Patent Application
20230101537
The present disclosure relates to the heat pump and, more specifically, to heat pump that increases heating efficiency and saves energy in heating mode.
In the case of the heat pump according to the prior art, the refrigerant of the cooling operation mode is discharged from the compressor and then transferred to the outdoor heat exchanger via the four-way valve and transferred from the outdoor heat exchanger to the indoor heat exchanger through an expansion mechanism and sucked into the compressor through the accumulator.
In the heating operation mode, the refrigerant flowing into the outdoor heat exchanger is in a liquid state.
The heat required for the liquid refrigerant to evaporate into a gaseous state is obtained from outdoor air.
Therefore, when the outside temperature is low, the evaporation of the refrigerant decreases, and accordingly, the liquid component of the refrigerant flowing into the indoor heat exchanger increases, and the heating performance is greatly reduced.
When the outside air temperature is lowered to 0° C. or less, which is the freezing point of water, frost is deposited on the outdoor heat exchanger and the heating operation efficiency is greatly reduced.
To solve the above problem, the recent heat pump is designed to have a defrost mode in which the heat pump is operated in reverse from the heating mode to the cooling mode for a certain time. When it is switched to the defrost mode in this way, the frost attached to the outdoor heat exchanger can be removed.
However, in conventional heat pump, when the indoor heat exchanger is in the heating mode, heating is performed by simply circulating the refrigerant in the heat pump cycle, so that it significantly falls short of consumer's expectation for an increase in heating efficiency and saving energy.
In addition, there is also a problem that the evaporation temperature drops excessively during heating and then generates freeze.
Accordingly, there is a need for a structure capable of preventing or delaying frost occurring in the outdoor heat exchanger of the air conditioner exposed to a low temperature environment.
The problem to be solved by the present disclosure is to efficiently prevent frosting that may occur in an outdoor heat exchanger during a heating operation or to efficiently reduce the frosting generated.
The problems of the present disclosure are not limited to the problems mentioned above, and other problems that are not mentioned will be clearly understood by those who skilled in the art from the following description.
To achieve the above problem, the heat pump according to the embodiment of the present disclosure includes a first pipe in which a first refrigerant flow, a second pipe disposed at the side of the first pipe and in which a second refrigerant flow, a first heat exchanger connected with the first pipe and the second pipe and in which the first refrigerant exchange heat with the second refrigerant, a boiler connected with the first pipe and in which the first refrigerant flow, a compressor connected with the second pipe and compressing the second refrigerant, a second heat exchanger connected with the second pipe and in which the second refrigerant exchange heat with an outdoor air, a bypass pipe branched from first pipe and disposed to exchange heat with the second heat exchanger and a three-way valve for inducing the first refrigerant to pass through the bypass pipe.
Details of other embodiments are included in the detailed description and drawings.
According to this embodiment, by installing a water pipe in a position close to the second heat exchanger 120, 220 used as an evaporator during heating or by installing a refrigerant pipe immediately after emission from the condenser, and by circulating the high temperature fluid toward the evaporator, the freezing on surface of the second heat exchanger 120, 220 may be delayed.
In addition, by applying it to the boiler B communicated with the heat pump, the inflow temperature into the plate heat exchanger, which is a condenser, may be lowered and then leads to an increase in efficiency.
In addition, by lowering the inflow temperature, the operating range of the heat pump is widened so that operating cost may be reduced.
Advantages and features of the present disclosure, and a method of achieving them will become apparent with reference to the embodiments described below in detail together with the accompanying drawings. However, the present disclosure is not limited to the embodiments disclosed below but may be implemented in a variety of different forms. The present embodiments are provided to disclose completely the present disclosure and to fully inform the scope of the present disclosure to those who skilled in the art to which the present disclosure pertains. The disclosure is only defined by the scope of the claims. The same reference sign refers to the same elements throughout the whole specification.
Referring to
The first heat exchanger 110 may operate variably depending on the flow direction of the first refrigerant or the second refrigerant, which is changed by the cooling mode or heating mode of the heat pump.
Specifically, the first heat exchanger 110 may operate as the condenser condensing high-temperature, high-pressure, and gaseous refrigerant into room temperature, high-pressure, and liquid state during the heating operation of the heat pump. The first heat exchanger 110 may operate as the evaporator that evaporates low-temperature, low-pressure, liquid refrigerant into a gaseous state during cooling operation of the heat pump.
As described above, by operating the first heat exchanger in reverse to the second heat exchanger 120 depending on the circulation of the first refrigerant or the second refrigerant, air conditioning desired by the user may be achieved.
In addition, the first heat exchanger 110 may be a plate heat exchanger having refrigerants flowing independently.
The first heat exchanger 110 has the first pipe 111 and the second pipe 112 disposed at both ends so that the first refrigerant and the second refrigerant may not contact each other and may flow independently.
