US20150159935A1

US20150159935A1 - Apparatus with dehumidification and defrosting abilities and controlling method thereof

Info

Publication number: US20150159935A1
Application number: US14/220,831
Authority: US
Inventors: Chung-Szu Wei; Jane-Sunn Liaw; Shih-Pei Lin; Min-Sheng Liu
Original assignee: Industrial Technology Research Institute ITRI
Current assignee: Industrial Technology Research Institute ITRI
Priority date: 2013-12-06
Filing date: 2014-03-20
Publication date: 2015-06-11
Also published as: TW201522873A; TWI539120B; CN104697253A

Abstract

An apparatus with dehumidification and defrosting abilities comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, a four-way valve and a means for refrigerant flow controlling. The compressor is coupled to the four-way valve. The four-way valve is coupled to the outdoor heat exchanger. The indoor heat exchanger is coupled to the four-way valve. The means for refrigerant flow controlling is respectively coupled to the indoor heat exchanger, the outdoor heat exchanger and the four way valve, to control mixing a low-temperature refrigerant and a high-temperature before flowing into the indoor heat exchanger, or to control mixing a low-temperature refrigerant and a high-temperature refrigerant before flowing into the compressor, or control mixing a low-temperature refrigerant and a high-temperature refrigerant before flowing into the outdoor heat exchanger.

Description

CROSS REFERENCE TO RELATED APPLICATION

This application also claims priority to Taiwan Patent Application No. 102144882 filed in the Taiwan Patent Office on Dec. 6, 2013, the entire content of which is incorporated herein by reference.

TECHNICAL FIELD

The present disclosure relates to an apparatus with dehumidification and defrosting abilities and controlling method thereof, and more particularly, to an apparatus and controlling method thereof capable of effectively performing a dehumidification process without causing temperature to rise, or effectively performing a defrosting process without causing temperature to drop.

BACKGROUND

An air conditioner that is a common appliance of our daily life is designed to change the air temperature and humidity within an area for cooling and heating or even defrosting depending on the air properties at a given time. It is noted that the operation of a conventional air conditioning system is typically done using a simple refrigeration cycle of refrigerant.
However, most refrigeration cycles of refrigerant are simple expansion circuits and thereby, while being used for indoor dehumidification, it can cause discomfort to people in the indoor environment since the indoor temperature can be fluctuated due to the dehumidification operation. On the other hand, while being used for defrosting, a problem of incomplete defrosting or insufficient heating can be induced
Therefore, it is in need of an improved refrigeration cycle of refrigerant that can be used for providing cool air at a constant temperature while being used in a dehumidification operation, or for providing sufficient heating in a defrosting operation for avoiding the problem of incomplete defrosting.

SUMMARY

The present disclosure provides an apparatus with dehumidification and defrosting abilities, comprising: a compressor, an indoor heat exchanger, an outdoor heat exchanger, a four-way valve and a means for refrigerant flow controlling. The compressor is coupled to the four-way valve. The four-way valve is coupled to the outdoor heat exchanger. The indoor heat exchanger is coupled to the four-way valve. The means for refrigerant flow controlling is respectively coupled to the indoor heat exchanger, the outdoor heat exchanger and the four way valve, to control the mixing of a low-temperature refrigerant and a high-temperature before flowing into the indoor heat exchanger, or to control the mixing of a low-temperature refrigerant and a high-temperature refrigerant before flowing into the compressor, or to control the mixing of a low-temperature refrigerant and a high-temperature refrigerant before flowing into the outdoor heat exchanger.
The present disclosure provide a dehumidification control method, comprising the steps of: enabling a low-temperature refrigerant to mix with a high-temperature refrigerant so as to form a middle temperature refrigerant when an indoor temperature is larger than a first temperature, while enabling the middle temperature refrigerant to flow into an indoor heat exchanger.
The present disclosure provide a defrosting control method, comprising the steps of: enabling a low-temperature refrigerant to mix with a high-temperature refrigerant so as to form a middle temperature refrigerant when an indoor temperature is smaller than a second temperature, while enabling the middle temperature refrigerant to flow into an outdoor heat exchanger.
Further scope of applicabilities of the present application will become more apparent from the detailed description given hereinafter. However, it should be understood that the detailed description and specific examples, while indicating exemplary embodiments of the disclosure, are given by way of illustration only, since various changes and modifications within the spirit and scope of the disclosure will become apparent to those skilled in the art from this detailed description.

BRIEF DESCRIPTION OF THE DRAWINGS

The present disclosure will become more fully understood from the detailed description given herein below and the accompanying drawings which are given by way of illustration only, and thus are not limitative of the present disclosure and wherein:

FIG. 1 is a schematic diagram showing an apparatus with dehumidification and defrosting abilities that is operating in a cooling operation mode according to a first embodiment of the present disclosure.

FIG. 2 is a schematic diagram showing an apparatus with dehumidification and defrosting abilities that is operating in a heating operation mode according to the first embodiment of the present disclosure.

