Patent Grant
9612047
The present invention generally relates to refrigeration cycle apparatuses provided with an ejector, and particularly relates to a refrigeration cycle apparatus capable of performing a high-capacity operation using a compressor having an injection and a high-efficiency operation due to a power recovery effect of an ejector in a low-outdoor-air-temperature environment.
A related-art refrigeration cycle apparatus provided with an ejector is configured to suppress decreasing an evaporation capacity and an operating efficiency by lowering a refrigerant flow rate into an evaporator due to a shortage of a driving power of the ejector (see Patent Literature 1, for example).
The related-art device includes a check valve bridge circuit for using the ejector in both a cooling operation and a heating operation. Further, a bypass circuit for bypassing the check valve bridge circuit connects a high-pressure-side inlet to a low-pressure-side outlet of the check valve bridge circuit with a refrigerant pipe and a bypass valve. A refrigerant circuit is formed such that when the evaporation capacity and the efficiency of the refrigeration cycle decrease due to the shortage of the recovery power in the ejector, this bypass circuit opens the bypass valve and fully closes a valve of a nozzle in the ejector so as to reduce a pressure using a regular expansion valve without using the ejector.
With this configuration, the refrigeration cycle apparatus can perform a high-efficiency operation due to power recovery of the ejector and provide high reliability due to a provision of the bypass circuit. Also, since the high-temperature heat source on the load side can be used during a defrosting operation, it is possible to reduce the time required for the defrosting operation. Thus, the suspension time of a heating operation is reduced, which makes it possible to prevent a reduction in comfort.
Further, with regard to refrigeration cycle apparatuses that provide improved heating capacity using a compressor having an injection port, a refrigeration cycle apparatus is known that has a configuration in which an outlet-side pipe of a condenser is connected to an injection port through a throttle mechanism and an internal heat exchanger by piping, for example. With this configuration, the throttle mechanism controls the injection flow rate. Further, in order to prevent liquid injection into a compressor, a refrigerant having a high dryness due to heat exchange by the internal heat exchanger is injected. Thus, it is possible to improve the reliability of the compressor (see Patent Literature 2, for example).
A problem with the related-art devices is that, during a heating operation under a low-outdoor-air-temperature condition, the suction density of the compressor is reduced due to a reduction in the evaporating pressure, which reduces the refrigerant circulation volume, and thus reduces the heating capacity. Another problem is that when the refrigerant circulation volume is increased by increasing the compressor frequency in order to improve the heating capacity, the power consumption of the compressor increases, so that the operating efficiency of the refrigeration cycle decreases.
The present invention has been made to overcome the above problems, and aims to provide a refrigeration cycle apparatus with improved heating capacity and improved efficiency under a low-outdoor-air-temperature condition.
A refrigeration cycle apparatus according to the present invention includes: a high-pressure-side refrigerant circuit in which a compressor, a condenser, an ejector, and a gas-liquid separator are connected in series with a refrigerant pipe; a low-pressure refrigerant circuit in which a liquid refrigerant that has flowed out of the gas-liquid separator flows through a fourth flow control valve 113 and an evaporator to a refrigerant suction port of the ejector; a compressor suction circuit that connects an upper outlet of the gas-liquid separator to a suction port of the compressor such that a gas refrigerant that has flowed out of the gas-liquid separator is suctioned into the compressor;
a first bypass circuit that connects a point between the condenser and the ejector of the high-pressure refrigerant circuit to an intermediate pressure portion of the compressor via a second flow control valve 109; an internal heat exchanger that exchanges heat between a refrigerant whose pressure has been reduced at the second flow control valve 109 of the first bypass circuit and a high-pressure refrigerant flowing in the high-pressure-side refrigerant circuit; and a second bypass circuit that connects a point between a first flow control valve 105 and the internal heat exchanger to a point between the fourth flow control valve 113 and the evaporator of the low-pressure refrigerant circuit via a third flow control valve 111 so as to allow the high-pressure refrigerant to take a bypass, the first flow control valve 105 being disposed between the internal heat exchanger and the ejector. While the second flow control valve 109 is opened such that the refrigerant flows through the first bypass circuit, the fourth flow control valve 113 is switched to be opened or closed, and the third flow control valve 111 is switched to be closed or opened.
