be described in detail hereinafter with reference to the exemplary embodiments shown in the accompanying drawings. However, it should be understood that the present application can be implemented in many different forms, and should not be construed as being limited to the embodiments set forth herein. These embodiments are provided here for the purpose of making the disclosure of the present application more complete and comprehensive, and fully conveying the concept of the present application to those skilled in the art.
With reference to
With continued reference to
In addition, to achieve the switching function of the heat pump system 100 between various operating modes, a corresponding flow path switching valve assembly shall also be provided. The flow path switching valve assembly in this embodiment is a first type four-way valve 151 and a second type four-way valve 152. The three ports of the first type four-way valve 151 are respectively connected to the suction port 110a and the exhaust port 110b of the compressor 110, and the first refrigerant flow path 130a of the outdoor heat exchanger 130. The three ports of the second type four-way valve 152 are respectively connected to the suction port 110a and the exhaust port 110b of the compressor 110, and the second refrigerant flow path 130b of the outdoor heat exchanger 130. The unconnected port of the first type four-way valve 151 (the leftmost port of the first type four-way valve 151 in
Wherein, the aforementioned interlaced heat exchanger is a mature heat exchanger in the field, which usually has at least two refrigerant inlets and at least two refrigerant outlets corresponding to each other. A plurality of refrigerant branches may be provided between each set of refrigerant inlet and outlet. These refrigerant branches between the same set of refrigerant inlet and outlet jointly constitute a set of refrigerant flow paths mentioned herein. The interlaced heat exchanger is characterized in that the refrigerant branches in different refrigerant flow paths can be arranged in an interlaced manner. Taking an interlaced heat exchanger with two refrigerant flow paths as an example, several refrigerant branches in the first refrigerant flow path can be arranged close to each other, while the other refrigerant branches thereof can be arranged close to several refrigerant branches in the second refrigerant flow path, so that the refrigerant in the two refrigerant flow paths can exchange heat sufficiently.
At this point, in a local defrosting mode, the heat pump system can drive the refrigerant to flow sequentially from the exhaust port of the compressor through at least one of the at least two refrigerant flow paths of the outdoor heat exchanger, the throttling element, at least another of the at least two refrigerant flow paths of the outdoor heat exchanger, and the suction port of the compressor.
The heat pump system according to the present application, by using an interlaced heat exchanger with at least two refrigerant flow paths as an outdoor heat exchanger and selectively conducting at least one of the refrigerant flow paths, makes it possible for the heat pump system to achieve local defrosting. In addition, through the flow path design of the system, the heating mode can still be maintained in operation at least when the heat pump system is in the local defrosting mode, thus avoiding frequent interruptions of the heating mode and improving the user experience. Furthermore, due to the structural characteristics of the interlaced heat exchanger, the heat losing in the heat transfer air media and heat transfer metal components can be reduced, thus improving the heat utilization efficiency in the local defrosting mode. It is also possible to perform pointing defrosting operations on some heat exchangers with more severe frosting in outdoor units, which also reduces energy loss. And, this flow path arrangement makes local defrosting mode possible with fewer valves, and at the same time maintains the indoor heating mode in operation in the local defrosting mode, which fully considers the cost-performance balance of the system.
Various possible modifications of the heat pump system are described below in conjunction with the accompanying drawings. In addition, additional components may be added for further improvement of the energy efficiency or reliability of the system, which are also exemplified below.
For example, in conjunction with
As another example, throttling element are arranged so that the refrigerant need to flow between two heat exchangers or two parts of the heat exchanger can undergo expansion throttling, thus achieving the functions of condensation and heat dissipation and evaporation and heat absorption before and after the expansion throttling, respectively. To this end, one or more throttling element may be provided in the flow path to achieve this purpose.