FIG. 3 is a schematic diagram showing an apparatus with dehumidification and defrosting abilities that is operating in a cooling operation mode according to a second embodiment of the present disclosure.

FIG. 4 is a schematic diagram showing an apparatus with dehumidification and defrosting abilities that is operating in a heating operation mode according to the second embodiment of the present disclosure.

FIG. 5 is a comparison diagram showing the varying of outdoor temperature with time when an apparatus with dehumidification and defrosting abilities of the present disclosure is enabled to operate in a heating operation mode.

FIG. 6 is a comparison diagram showing the varying of indoor temperature with time when an apparatus with dehumidification and defrosting abilities of the present disclosure is enabled to operate in a cooling operation mode.

DETAILED DESCRIPTION

In the following detailed description, for purposes of explanation, numerous specific details are set forth in order to provide a thorough understanding of the disclosed embodiments. It will be apparent, however, that one or more embodiments may be practiced without these specific details. In other instances, well-known structures and devices are schematically shown in order to simplify the drawing.
Please refer to FIG. 1, which is a schematic diagram showing an apparatus with dehumidification and defrosting abilities that is operating in a cooling operation mode according to a first embodiment of the present disclosure. In FIG. 1, an apparatus with dehumidification and defrosting abilities comprises: a compressor 10, a four-way valve 11, an indoor heat exchanger 12, a means for refrigerant flow controlling 13, an outdoor heat exchanger 14, a first sensor 15, a second sensor 16, an outdoor temperature sensor 17, an indoor temperature sensor 18, a first pipe 20, a second pipe 21, a third pipe 22, a fourth pipe 23, a fifth pipe 24, a sixth pipe 25, a seventh pipe 26 and an eighth pipe 27.
Wherein, the compressor 10 is coupled to the four-way valve 11 via the fourth pipe 23; the four-way valve 11 is coupled to the outdoor heat exchanger 14 via the fifth pipe 24, whereas the outdoor heat exchanger 14 can be a condensation evaporator or an evaporator; the outdoor heat exchanger 14 is coupled to the means for refrigerant flow controlling 13 via the sixth pipe 25, whereas the means for refrigerant flow controlling 13 is configured with a first expansion valve 130, a second expansion valve 131 and a third expansion valve 132, and the sixth pipe 25 is arranged coupling respectively to the first expansion valve 130 and the second expansion valve 131 while allowing the second sensor 16 to be disposed at a position between the sixth pipe 25 and the second expansion valve 131.
In addition, the means for refrigerant flow controlling 13 is coupled to the indoor heat exchanger 12 via the first pipe 20. In detail, the second expansion valve 131 and the third expansion valve are arranged coupling to the indoor heat exchanger 12 via the first pipe 20, whereas the indoor heat exchanger 12 can be a condenser or an evaporator. In a condition when an evaporator is adopted to be the indoor heat exchanger 12, the outdoor heat exchanger 14 will be a condenser. On the other hand, when a condenser is adopted to be the indoor heat exchanger 12, the outdoor heat exchanger 14 will be an evaporator.
In FIG. 1, the third expansion valve 132 is coupled to the fifth pipe 24 via the eighth pipe 27, while allowing the eighth pipe 27 to be arranged winding around the periphery of the compressor 10. Moreover, the first sensor 15 is disposed at a position between the first pipe 20 and the second expansion valve 131; the indoor heat exchanger 12 is coupled to the four-way valve 11 via the second pipe 21, and the four-way valve 11 is further coupled to the compressor 10 via the third pipe 22; the outdoor temperature sensor 17 is arranged in the outdoor heat exchanger 14, while the indoor temperature sensor 18 is arranged in the indoor heat exchanger 12.
As shown in FIG. 1, the apparatus with dehumidification and defrosting abilities is operating in a cooling operation mode, by that a refrigerant that being is compressed by the compressor 10 and then forced to flow through the four-way valve 11 and the fifth pipe 24 and then into the outdoor heat exchanger 14 is transformed into a high-temperature high-pressure refrigerant.
Thereafter, the heat of the high-temperature high-pressure refrigerant is dissipated in the outdoor heat exchanger 14 for transforming the same into a low-temperature refrigerant, while enabling the low-temperature refrigerant to flow respectively into the first expansion valve 130 and the second expansion valve 131 via the sixth pipe 25, whereas the low-temperature refrigerant is a low-temperature high-pressure refrigerant.
The low-temperature refrigerant will expand inside the second expansion valve 131 so as to be transformed into a low-temperature low-pressure refrigerant. Thereafter, the low-temperature low-pressure refrigerant is enabled to flow into the indoor heat exchanger 12 via the first pipe 20 for absorbing heat, by that an air flow can be cooled and then flow into an indoor environment while the low-temperature low-pressure refrigerant after absorbing heat is transformed into a high-temperature low-pressure refrigerant.
Thereafter, the high-temperature low-pressure refrigerant is guided to flow into the four-way valve 11 via the second pipe 21, and then into the compressor 10 via the third pipe 22 where it is to be compressed and transformed into a high-temperature high-pressure refrigerant.