The refrigeration cycle apparatus according to the present invention can provide improved heating capacity by increasing the refrigerant circulation volume in the high-pressure-side refrigerant circuit with use of the first bypass circuit, and can perform a high-efficiency operation due to power recovery by the ejector.
Further, in the case where a nozzle portion of the ejector is clogged with impurities inside the refrigeration cycle, the refrigeration cycle apparatus uses the second bypass circuit and thus can prevent its operation from being stopped.
The ejector 106 decompresses and expands a high-pressure refrigerant, which is a driven flow, in the pressure reducing portion 201a, accelerates the refrigerant to a sonic speed in the nozzle throat portion 201b, and further decompresses and accelerates the refrigerant to a supersonic speed in the tapered portion 201c. The refrigerant, that is, the driven flow may be either in a supercooled liquid state or in a two-phase gas-liquid flow state. The refrigerant is suctioned through the suction portion 204 from the surrounding area (suction refrigerant). The driven refrigerant and the suction refrigerant in the ejector 106 are mixed in the mixing portion 202, so that the pressure is recovered (increased) through exchange of momentum therebetween. The pressure is further recovered in the diffuser portion 203 by the decelerating effect due to an expansion of the passage. Then, the refrigerant flows out of the diffuser portion 203.
Next, operations are described in a heating operation, for example.
The compressor having an injection port makes a refrigerant injected into an intermediate pressure of the compressor so as to increase the refrigerant circulation volume in the compressor, and thereby improves the capacity. On the other hand, the ejector recovers the expansion power that has been generated in an expansion process of the refrigerant and utilizes the recovered power so as to reduce the power consumption of the compressor, and thereby improves the COP. In this case, the opening degrees of the first flow control valve 105, the second flow control valve 109, and the fourth flow control valve 113 are set in accordance with a control operation described below, while the third flow control valve 111 is fully closed.
A low-pressure refrigerant in a state “a” at a suction port of the compressor 101 is compressed to be in a state “b” by the compressor 101. The refrigerant in the state “b” passes through the refrigerant four-way valve 102 and is cooled in the condenser 103 through heat exchange with the indoor air so as to be in a state “c”. The refrigerant in the state “c” is divided into a refrigerant that flows toward a refrigerant inlet of the ejector 106 and a refrigerant that flows toward the first bypass circuit 110. The refrigerant in the state “c” that has flowed into the first bypass circuit 110 is subjected to pressure reduction by the second flow control valve 109 so as to be in a state “k”, and then flows into a low-pressure-side inlet of the supercooler 104. On the other hand, the high-temperature high-pressure refrigerant in the state “c” flowing toward the ejector 106 flows into a high-pressure-side inlet of the supercooler. In the supercooler 104, the high-temperature high-pressure refrigerant in the state “k” and the low-temperature low-pressure refrigerant in the state “c” exchange heat with each other. Thus, the refrigerant in the state “k” is heated so as to be in a state “l”, and then is injected into the intermediate pressure of the compressor. On the other hand, the refrigerant in the state “c” is cooled so as to be in a state “d”, and flows toward the ejector 106.
The refrigerant in the state “d” flowing toward the ejector 106 is subjected to pressure reduction by the first flow control valve 105 so as to be in a state “e”, is subjected to pressure reduction by the pressure reducing portion 201a so as to be in a state “f”, and is ejected from a nozzle outlet as a high-speed two-phase gas-liquid refrigerant. The refrigerant in the state “f” immediately after ejection from the nozzle outlet is mixed with the refrigerant in a state “j” that has flowed from the ejector suction portion 204. After the pressure is increased in the mixing portion 202 and the diffuser portion 203, the refrigerant is brought into a state “g”, and then flows out of the ejector 106. The two-phase gas-liquid refrigerant in the state “g” that has flowed out of the ejector 106 is divided into a liquid refrigerant and a gas refrigerant by the gas-liquid separator 107. The refrigerant in a state “h” that has flowed out of the liquid refrigerant outlet of the gas-liquid separator 107 is brought into a state “i” at the fourth flow control valve 113, and flows into the evaporator 108. The refrigerant in the state “i” absorbs heat from the outdoor air in the evaporator 108 so as to be in the state “j”, and flows into the ejector suction portion 204. On the other hand, the refrigerant in the state “a” that has flowed out of a gas refrigerant outlet of the gas-liquid separator 107 is guided to the suction port of the compressor 101. Although not shown, a gas refrigerant pipe inside the gas-liquid separator 107 is formed in a U-shape and has an oil hole. Thus, oil that has accumulated in the gas-liquid separator 107 flows into the compressor 101 together with the gas refrigerant.