The flow inside the first heat exchanger 110 will be described in more detail. The first refrigerant has a single path, where the first refrigerant flow into the first pipe 111 through an inlet (not shown) formed on the left end and flow to a longitudinal direction of a plate 113 by moving to one side and emitted through the other side of the first pipe 111.
In addition, the second refrigerant flowing into the second pipe 112 through an inlet (not shown) formed on the right end has a single path, where the second refrigerant flow to the longitudinal direction (opposite to the flowing direction of the first refrigerant) of the plate 113 by moving to the one side and is emitted through an outlet (not shown) of the second pipe 112.
In addition, plate 113 may define a first flow part and a second flow part mentioned above by the bonding of a bonding part (not shown) that bonds two kinds of a first plate (not shown) and a second plate (not shown). Here, the plates 113 adjacent to each other may be bonded to each other by brazing.
A blowing fan 121 may be provided on one side of the second heat exchanger 120. The blowing fan 121 may guide the outdoor air to the second heat exchanger 120.
The air forced to flow by the blowing fan 121 exchanges heat with the second refrigerant flowing inside the second heat exchanger 120.
A boiler B is connected to the first pipe 111 and may perform the hot water supply function with a water refrigerant flowing inside the first pipe 111.
The second refrigerant may include the refrigerant R32 or R290 circulating the second heat exchanger 120 and a compressor 130.
In other words, the second refrigerant may include one or a mixed refrigerant in the group selected as difluoromethane (R32) or propane (Propane, R290), which are alternative refrigerant having the OZONE DEPLETION POTENTIAL (ODP) of 0.0.
The compressor 130 compresses the gas refrigerant having low temperature and low pressure to high temperature and high pressure and supplies it to the condenser.
In addition, the compressor 130 may be provided in plural. For example, when the compressor 130 is an inverter compressor capable of converting an operating frequency, it may include a constant speed compressor using a fixed operating frequency.
The bypass pipe 144 may be branched from the first pipe 111. The first refrigerant flow inside the bypass pipe 144.
A three-way valve 140 may include a first flow path 141, a second flow path 142 and a third flow path 143. The first flow path 141 may circulate the first refrigerant by being connected with the boiler B. The second flow path 142 may be connected to the first pipe 111. The third flow path 143 may be disposed to join to the second flow path 142 via the bypass pipe 144 exchanging heat with the second heat exchanger 120 and emitted in the direction excluding the first flow path 141 and the second flow path 142.
In the cooling mode of the heat pump, the three-way valve 140 may be controlled to close so that the first refrigerant passing through the boiler B is not supplied to the second heat exchanger 120. In the heating mode, the three-way valve 140 may be controlled to open so that the first refrigerant passing through the boiler B is supplied to the second heat exchanger 120. The operation related to this will be described later.
An accumulator 150 may be further included between the compressor 130 and the second heat exchanger 120.
In the accumulator 150, the liquid refrigerant that has not been evaporated is filtered out, and only the gaseous refrigerant is selected and then supplied to the compressor 130.
The accumulator 150 may be provided between pipes on the suction side of the compressor 130. The accumulator 150 receives the refrigerant from the first heat exchanger 110 or the second heat exchanger 120 and separates the refrigerant into a gaseous and liquid state and then supplies only a gaseous refrigerant to the compressor 130.
An expansion valve 160 may be further included between the second pipe 112 and the second heat exchanger 120.
The expansion valve 160 expands the liquid refrigerant of room temperature and high pressure that has passed through the condenser and supplies the liquid refrigerant of low temperature and low pressure to the evaporator.
As the expansion valve 160, an electric expansion valve capable of controlling an opening degree may be applied.
When the heat pump operates in the heating mode, a four-way valve 170 guides the refrigerant passing through the compressor 130 to flow into the first heat exchanger 110 and guides the refrigerant passing through the second heat exchanger 120 to flow into the accumulator 150.
Meanwhile, when the heat pump operates in the cooling mode, the four-way valve 170 guides the refrigerant passing through the compressor 130 to flow into the second heat exchanger 120 and controls the refrigerant passing through the first heat exchanger 110 to flow into the accumulator 150.
A muffler 180 may be further included between the four-way valve 170 and the compressor 130. The expansion valve 160 is generally used with a capillary tube, which does not affect the refrigeration performance, but generates noise due to a rapid change in the flow of the refrigerant.
The noise at this time includes a loud flow noise due to a complex change in phase, pressure, speed and internal energy of the refrigerant, and the muffler 180 may be included to reduce such noise.
In other words, the muffler 180 performs reducing the vibration or noise of the refrigerant emitted from the compressor 130.
Hereinafter, the operation of the heat pump according to one embodiment of the present disclosure will be described.
When the heat pump according to an embodiment of the present disclosure operates in the heating mode, the high-temperature, high-pressure refrigerant emitted from the compressor 130 by the control of the four-way valve 170 flow to the first heat exchanger 110.