When the apparatus of the present disclosure is operating in an unbalance status due to load variation or changing outdoor environment, the abovementioned first expansion valve 130 will be opened for allowing the low-temperature high-pressure refrigerant to expand and transform into a low-temperature low-pressure refrigerant and then enabling the low-temperature low-pressure refrigerant to flow into through the seventh pipe 26 into the second pipe 21 where it is to be mixed with the high-temperature low-pressure refrigerant from the indoor heat exchanger 12 so as to form a middle-temperature low-pressure refrigerant. Thereafter, the middle-temperature low-pressure refrigerant is enabled to flow into the four-way valve 11 and then into the compressor 10 via the third pipe 22 so as to be compressed. Consequently, by the mixing of the two refrigerants of different temperatures and pressures, the apparatus of the present disclosure is operating in a balance status. It is noted that the low pressure achieved in the middle-temperature low-pressure refrigerant is higher than the low pressure achieved in the high-temperature low-pressure refrigerant, and the state of balance in the apparatus of the present disclosure is determined by the opening of the first expansion valve 130, i.e. the larger the opening of the first expansion valve 130 is, the higher balance level will be achieved, and vice versa.
When a dehumidification process is enabled in respond to the cooperative detection of the second sensor 16 and the indoor temperature sensor 18, the third expansion valve 132 is opened for allowing a refrigerant to flow through the eighth pipe 27 into the fifth pipe 24 while enabling the refrigerant inside the eighth pipe 27 to be compressed by the compressor 10 for raising the temperature thereof to a specific temperature so as to transform the refrigerant into a high-temperature high-pressure refrigerant, and thereafter the high-temperature high-pressure refrigerant is enabled to flow into the third expansion valve 132 for allowing high-temperature high-pressure refrigerant to expand and transform into a high-temperature low-pressure refrigerant. It is noted that the temperature of the high-temperature high-pressure refrigerant that is flowing inside the eighth pipe 27 is higher than the temperature of the high-temperature high-pressure refrigerant that is already flowing inside the fifth pipe 24. The high-temperature low-pressure refrigerant is enabled to flow into the first pipe 20 where it is to be mixed with the low-temperature low-pressure refrigerant from the second expansion valve 131 so as to form a middle-temperature low-pressure refrigerant, and then the middle-temperature low-pressure refrigerant is enabled to flow into the indoor heat exchanger 12 to be used in a heat exchange process for enable the indoor temperature to maintain stable and also simultaneously dehumidifying the indoor environment. It is noted that the pressure of the low-temperature low-pressure refrigerant from the third expansion valve 132 is higher than the pressure of the low-temperature low-pressure refrigerant from the second expansion valve 131, and the state of dehumidification capable of being achieved by the apparatus of the present disclosure is determined by the opening of the third expansion valve 132, i.e. the larger the opening of the third expansion valve 132 is, the higher the dehumidification capability will be achieved, and vice versa.
Please refer to FIG. 2, which is a schematic diagram showing an apparatus with dehumidification and defrosting abilities that is operating in a heating operation mode according to the first embodiment of the present disclosure. While operating in a heating operation mode, a high-temperature high-pressure refrigerant will be ejected from the compressor 10 which is then being enabled to flow into the four-way valve 11 through the fourth pipe 23, and then into the indoor heat exchanger 12 via the second pipe 21 for dissipating heat into an indoor environment. Thus, after heat dissipating, the high-temperature high-pressure refrigerant will be transformed into a low-temperature high-pressure refrigerant.
Thereafter, the low-temperature high-pressure refrigerant is enabled to flow through the first pipe 20 into the second expansion valve 131 and the third expansion valve 132. The low-temperature high-pressure refrigerant that is flowing into the second expansion valve 131 is expanded into a low-temperature low-pressure refrigerant while allowing the low-temperature low-pressure refrigerant to flow through the sixth pipe 25 into the outdoor heat exchanger 14 to be used in a heat absorbing process, and thus the low-temperature low-pressure refrigerant is transformed into a high-temperature low-pressure refrigerant. Then, the high-temperature low-pressure refrigerant is enabled to flow through the fifth pipe 24 into the four-way valve 11 where it is enabled to flow into the compressor 10 via the third pipe 22 where it is compressed into a high-temperature high-pressure refrigerant.
For achieving a balance state in the apparatus of the present invention, the third expansion valve 132 will be opened for allowing the low-temperature high-pressure refrigerant from the first pipe 20 to flow into the third expansion valve 132 where it is expanded into a low-temperature low-pressure refrigerant. It is noted that the pressure of the low-temperature low-pressure refrigerant from the third expansion valve 132 is higher than the pressure of the low-temperature low-pressure refrigerant from the first expansion valve 131.