With these operations, a refrigeration cycle is formed.
The operations illustrated in
The first bypass circuit 110 may be used when the outdoor air temperature is lower than B (e.g., lower than 2 degrees C.), and this outdoor air temperature B may be set in a temperature range in which a capacity-improved operation is started. In this case, the passage cross-sectional area of the ejector throat portion 201b of
Next, a description will be given of operations that, when the outdoor air temperature is B or higher, achieve a sufficient heating capacity without using injection of a refrigerant into the compressor 101, and realize high-efficiency using an ejector, with reference to a Mollier chart of
The refrigerant in a state “a” that has flowed into the compressor 101 is brought into a high-temperature high-pressure state “b”. The refrigerant in the state “b” is cooled in the condenser 103 through heat exchange with the indoor air so as to be in a state “c”. The refrigerant in the state “c” that has flowed out of the condenser passes through a high-pressure-side refrigerant passage of the supercooler 104, and then flows into the ejector 106. At this point, since the second flow control valve 109 is closed, the refrigerant does not flow into the first bypass circuit 110. Accordingly, heat exchange is not performed in the supercooler 104, and hence the state of the refrigerant at the outlet of the supercooler is the same as the state “c”. The refrigerant in a state “d” flowing toward the ejector 106 is subjected to pressure reduction by the first flow control valve 105 so as to be in a state “e”, is subjected to pressure reduction by the pressure reducing portion 201a so as to be in a state “f”, and is ejected from the nozzle outlet as a high-speed two-phase gas-liquid refrigerant. The refrigerant in the state “f” immediately after ejection from the nozzle outlet is mixed with the refrigerant in a state “j” that has flowed from the ejector suction portion 204 so as to be in a state “g”. After the pressure is increased in the mixing portion 202 and the diffuser portion 203, the refrigerant is brought into a state “g”, and then flows out of the ejector 106. The two-phase gas-liquid refrigerant in the state “g” that has flowed out of the ejector 106 is separated into a liquid refrigerant and a gas refrigerant by the gas-liquid separator 107. Thus, the liquid refrigerant is in a state “h”, and the gas refrigerant is in the state “a”. The liquid refrigerant in the state “h” that has flowed out of the liquid refrigerant outlet of the gas-liquid separator 107 is brought into a state “ri” at the fourth flow control valve 113, and flows into the evaporator 108. The refrigerant in the state “i” absorbs heat from the outdoor air in the evaporator 108 so as to be in the state “j”, and flows into the ejector suction portion 204. On the other hand, the gas refrigerant in the state “a” that has flowed out of the gas refrigerant outlet of the gas-liquid separator 107 is guided to the suction port of the compressor 101.
With these operations, a refrigeration cycle is formed.
When this refrigeration cycle is used, the suction pressure of the compressor 101 is increased due to the pressure increasing effect of the ejector, compared with the case where the ejector is not used. Thus, the power consumption of the compressor 101 is reduced, so that the COP is improved.