With reference to
In addition, when one of the three throttling element is used only for conducting the flow path, the valve can also be selected to be a first solenoid valve. For example, under such an arrangement, the third throttling element 143 may be arranged as a first solenoid valve. At this point, the first throttling element 141 and the second throttling element 142 must be arranged on the other two connecting lines in the heat pump system accordingly, so as to ensure that the refrigerant can be throttled at least once when flowing between any two heat exchangers in each mode.
As a matter of fact, in accordance with the purpose of arranging the throttling element mentioned above, when any one of the first throttling element 141, the second throttling element 142 and the third throttling element 143 with the aforementioned positions is replaced by a solenoid valve in the system, a throttling element can still be present between any two heat exchangers or two parts of the heat exchanger. That is, the aforementioned heat pump system can also have a usual throttling process in various modes.
The control method for the heat pump system 100 will be described below in conjunction with
Referring to
At this point, the refrigerant undergoes gas-phase compression by the compressor 110, flows sequentially from the exhaust port 110b of the compressor 110 through the first type four-way valve 151 to the first refrigerant flow path 130a of the outdoor heat exchanger 130 for condensation and heat dissipation, thus defrosting the refrigerant flow path pipes accordingly. After that, the refrigerant is throttled by one or both of the first throttling element 141 and the second throttling element 142, flows through the second refrigerant flow path 130b of the outdoor heat exchanger 130 for evaporation and heat absorption, and then returns to the suction port 110a of the compressor 110 through the second type four-way valve 152, thus completing the cycle.
Referring to
At this point, after undergoing gas-phase compression by the compressor 110, a portion of refrigerant flows from the exhaust port 110b of the compressor 110 through the second type four-way valve 152 to the second refrigerant flow path 130b of the outdoor heat exchanger 130 for condensation and heat dissipation, thus defrosting the refrigerant flow path pipes accordingly. After that, this portion of refrigerant passes through the fully open second throttling element 142, flows through the first throttling element 141 for throttling and then through the first refrigerant flow path 130a of the outdoor heat exchanger 130 for evaporation and heat absorption, and finally returns to the suction port 110a of the compressor 110 through the first type four-way valve 151, thus completing the cycle of this portion of refrigerant. At the same time, another portion of the compressed refrigerant flows from the exhaust port 110b of the compressor 110 through the first type four-way valve 151 to the indoor heat exchanger 120 for condensation and heat dissipation, thus providing heating for indoors accordingly. After that, this portion of refrigerant passes through the fully open third throttling element 143, flows through the first throttling element 141 for throttling and then through the first refrigerant flow path 130a of the outdoor heat exchanger 130 for evaporation and heat absorption, and finally returns to the suction port 110a of the compressor 110 through the first type four-way valve 151, thus completing the cycle of this portion of refrigerant.
Furthermore, although not shown in the figure, it is also possible to perform only the defrosting function of the combined defrosting mode shown in
At this point, after undergoing gas-phase compression by the compressor 110, the refrigerant flows from the exhaust port 110b of the compressor 110 through the second type four-way valve 152 to the second refrigerant flow path 130b of the outdoor heat exchanger 130 for condensation and heat dissipation, thus defrosting the refrigerant flow path pipes accordingly. After that, the refrigerant passes through the fully open second throttling element 142, flows through the first throttling element 141 for throttling, and then through the first refrigerant flow path 130a of the outdoor heat exchanger 130 for evaporation and heat absorption, and finally returns to the suction port 110a of the compressor 110 through the first type four-way valve 151, thus completing the refrigerant cycle.
In the second local defrosting mode, when it is necessary to disconnect the pipe connection of the indoor heat exchanger, if the above third throttling element 143 is taken as an example, the third throttling element may be kept at a minimum opening or kept periodically open for reliability reasons; if the first solenoid valve is taken as an example, it can be closed directly and opened on periodically. This realizes another local pointing defrosting mode without taking heat from indoors. Although the heating mode of the indoor heat exchanger is no longer in operation at this time, the indoor comfort can be improved to some extent as compared with the conventional defrosting mode which takes heat from indoors.