The low-temperature low-pressure refrigerant from the third expansion valve 132 is then being enabled to flow through the eighth pipe 27 into the fifth pipe 24. It is noted that the temperature of the low-temperature low-pressure refrigerant from the third expansion valve 32 that is flowing inside the eighth pipe 27 will be raised to a specific temperature by the compressor 10 so as to form a high-temperature low-pressure refrigerant, and the temperature of such high-temperature low-pressure refrigerant is lower than the temperature of the high-temperature low-pressure refrigerant flowing inside the fifth pipe 24.
Since the outdoor heat exchanger 14 is more than likely being cold, the low-temperature low-pressure refrigerant that is enabled to flow into the outdoor heat exchanger 14 will not be able to absorb heat and transform into a high-temperature low-pressure refrigerant, but instead, it will be induced to dissipate heat for enabling the temperature thereof to drop even more. Consequently, a harmful liquid hammer effect could be induced if such low-temperature low-pressure refrigerant that had been cooled by the frosted outdoor heat exchanger 14 is guided to flow directly into the compressor 10.
Therefore, such low-temperature low-pressure refrigerant that had been cooled by the frosted outdoor heat exchanger 14 is enabled to mixed with the high-temperature low-pressure refrigerant from the eighth pipe 27 so as to form a middle-temperature refrigerant, whereas the pressure of the high-temperature low-pressure refrigerant is higher than the pressure of the middle-temperature low-pressure refrigerant. Thereafter the middle-temperature low-pressure refrigerant is enabled to flow through the four-way valve 11 and the third pipe 22 into the compressor 10, so that the harmful liquid hammer effect could be avoided while allowing a balance state to be achieved in the apparatus of the present disclosure.
The degree of opening of the third expansion valve 132 determines the degree of balance that can be achieved in the apparatus of the present disclosure. That is, the larger the degree of balance that can be achieved in the apparatus of the present disclosure, the larger the opening of the third expansion valve 132 should be, and vice versa.
Operationally, when a defrosting process is enabled in respond to the cooperative detection of the first sensor 15 and the outdoor temperature sensor 17, the first expansion valve 130 will be opened for allowing the high-temperature high-pressure refrigerant in the second pipe 21 to flow through the seventh pipe 26 into the first expansion valve 130 while enabling the refrigerant inside the seventh pipe 26 to expand so as to be transformed into a high-temperature low-pressure refrigerant.
Thereafter, the high-temperature low-pressure refrigerant is enabled to flow into the sixth pipe 25 for allowing high-temperature low-pressure refrigerant to mix with the low-temperature low-pressure refrigerant from the second expansion valve 131 so as to form a middle-temperature low-pressure refrigerant. Then, the middle-temperature low-pressure refrigerant is enabled to flow into the outdoor heat exchanger to be used for absorbing heat in the defrosting process and thereby be transformed into a high-temperature low-pressure refrigerant. It is noted that the temperature of the high-temperature low-pressure refrigerant from the first expansion valve 130 is higher than the temperature of the high-temperature low-pressure refrigerant flowing inside the outdoor heat exchanger 14. However, in a condition when the aforesaid high-temperature low-pressure refrigerant can not be achieved, the low-temperature low-pressure refrigerant from the outdoor heat exchanger 14 will be mixed with the high-temperature refrigerant from the eighth pipe 24 inside the fifth pipe 24 so as to form a middle-temperature low-pressure refrigerant. As described in the abovementioned heating operation mode, the high-temperature refrigerant or the middle-temperature refrigerant is enabled to flow into the four-way valve 11 via the fifth pipe 24 and then to flow into the compressor 10 via the third pipe 22.
Please refer to FIG. 3, which is a schematic diagram showing an apparatus with dehumidification and defrosting abilities that is operating in a cooling operation mode according to a second embodiment of the present disclosure. In this embodiment, the apparatus comprises: a compressor 10, a four-way valve 11, an indoor heat exchanger 12, a means for refrigerant flow controlling 13, an outdoor heat exchanger 14, a first sensor 15, a second sensor 16, an outdoor temperature sensor 17, an indoor temperature sensor 18, a first pipe 20, a second pipe 21, a third pipe 22, a fourth pipe 23, a fifth pipe 24, a sixth pipe 26, a seventh pipe 27 and an eighth pipe 27, which are arranged and numbered similar to the first embodiment.
In this second embodiment, there is further a valve 28 disposed in the eighth pipe 27 for coupling a first position 270 of the eighth pipe 27 to a second position 271 of the eighth pipe 27, whereas the first position 270 of the eighth pipe 27 is located at a position between the third expansion valve 132 and the compressor 10, while the second position 271 is located at a position between the compressor 10 and the fifth pipe 24. It is noted that the valve 28 is a one-way valve, by that the refrigerant inside the eighth pipe 28 can only be allowed to flow in one direction.
During the proceeding of a dehumidification process when the apparatus is enabled to operated in a cooling operation mode, the valve 28 will be opened if it is intended to reduce the effectiveness of dehumidification, and thereby, due to the characteristic of fluid that it is natural to flow from high pressure zone to low pressure zone, the high-temperature refrigerant will automatically flow from the second position 271 to the first position 270 without flowing passing through the eighth pipe 27 that is arranged winding around the compressor 10, so that the temperature of the high-temperature refrigerant will be raised by the compressor 10 to a specific temperature and thus the effectiveness of dehumidification is reduced.