Next, a description will be given of operations that perform only a capacity-improved operation without using an ejector with reference to a Mollier chart of
In this case, the first flow control valve 105 and the fourth flow control valve 113 are fully closed, while the opening degrees of the second flow control valve 109 and the third flow control valve 111 are adjusted in accordance with a control operation. The state shown in the Mollier chart of
The low-pressure refrigerant in a state “a” at the suction port of the compressor 101 is compressed to be in a state “b” by the compressor 101. The refrigerant in the state “b” passes through the refrigerant four-way valve 102 and is cooled in the condenser 103 through heat exchange with the indoor air so as to be in a state “c”. The refrigerant in the state “c” is divided into a refrigerant that flows toward the refrigerant inlet of the ejector 106 and a refrigerant that flows toward the first bypass circuit 110. The refrigerant in the state “c” that has flowed into the first bypass circuit 110 is subjected to pressure reduction by the second flow control valve 109 so as to be in a state “k”, and then flows into a low-pressure-side inlet of the supercooler 104. The high-temperature high-pressure refrigerant in the state “c” flowing toward the third flow control valve 111 flows into the high-pressure-side inlet of the supercooler. In the supercooler 104, the low-temperature low-pressure refrigerant in the state “k” and the high-temperature high-pressure refrigerant in the state “c” exchange heat with each other. Thus, the refrigerant in the state “k” is heated so as to be in a state “l”, and then is injected into the intermediate pressure of the compressor. The refrigerant in the state “c” flowing through the high-pressure-side passage of the supercooler 104 is cooled so as to be in a state “d”, and flows into the third flow control valve 111. The flow rate of the refrigerant in the state “d” is restricted by the third flow control valve 111, so that the refrigerant is brought into a state “i”. Then, the refrigerant flows into the evaporator 108. In the evaporator 108, the refrigerant is brought into a state “j” through heat exchange with the outdoor air. After that, the refrigerant flows through the suction portion 204 of the ejector 106 and the gas refrigerant outlet of the gas-liquid separator 107 so as to be in the state “a”, and then is suctioned into the compressor 101.
With these operations, a refrigeration cycle is formed. Thus, the refrigerant flow rate into the condenser 103 is increased by injection of the refrigerant into the compressor, so that the capacity can be increased.
Next, a description will be given of operations using a conventional refrigeration cycle without using the ejector 106 and injection with reference to a Mollier chart of
The refrigerant in a state “a” that has flowed into the compressor 101 is brought into a high-temperature high-pressure state “b”. The refrigerant in the state “b” is cooled in the condenser 103 through heat exchange with the indoor air so as to be in a state “c”. The refrigerant in the state “c” that has flowed out of the condenser 103 passes through the high-pressure-side refrigerant passage of the supercooler 104, and then flows into the third flow control valve 111. At this point, since the second flow control valve 109 is closed, the refrigerant does not flow into the first bypass circuit 110. Accordingly, heat exchange is not performed in the supercooler 104, and hence the state “d” of the refrigerant at the outlet of the supercooler is the same as the state “c”. The flow rate of the refrigerant that has flowed out of the condenser 103 is restricted by the third flow control valve 111, so that the refrigerant is brought into a state “i”. Then the refrigerant flows into the evaporator 108. The refrigerant that has flowed into the evaporator 108 is brought into a state “j” through heat exchange with the outdoor air. After that, the refrigerant flows via the suction portion 204 and the mixing portion 202 of the ejector 106 through the gas refrigerant outlet of the gas-liquid separator 107 so as to be in the state “a”, and then is suctioned into the compressor.
With this operation, even if the nozzle portion of the ejector 106 is clogged, it is possible to provide a refrigeration cycle having a high reliability by using a bypass circuit.
Next, a description will be given of a defrosting operation.
Since the outdoor heat exchanger serves as an evaporator during a heating operation, the saturation temperature of the refrigerant flowing in the outdoor heat exchanger is lower than the temperature of the outdoor air. When the evaporating temperature falls below 0 degrees C., water vapor in the atmosphere turns into frost and adheres to the outdoor heat exchanger. The frost on the outdoor heat exchanger increases thermal resistance, and hence the evaporation capacity decreases. Therefore, it is necessary to perform a defrosting operation regularly. In a defrosting operation, the four-way valve 102 switches the passages such that the first flow control valve 105, the second flow control valve 109, and the fourth flow control valve 113 are fully closed while the third flow control valve 111 is opened.
When a defrosting operation starts, the four-way valve 102 switches the passages such that a refrigerant that has flowed out of the compressor 101 flows into the outdoor heat exchanger 108. The frost on the outdoor heat exchange is melted by the high-temperature high-pressure refrigerant. In this case, the outdoor heat exchanger 108 serves as a condenser. Thus, the refrigerant is liquefied, is subjected to pressure reduction by the third flow control valve 111, and flows into an indoor heat exchanger. The refrigerant that has flowed into the indoor heat exchanger evaporates through heat exchange with the indoor air, sequentially passes through the suction portion 204 of the ejector 106, the mixing portion 202, the diffuser portion 203, and the gas-liquid separator 107, and is suctioned into the compressor 101. Thus, a refrigeration cycle is formed. In a cooling operation, as in the case of the defrosting operation, a refrigeration cycle is formed by appropriately controlling the opening degree of the third flow control valve 111. Although the refrigeration cycle diagram of the cooling operation is similar to that of
Next, a description will be given of a method of controlling the flow control valves 105, 109, 111, and 113.