Thereafter, the second refrigerant in a high-temperature and high-pressure state is condensed and liquefied during exchanging heat with the first refrigerant passing through the first heat exchanger 110.
Thereafter the second refrigerant passing through the expansion valve 160 passes through the second heat exchanger 120 in the state of a two-phase refrigerant with a high temperature and low pressure.
As a result, the second heat exchanger 120 operates as an evaporator, and the surface temperature of the second heat exchanger 120 becomes a low temperature state.
Here, since the surface temperature of the second heat exchanger 120 become lower than the external temperature, condensate is formed on the surface of the second heat exchanger 120.
In addition, when the external temperature is lower than or equal to the freezing temperature, the condensate is frozen on the surface of the second heat exchanger 120. As this state lasts for a long time, the heat exchange performance of the second heat exchanger 120 with the external air declines due to the freezing of the condensate, and finally, ice frozen on the surface must be removed by performing a defrost operation.
For this, the first refrigerant with a relatively high temperature emitted from the boiler B is bypassed to the bypass pipe 144 by the control of the three-way valve 140.
Accordingly, the ice generated on the outer surface of the second heat exchanger 120 may be melted and removed through the process of heat-exchanging of the second refrigerant with the second heat exchanger 120.
The bypass pipe 144 may be disposed as close as possible to exchange heat with the second heat exchanger 120, and its position may be variously applied depending on the design position.
Meanwhile, when the heat pump according to one embodiment of the present disclosure operates in the cooling mode, the refrigerant emitted from the compressor 130 flow to the second heat exchanger 120 in a state of high temperature and high pressure under the control of the four-way valve 170.
Thereafter, the second refrigerant in a high-temperature and high-pressure state passing through the second heat exchanger 120 is condensed and liquefied during heat exchange with external air by the blowing fan 121.
Accordingly, the first heat exchanger 110 operates as an evaporator.
The second refrigerant changed in a phase, a low-temperature and a low-pressure, in the first heat exchanger 110 passes through the muffler 180 to reduce noise and pulsation, and then flow to the compressor 130.
Referring to
The bypass pipe 244 may be branched from the first pipe 212. The second refrigerant flow inside the bypass pipe 244.
The three-way valve 240 shown in
When the heat pump of
Thereafter, the second refrigerant in a high-temperature and high-pressure state passing through the first heat exchanger 210 is condensed and liquefied during heat exchange with the first refrigerant.
Thereafter, the second refrigerant passes through the expansion valve 260 the second heat exchanger 220 in the state of a two-phase refrigerant with the high temperature and low pressure.
As a result, the second heat exchanger 220 functions as an evaporator, and the surface temperature of the second heat exchanger 220 becomes a low temperature state.
Here, since the surface temperature of the second heat exchanger 220 is lower than the external temperature, the condensate is formed on the surface.
Also, when the external temperature is lower than or equal to the freezing temperature, the condensate is frozen on the surface of the second heat exchanger 120. As this state lasts for a long time, the heat exchange performance of the second heat exchanger 120 with the external air declines due to the freezing of the condensate, and finally, ice frozen on the surface must be removed by performing a defrost operation.
For this, the second refrigerant before flowing into the expansion valve 260 installed between the first heat exchanger 210 and the second heat exchanger 220, by the control of the three-way valve 240, bypass the second heat exchanger 220 through the bypass pipe 244 without passing through the expansion valve 260.
In other words, since the temperature of the second refrigerant passing through the first heat exchanger 210 in a high-pressure state at room temperature or low temperature is higher than the temperature of the second refrigerant of the second heat exchanger 220 acting as an evaporator, ice generated on the surface of the second heat exchanger 220 may be melted and removed.
The bypass pipe 244 may be disposed as close as possible to exchange heat with the second heat exchanger 220, and its position may be variously applied depending on the design position.
Meanwhile, when the heat pump according to other embodiment of the present disclosure operates in the cooling mode, the high-temperature and high-pressure refrigerant emitted from the compressor 230 flow to the second heat exchanger 220 by the control of the four-way valve 270.
Thereafter, the second refrigerant in a high-temperature and high-pressure state passing through the second heat exchanger 220 is condensed and liquefied in the process of being heat-exchanged with external air by the blowing fan 221.
Thereafter, the second refrigerant with the high-temperature, low-pressure passing through the expansion valve 260 passes through the first heat exchanger 210 in the state of a two-phase refrigerant.
Due to this, the first heat exchanger 210 functions as an evaporator.
Like the case of
Referring to
Preferred embodiments of the present disclosure have been illustrated and described above, but the present disclosure is not limited to the specific embodiments described above. The present disclosure can be implemented in various modifications by those who skilled in the art to which the present disclosure belongs without getting out of the point of the present disclosure in the claims. These modified implementations should not be individually understood from the technical idea or perspective of the present disclosure.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10-2020-0023201 | Feb 2020 | KR | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/KR2021/002317 | 2/24/2021 | WO |