Similarly, as shown in FIG. 4 that a balancing process is enabled while the apparatus is operating in a heating operation mode, the valve 28 will block the flowing of the low-temperature refrigerant of the third valve 132 from flowing passing through the valve 28 since it is substantially a one-way valve, but only allow the low-temperature refrigerant of the third valve 132 to flow inside the eighth pipe 27 while being heated by the compressor 10 so as to be transformed into a high-temperature refrigerant and then to be enabled to flow into the fifth pipe 24.
The present disclosure further provides a dehumidification control method, which is adapted for the apparatus shown in FIG. 1, whereas the first sensor 15 is used for detecting a first temperature, the second sensor is used for detecting a second temperature, and the indoor temperature sensor is used for detecting an indoor temperature. The steps performed in aforesaid dehumidification control method are provided hereinafter.
When the apparatus of FIG. 1 is enabled to operated in a cooling operation mode and when the first temperature is lower than the second temperature, the second expansion valve 131 is opened to a degree determined by the difference between the first temperature and the second temperature, i.e. the smaller the difference between the first temperature and the second temperature is, the larger the opening will be for enhancing the effectiveness of cooling.
Thereby, a low-temperature refrigerant is enabled to flow into the indoor heat exchanger 12 for absorbing heat so as to providing cooling to an indoor environment. Consequently, when the second expansion valve 131 is enabled to open larger, there will be more refrigerant flowing into the indoor heat exchanger so that the effectiveness of cooling to the indoor environment will be increased.
Furthermore, when the first temperature is lower than an indoor temperature of the indoor environment, the third expansion valve 132 will be opened to a degree determined by the difference between the first temperature and the indoor temperature, i.e. the smaller the difference between the first temperature and the indoor temperature is, the larger the opening will be for enhancing the effectiveness of dehumidification.
Thereby, a high-temperature refrigerant is enabled to mix with a low-temperature refrigerant so as to form a middle-temperature refrigerant, and then the middle-temperature refrigerant is enabled to flow into the indoor heat exchanger 12 to be used in a heat exchanging process for dehumidifying the indoor environment.
In addition, when the second temperature is lower than the outdoor temperature, the first expansion valve 130 will be opened to a degree determined by the difference between the second temperature and the outdoor temperature, i.e. the smaller the difference between the second temperature and the outdoor temperature is, the larger the opening will be for enhancing the effectiveness of balancing.
Thereby, a low-temperature refrigerant is enabled to mix with a high-temperature refrigerant so as to form a middle-temperature refrigerant, and then the middle-temperature refrigerant is enabled to flow into compressor 10 for balancing.
The present disclosure further provides a defrosting control method, which is adapted for the apparatus of the present disclosure, whereas the steps performed in aforesaid dehumidification control method are provided hereinafter.
When the apparatus of FIG. 2 is enabled to operated in a heating operation mode and when the first temperature is higher than the second temperature, the second expansion valve 131 is opened to a degree determined by the difference between the first temperature and the second temperature, i.e. the larger the difference between the first temperature and the second temperature is, the larger the opening will be for enhancing the effectiveness of heating.
Thereby, a high-temperature refrigerant is enabled to flow into the indoor heat exchanger 12 for dissipating heat so as to providing heating to an indoor environment.
Furthermore, when the first temperature is higher than an indoor temperature of the indoor environment, the third expansion valve 132 will be opened to a degree determined by the difference between the first temperature and the indoor temperature, i.e. the larger the difference between the first temperature and the indoor temperature is, the larger the opening will be for enhancing the effectiveness of balancing.
Thereby, a high-temperature refrigerant is enabled to mix with a low-temperature refrigerant so as to form a middle-temperature refrigerant, and then the middle-temperature refrigerant is enabled to flow into the compressor 10, by that a harmful liquid hammer effect could be avoid from happening while enabling a balance state to be achieved in the apparatus of the present disclosure.
In addition, when the second temperature is higher than the outdoor temperature, the first expansion valve 130 will be opened to a degree determined by the difference between the second temperature and the outdoor temperature, i.e. the larger the difference between the second temperature and the outdoor temperature is, the larger the opening will be for enhancing the effectiveness of defrosting.
Thereby, a high-temperature refrigerant is enabled to mix with a low-temperature refrigerant so as to form a middle-temperature refrigerant, and then the middle-temperature refrigerant is enabled to flow into the outdoor heat exchanger 14 for defrosting.