The power that can be recovered by the ejector 106 is obtained by the product of the adiabatic heat drop (the enthalpy difference from an ejector nozzle state to a state adiabatically expanded to an outlet pressure of the ejector nozzle), the refrigerant flow rate into the ejector nozzle portion 201, and the power recovery efficiency (ejector efficiency).
In ST101, the temperature sensor 116 attached to the outlet of the supercooler 104 detects a temperature. In ST102, the pressure sensor 117 attached to a discharge pipe of the compressor 101 detects a pressure. In ST103, a saturation temperature of the refrigerant is computed based on the pressure value detected in Step ST102. In ST104, the degree of supercooling in the point “ni” at the outlet of the supercooler 104 is computed from the difference between the computed value of the saturation temperature of the refrigerant and the detected temperature value of the outlet of the supercooler. A determination is made on this computed value of the degree of supercooling in ST105, and then the opening degree of the first flow control valve 105 is controlled.
If the computed value of the degree of supercooling is less than a target value, the opening degree of the first flow control valve 105 is reduced in ST106-1 so as to reduce the refrigerant flow rate (ST106-1a) and thereby increase the degree of supercooling (ST106-1b). When the target value of the supercooling is greater, the opening degree of the first flow control valve 105 is increased in ST106-2 so as to increase the refrigerant flow rate (ST106-2a) and thereby reduce the degree of supercooling (ST103-2b). This operation is repeated periodically so as to control the degree of supercooling in the point “ni” at the outlet of the supercooler 104. Referring to
Next, a description will be given of control of the second flow control valve 109 with reference to
In ST201, the outdoor air temperature sensor 118 detects the outdoor air temperature. In ST202, it is determined whether to open or close the second flow control valve 109 based on this detected value. When the detected value of the outdoor air temperature sensor 118 is less than a first setting value, the second flow control valve 109 is opened. When the detected value is equal to or greater than the first setting value, the second flow control valve 109 is closed. It is to be noted that the first setting value may be set to a temperature at which the heating capacity starts decreasing in the case where the second flow control valve 109 is in a closed state.
If the detected value is less than the first setting value and it is determined to open the second flow control valve 109 in ST202, the opening degree is controlled based on a computed value of the degree of superheat of the refrigerant discharged from the compressor 101 in ST203. The degree of superheat of the refrigerant discharged from the compressor 101 is computed from the difference between a detected value of the temperature sensor 119 attached to a discharge pipe of the compressor 101 and a saturation temperature of the refrigerant, which is calculated on the basis of a detected value of the pressure sensor 117 attached to the discharge pipe of the compressor 101. When the degree of superheat is less than a second setting value in ST203, the opening degree of the second flow control valve 109 is reduced in ST204-1. Thus, the refrigerant flow rate into the first bypass circuit 110 decreases (ST204-1a), so that the degree of superheat increases (ST204-1b). When the degree of superheat is equal to or greater than the second setting value in ST203, the opening degree of the second flow control valve 109 is increased in ST204-2. Thus, the refrigerant flow rate into the first bypass circuit 110 is increased (ST204-2a), so that the degree of superheat is reduced (ST204-2b). This operation is repeated periodically so as to control the degree of superheat of the refrigerant discharged from the compressor 101 in the point “b”.
If the second setting value is small, the refrigerant flow rate into the first bypass circuit 110 is increased, and therefore the low-pressure refrigerant flowing in the supercooler cannot be sufficiently evaporated. Thus, the refrigerant containing a large amount of liquid refrigerant is injected into the intermediate pressure of the compressor 101, which may result in a trouble of the compressor. Accordingly, the second setting value may preferably be set by taking the reliability of the compressor into consideration.
Next, a description will be given of control of the third flow control valve 111.