Under the above system arrangement, no matter the first local defrosting mode, the second local defrosting mode or the combined defrosting mode, local pointing defrosting can all be achieved without taking heat from indoors, which is advantageous in improving indoor comfort than the conventional defrosting mode which takes heat from indoors. In addition, in the combined defrosting mode, the heating operation of indoor heat exchanger can be maintained while performing defrosting. The flow path arrangement of the system is relatively simple, no additional valves are needed to control the on-off and change of direction of the flow path, and the control logic is simple, so it has good applicability in low-cost occasions.
Of course, the heat pump system can also achieve the conventional cooling mode, heating mode and overall defrosting mode (i.e., to reverse operating the cooling mode in the heating mode), which will be exemplified below in conjunction with
Referring to
At this point, after undergoing gas-phase compression by the compressor 110, a portion of refrigerant flows from the exhaust port 110b of the compressor 110 through the first type four-way valve 151 to the first refrigerant flow path 130a of the outdoor heat exchanger 130 for condensation and heat dissipation (or in the overall defrosting mode, defrosts the refrigerant flow path pipes accordingly). After that, this portion of refrigerant is throttled by one or both of the first throttling element 141 and the third throttling element 143, flows through the indoor heat exchanger 120 for evaporation and heat absorption and provides cooling for indoors accordingly, and then returns to the suction port 110a of the compressor 110 through the first type four-way valve 151, thus completing the cycle of this portion of refrigerant. At the same time, the other portion of the refrigerant flows from the exhaust port 110b of the compressor 110 through the second type four-way valve 152 to the second refrigerant flow path 130b of the outdoor heat exchanger 130 (or in the overall defrosting mode, defrosts the refrigerant flow path pipes accordingly). After that, this portion of refrigerant is throttled by one or both of the second throttling element 142 and the third throttling element 143, flows through the indoor heat exchanger 120 for evaporation and heat absorption and provides cooling for indoors accordingly, and then returns to the suction port 110a of the compressor 110 through the first type four-way valve 151, thereby completing the cycle of this portion of refrigerant.
Referring to
At this point, after undergoing gas-phase compression by the compressor 110, the refrigerant flows from the exhaust port 110b of the compressor 110 through the first type four-way valve 151 to the indoor heat exchanger 120 for condensation and heat dissipation. After that, a portion of the refrigerant is throttled by one or both of the third throttling element 143 and the first throttling element 141, flows through the first refrigerant flow path 130a of the outdoor heat exchanger 130 for evaporation and heat absorption, and then returns to the suction port 110a of the compressor 110 through the second type four-way valve 152, thereby completing the cycle of this portion of refrigerant. At the same time, the other portion of the refrigerant is throttled by one or both of the third throttling element 143 and the second throttling element 142, flows through the second refrigerant flow path 130b of the outdoor heat exchanger 130 for evaporation and heat absorption, and then returns to the suction port 110a of the compressor 110 through the first type four-way valve 151, thereby completing the cycle of this portion of refrigerant.
It should be appreciated that although the embodiments of the control method for the heat pump system is described in a certain order, these steps are not necessarily performed in the order described. Unless explicitly stated herein, there is no strict restriction in terms of the order of carrying out these steps. Instead, these steps can be carried out in other order. In addition, at least one part of the steps of the method may include multiple sub-steps or stages, which may not necessarily be executed at the same time but may be executed at different times, and may not necessarily be executed sequentially but may be executed in turn or alternately with at least one part of the sub-steps or stages of other steps or stages.
The above examples mainly illustrate a heat pump system and a control method thereof according to the present invention. Although only some of the embodiments of the present invention are described, those skilled in the art should understand that the present invention can, without departing from the spirit and scope of the present invention, be implemented in many other forms. Therefore, the illustrated examples and embodiments are to be considered as illustrative but not restrictive, and the present invention may cover various modifications or replacements if not departed from the spirit and scope of the present invention as defined by the appended claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 202210079670.1 | Jan 2022 | CN | national |