Please refer to FIG. 5, which is a comparison diagram showing the varying of outdoor temperature with time when an apparatus with dehumidification and defrosting abilities of the present disclosure is enabled to operate in a heating operation mode. In FIG. 5, the apparatus of the present disclosure is enabled to operate in a heating operation mode while the outdoor temperature is about 7° C. or higher. After operating for several minutes, the curve A is flattened indicating that the heating form the apparatus is stabilized, and the longer the apparatus is enabled to operate in the heating operation mode, the more flattening the curve A will become.
The curve B describes the apparatus is operating for defrosting in a condition that the outdoor temperature is ranged between 7° C. and 0° C., in which a cool circuit is the flowing path of the aforesaid low-temperature refrigerant, and a hot circuit is the flowing path of the aforesaid high-temperature refrigerant. After operating for several minutes, the curve B appears to become flattened and overlay with the curve A, indicating that both the defrosting and heating of the apparatus are stabilized.
As indicated in the curve B with reference to FIG. 2, a high-temperature high-pressure refrigerant flowing into the indoor heat exchanger 12 for heat dissipating is transformed into a low-temperature high-pressure refrigerant, and then the low-temperature high-pressure refrigerant is enabled to flow into the means for refrigerant flow controlling 13 via the first pipe 20 where it is expanded into a low-temperature low-pressure refrigerant.
Thereafter, the low-temperature low-pressure refrigerant is enabled to flow into the outdoor heat exchanger via the sixth pipe 25 for absorbing heat so as to be transformed into a high-temperature low-pressure refrigerant.
Such high-temperature low-pressure refrigerant is then being enabled to flow sequentially via the fifth pipe 24, the four-way valve 11 and the third pipe 22 into the compressor 10 so as to be transformed back into the forgoing high-temperature high-pressure refrigerant. Then the high-temperature high-pressure refrigerant is being enabled to flow sequentially via the fourth pipe 23, the four-way valve 11 and the second pipe 22 into the indoor heat exchanger 12.
There are two parts of adjustments in the curve B, which are a cool circuit adjustment and a hot circuit adjustment.
In the hot circuit adjustment, the low-temperature high-pressure refrigerant from the first pipe 20 is enabled to flow into the means for refrigerant flow controlling 13 where it is expanded into a low-temperature low-pressure refrigerant. Then the low-temperature low-pressure refrigerant is enabled to flow into the eighth pipe 27 while being heated by the compressor 10 so as to form a high-temperature low-pressure refrigerant to be enabled to flow into the fifth pipe 24. However, after being heated by the compressor, the temperature of the high-temperature low-pressure refrigerant is lower than the temperature of the high-temperature low-pressure refrigerant that is already flowing inside the fifth pipe 24, and also the pressure of the high-temperature low-pressure refrigerant flowing in the eighth pipe 27 is smaller than the pressure of the high-temperature low-pressure refrigerant flowing inside the fifth pipe 24. Therefore, by the mixing of the aforesaid two refrigerants inside the fifth pipe 24, a middle-temperature low-pressure refrigerant can be achieved, but is still being referred as a high-temperature low-pressure refrigerant for clarity.
In the cool circuit adjustment, the high-temperature high-pressure refrigerant from the compressor 10 is enabled to flow into the means for refrigerant flow controlling 13 where it is expanded into a high-temperature low-pressure refrigerant. Thereafter, the high-temperature low-pressure refrigerant is mixed with the low-temperature low-pressure refrigerant flowing inside the sixth pipe 25 so as to form a middle-temperature low-pressure refrigerant while allowing the middle-temperature low-pressure refrigerant to flow into the outdoor heat exchanger 14 for absorbing heat to be transformed into a high-temperature low-pressure refrigerant. Such high-temperature low-pressure refrigerant is then being enabled to flow sequentially via the fifth pipe 24, the four-way valve 11 and the third pipe 22 into the compressor 10. It is noted that the pressure of the middle-temperature low-pressure refrigerant is larger than the pressure of the high-temperature low-pressure refrigerant flowing inside the fifth pipe 24.
According to the above description, by the splitting and mixing of refrigerants inside the apparatus of the present disclosure, the temperature and pressure of the refrigerant flowing into the outdoor heat exchanger 14 are varied as well as the temperature and pressure of the refrigerant flowing into the compressor 10, and thereby, the purposes of the cool circuit adjustment and the hot circuit adjustment can be achieved.
The curve C in FIG. 5 describes the hot circuit adjustment of the apparatus for defrosting and the outdoor temperature is lower than 0° C. During which the apparatus is enabled to perform three operations, i.e. heating, defrosting and balancing. As shown in FIG. 5, after operating for several minutes, the curve C appears to become flattened and overlay with the curve A, indicating that the balancing, the defrosting and heating of the apparatus are stabilized.