In ST304, when the degree of superheat is lower than a third setting value, it is determined that the ejector 106 is suctioning the refrigerant. Then, the first flow control valve 105 is opened (ST305-1); the third flow control valve 111 is closed (ST306-1); and the fourth flow control valve 113 is opened (ST307-1). Thus, the refrigerant is caused to flow into the ejector 106 (ST308-1) so as to perform a high efficiency operation using the ejector 106. On the other hand, when the degree of superheat is higher than the third setting value in ST304, the suction flow rate of the ejector 106 is reduced, and hence the ejector 106 is determined to be in an abnormal state. Then, the operation is switched to an operation using a circuit in which the first flow control valve 105 is closed (ST305-2); the third flow control valve 111 is opened (ST306-2); the fourth flow control valve 113 is closed (ST307-2); and the refrigerant is caused to flow into the second bypass circuit 112 so as to bypass the ejector 106 (ST308-2).
The third setting value may be set to be lower than or equal to 6 degrees C. at which the COP starts decreasing as shown in
Further, the third flow control valve 111 may be controlled in accordance with the outdoor air temperature.
It is to be noted that a pressure sensor may be provided at a refrigerant inlet of the evaporator 108 such that the degree of superheat in the ejector suction portion 204 can also be calculated on the basis of a detected value of this pressure sensor and a detected value of the temperature sensor 120 at the suction portion of the ejector.
On the other hand, at low outdoor air temperatures, the ejector is unable to achieve an optimum expansion for the refrigeration cycle, so that the power recovery efficiency is reduced. Thus, as shown in
The setting values of the first outdoor air temperature and the second outdoor air temperature may be set in a temperature range in which it is desired to improve the efficiency using the ejector, and the ejector may be designed such that the power recovery efficiency of the ejector have a maxima value in this temperature range.
Further, a determination of whether to open or close the third flow control valve 111 may be made based on the rotation speed of the compressor 101. The recovery power of the ejector 106 is obtained by the product of the adiabatic heat drop, the ejector-driven refrigerant flow rate, and the power recovery efficiency. Accordingly, in the case where the ejector-driven refrigerant flow rate is high, that is, the case where the rotation speed of the compressor 101 is high, a high-efficiency operation using the ejector is performed. When the refrigerant flow rate is low, the recovery power decreases, so that the suction refrigerant flow rate of the ejector 106 decreases. Thus, the degree of superheat in the ejector suction portion rises, so that the COP decreases as shown in
Detecting means for detecting the rotation speed of the compressor detects the rotation speed in ST501, and it is determined whether to open or close the flow control valves 105, 111, and 113 in accordance with the rotation speed of the compressor in ST502. When the compressor rotation speed is equal to or greater than the fourth setting value, the first flow control valve 105 is opened in ST503-1; the third flow control valve 111 is closed in ST504-1; and the fourth flow control valve 113 is opened in ST505-1. Thus, the refrigerant flows into the ejector 106 (ST506-1).
When the compressor rotation speed is less than the fourth setting value, the first flow control valve 105 is closed in ST503-2; the third flow control valve 111 is opened in ST504-2; and the fourth flow control valve 113 is closed in ST505-2. Thus, the refrigerant flows into the second bypass circuit (ST506-2).
Next, a description will be given of control of the fourth flow control valve 113.
As shown in
As can be seen from the above, according to this embodiment, it is possible to perform a high-capacity operation at low outdoor air temperatures using the compressor 101 having an injection port, and a high-efficiency operation using power recovery by the ejector 106. Also, it is possible to provide diversity in the operating condition of the refrigerant circuit by opening and closing the flow control valve. When the recovery power of the ejector is reduced due to a change in the outdoor air temperature or the frequency of the compressor, an operation can be performed using second bypass circuit 112 without using the ejector. Further, when the nozzle portion of the ejector is clogged, the second bypass circuit 112 is used which is provided in parallel with the ejector. Thus, it is possible to provide a refrigeration cycle apparatus having a high efficiency and a high reliability.
In this embodiment, the first flow control valve 105 is provided upstream of the ejector 106. However, as shown in
Further, although a compressor having an injection port is used in the present embodiment, the present invention is not limited thereto. The same effects can be obtained by using an equivalent structure, for example, a two-stage compressor and a plurality of compressors that may be connected in series such that refrigerants discharged from a first one of the compressors and a low-pressure-side refrigerant in the supercooler 104 are mixed with each other and are suctioned into a second one of the compressors. In this case, the same effects can be obtained.