Please refer to FIG. 6, which is a comparison diagram showing the varying of indoor temperature with time when an apparatus with dehumidification and defrosting abilities of the present disclosure is enabled to operate in a cooling operation mode. In FIG. 6, the apparatus of the present disclosure is enabled to operate in a cooling operation mode while the outdoor temperature is about 27° C. or higher. After operating for several minutes, the curve D is flattened indicating that the cooling form the apparatus is stabilized, and the longer the apparatus is enabled to operate in the heating operation mode, the more flattening the curve D will become.
The curve E describes the apparatus is operating for dehumidification in a condition that the outdoor temperature is ranged between 27° C. and 24° C. Similarly, after operating for a period of time, the curve E appears to become flattened and overlay with the curve D, indicating that both the dehumidification and cooling of the apparatus are stabilized. It is noted that the period of time should last for at several minutes to more than ten minutes.
As indicated in the curve E with reference to FIG. 1, a high-temperature low-pressure refrigerant from the first pipe 20 is enabled to flow into the indoor heat exchanger 12 for absorbing heat dissipating so as to be transformed into a high-temperature high-pressure refrigerant, and then the high-temperature high-pressure refrigerant is enabled to flow into the compressor 10 via the second pipe 21 so as to be transformed into a high-temperature high-pressure refrigerant. Thereafter, such high-temperature high-pressure refrigerant is enabled to flow through the fourth pipe 23 into the outdoor heat exchanger 14 for dissipating heat to be transformed into a low-temperature high-pressure refrigerant.
Then, the low-temperature high-pressure refrigerant is enabled to flow through the sixth pipe 25 into the means for refrigerant flow controlling 13 where it is expanded into the aforesaid low-temperature low-pressure refrigerant while enabling the low-temperature low-pressure refrigerant to flow into the indoor heat exchanger 12 via the first pipe 20.
There are also two parts of adjustments in the curve E, which are a cool circuit adjustment and a hot circuit adjustment.
In the cool circuit adjustment, the high-temperature high-pressure refrigerant from the compressor 10 is enabled to flow sequentially through the fourth pipe 23, the four-way valve 11, the fifth pipe 24 and the eighth pipe 27 into the means for refrigerant flow controlling 13 where it is expanded into a high-temperature low-pressure refrigerant. Thereafter, the high-temperature low-pressure refrigerant is mixed with the low-temperature low-pressure refrigerant flowing inside the first pipe 20 so as to form a middle-temperature low-pressure refrigerant while allowing the middle-temperature low-pressure refrigerant to flow into the indoor heat exchanger 12. It is noted that the pressure of the middle-temperature low-pressure refrigerant is larger than the pressure of the low-temperature low-pressure refrigerant.
In the hot circuit adjustment, the low-temperature high-pressure refrigerant from the outdoor heat exchanger 14 is enabled to flow through the sixth pipe 25 into the means for refrigerant flow controlling 13 where it is expanded into a low-temperature low-pressure refrigerant. Then the low-temperature low-pressure refrigerant is enabled to flow through the seventh pipe 26 into the second pipe 21 where it is mixed with the high-temperature low-pressure refrigerant that is already flowing inside the second pipe 21 so as to form a middle-temperature low-pressure refrigerant. It is noted that the pressure of the middle-temperature low-pressure refrigerant is larger than the pressure of the high-temperature low-pressure refrigerant.
According to the above description, by the splitting and mixing of refrigerants inside the apparatus of the present disclosure, the temperature and pressure of the refrigerant flowing into the indoor heat exchanger 12 are varied as well as the temperature and pressure of the refrigerant flowing into the compressor 10, and thereby, the purposes of the cool circuit adjustment and the hot circuit adjustment can be achieved.
The curve F in FIG. 6 describes the hot circuit adjustment of the apparatus for dehumidification and the outdoor temperature is lower than 24° C. During which the apparatus is enabled to perform three operations, i.e. heating, dehumidification and balancing. As shown in FIG. 6, after operating for several minutes, the curve F appears to become flattened and overlay with the curve D, indicating that the balancing, the dehumidification and heating of the apparatus are stabilized.
To sum up, as the conventional air conditioning systems or dehumidification systems that are currently available can generally cause indoor temperature to increase while being used for dehumidifying, or can cause the indoor temperature to drop while being used for defrosting, both can cause discomfort to the people indoors. Therefore, by the balancing of the apparatus of the present disclosure that is achieved through the mixing of a high-temperature refrigerant and a low-temperature refrigerant, either the apparatus can be used for dehumidification or for defrosting without causing any indoor temperature to fluctuate, and thus the comfort of people indoors can be maintained.
With respect to the above description then, it is to be realized that the optimum dimensional relationships for the parts of the disclosure, to include variations in size, materials, shape, form, function and manner of operation, assembly and use, are deemed readily apparent and obvious to one skilled in the art, and all equivalent relationships to those illustrated in the drawings and described in the specification are intended to be encompassed by the present disclosure.

Claims

What is claimed is:

1. An apparatus with dehumidification and defrosting abilities, comprising:

a compressor;

an indoor heat exchanger;

an outdoor heat exchanger;

a four-way valve; and

a means for refrigerant flow controlling;

wherein, the compressor is coupled to the four-way valve; the four-way valve is coupled to the outdoor heat exchanger; the indoor heat exchanger is coupled to the four-way valve; and the means for refrigerant flow controlling is respectively coupled to the indoor heat exchanger, the outdoor heat exchanger and the four way valve, while being enabled to a process selecting from the group consisting of: controlling the mixing of a low-temperature refrigerant and a high-temperature before flowing into the indoor heat exchanger, controlling the mixing of a low-temperature refrigerant and a high-temperature refrigerant before flowing into the compressor, and controlling the mixing of a low-temperature refrigerant and a high-temperature refrigerant before flowing into the outdoor heat exchanger.

2. The apparatus of claim 1, further comprising: a first pipe, a second pipe, a third pipe, a fourth pipe, a fifth pipe, a sixth pipe, a seventh pipe, and an eighth pipe, being arranged in a manner that the compressor is coupled to the four-way valve via the fourth pipe; the four-way valve is coupled to the outdoor heat exchanger via the fifth pipe; the outdoor heat exchanger is coupled to the means for refrigerant flow controlling via the sixth pipe; the means for refrigerant flow controlling is coupled to the indoor heat exchanger via the first pipe; the indoor heat exchanger is coupled to the four-way valve via the second pipe; the four-way valve is coupled to the compressor via the third pipe; the means for refrigerant flow controlling is coupled to the second pipe via the seventh pipe; the means for refrigerant flow controlling is coupled to the fifth pipe via the eighth pipe, while allowing the eighth pipe to be disposed winding around the periphery of the compressor.

3. The apparatus of claim 2, wherein the means for refrigerant flow controlling further comprises: a first expansion valve, a second expansion valve and a third expansion valve, being arranged in a manner that the first expansion valve and the second expansion valve are arranged coupling to the sixth pipe in respective, while allowing the first expansion valve to couple to the seventh pipe; and the second expansion valve and the third expansion valve are arranged coupling to the first pipe in respective, while allowing the third expansion valve to couple to the eighth pipe.

4. The apparatus of claim 3, wherein each of the first expansion valve, the second expansion valve and the third expansion valve is substantially an electronic expansion valve.

5. The apparatus of claim 3, wherein the eighth pipe is configured with a first position, a second position and a valve in a manner that the valve is disposed coupling respectively to the first position and the second position.

6. The apparatus of claim 5, wherein the first position is disposed between the third expansion valve and the compressor; the second position is disposed between the compressor and the fifth pipe; and the valve is a one-way valve.

7. The apparatus of claim 1, wherein the outdoor heat exchanger further comprises an outdoor temperature sensor; and the indoor heat exchanger further comprises an indoor temperature sensor.

8. A dehumidification control method, comprising the step of:

enabling a low-temperature refrigerant to mix with a high-temperature refrigerant so as to form a middle temperature refrigerant when an indoor temperature is larger than a first temperature, while enabling the middle temperature refrigerant to flow into an indoor heat exchanger.

9. The dehumidification control method of claim 8, further comprising the step of:

enabling a low-temperature refrigerant to mix with a high-temperature refrigerant so as to form a middle temperature refrigerant when an outdoor temperature is larger than a second temperature, while enabling the middle temperature refrigerant to flow into a compressor where it is forced to flow into an outdoor heat exchanger.

10. The dehumidification control method of claim 9, wherein the first temperature is detected and obtained by a first sensor arranged in a means for refrigerant flow controlling; the second temperature is detected and obtained by a second sensor arranged in the means for refrigerant flow controlling; the indoor temperature is detected and obtained by an indoor temperature sensor; and the outdoor temperature is detected and obtained by an outdoor temperature sensor.

11. The dehumidification control method of claim 10, wherein the means for refrigerant flow controlling is configured with a second expansion valve, the second expansion valve is coupled to an indoor heat exchanger, the first sensor is disposed at a position between the indoor heat exchanger and the second expansion valve, the second expansion valve is further coupled to an outdoor heat exchanger, and the second sensor is disposed at a position between the second expansion valve and the outdoor heat exchanger.

12. A defrosting control method, comprising the step of:

enabling a low-temperature refrigerant to mix with a high-temperature refrigerant so as to form a middle temperature refrigerant when an outdoor temperature is smaller than a second temperature, while enabling the middle temperature refrigerant to flow into an outdoor heat exchanger.

13. The defrosting control method of claim 12, further comprising the step of:

enabling a low-temperature refrigerant to mix with a high-temperature refrigerant so as to form a middle temperature refrigerant when an indoor temperature is smaller than a first temperature, while enabling the middle temperature refrigerant to flow into an indoor heat exchanger.

14. The defrosting control method of claim 13, wherein the first temperature is detected and obtained by a first sensor arranged in a means for refrigerant flow controlling; the second temperature is detected and obtained by a second sensor arranged in the means for refrigerant flow controlling; the indoor temperature is detected and obtained by an indoor temperature sensor; and the outdoor temperature is detected and obtained by an outdoor temperature sensor.

15. The defrosting control method of claim 14, wherein the means for refrigerant flow controlling is configured with a second expansion valve, the second expansion valve is coupled to an indoor heat exchanger, the first sensor is disposed at a position between the indoor heat exchanger and the second expansion valve, the second expansion valve is further coupled to an outdoor heat exchanger, and the second sensor is disposed at a position between the second expansion valve and the outdoor heat exchanger.