While the heat exchanger serving as the evaporator 108 is an air heat exchanger in Embodiment 1, a heat exchanger used in Embodiment 2 is a water heat exchange. Other components denoted by the same reference signs as in Embodiment 1 in a configuration diagram and characteristic diagrams have the same configurations and functions as those of Embodiment 1. A check valve 114 is provided at a liquid refrigerant outlet of the gas-liquid separator 107 in place the fourth flow control valve 113 in order to achieve a cost reduction. Further, the second flow control valve 109 is attached to the outlet of the supercooler 104 in place of the inlet thereof. Since the performance of the supercooler does not affect its attachment position, the attachment position may be selected in accordance with the layout of a refrigerant pipe in an outdoor unit that is mounted at the site.
In this embodiment, with regard to a generating temperature of cold water, when a feed water temperature is 12 degrees C. and an outflow temperature is 5 degrees C., for example, it is possible to perform a high-capacity operation without using injection of a refrigerant into the compressor 101. In such an operation, a temperature range in which an ejector is used may be set to a high-temperature range between A and C as shown in
While the heat exchanger serving as the condenser 103 is an air heat exchanger in Embodiment 1, a heat exchanger used in Embodiment 3 is a water heat exchange for hot water generation (water heater). Other components denoted by the same reference signs as in Embodiment 1 in a configuration diagram and characteristic diagrams have the same configurations and functions as those of Embodiment 1.
In this embodiment, the opening and closing valve 115 is provided in place of the first flow control valve 105 connected to the liquid refrigerant outlet of the gas-liquid separator 107 so as to reduce pressure loss. Further, in the configuration of Embodiment 1, a separation efficiency of the gas-liquid separator 107 is low. Therefore, the liquid refrigerant may flow into the compressor suction, which may result in a reduced concentration of refrigerant oil in the compressor or a seizure due to liquid compression. In this embodiment, the second supercooler 104a is provided such that a two-phase gas-liquid refrigerant flowing out of the gas-liquid separator 107 is completely evaporated and is suctioned into the compressor. This can improve the reliability of the compressor.
The refrigerant used in the refrigeration cycles of the present Embodiments 1 to 3 may include fluorocarbon refrigerants such as R410A, and natural refrigerants such as propane and carbon dioxide. The same effects as those of the present embodiments can be obtained by using propane or CO2. In this case, although propane is a flammable refrigerant, if an evaporator and a condenser are disposed spaced apart from each other in the same housing and if hot water or cold water that has been subjected to heat exchange by a water heat exchanger as described in Embodiment 2 or 3 is circulated, it is possible to provide a safe refrigeration cycle apparatus. Also, the same effects can be obtained by using a low GWP HFO-based refrigerant or a refrigerant mixture thereof.
According to the present invention, it is possible to provide a refrigeration cycle apparatus that solves the problem of a reduction in the capacity and efficiency under operational conditions of low outdoor air temperatures by use of a compressor having an injection and an ejector and that is therefore capable of performing a high-capacity operation and a high-efficiency operation. Also, in the case where the refrigeration cycle apparatus is used in air-conditioning apparatuses, chillers, and water heaters, when an ejector is appropriately designed under operational conditions which contribute the most to the annual power consumption, it is possible to reduce the annual power consumption.
Although the refrigeration cycle apparatus has been described in the above embodiments, this refrigeration cycle apparatus may be embodied as a refrigerant circulation method as described below.
More specifically, this refrigeration cycle apparatus may be embodied as:
a refrigerant circulation method including the steps of:
forming a high-pressure-side refrigerant circuit in which a compressor, a condenser, an ejector, and a gas-liquid separator are connected in series with a refrigerant pipe;
forming a low-pressure refrigerant circuit in which a liquid refrigerant that has flowed out of the gas-liquid separator flows through a fourth flow control valve and an evaporator to a refrigerant suction portion of the ejector;
forming a compressor suction circuit that connects an upper outlet of the gas-liquid separator to a suction port of the compressor such that a gas refrigerant that has flowed out of the gas-liquid separator is suctioned into the compressor;
forming a first bypass circuit that connects a point between the condenser and the ejector of the high-pressure refrigerant circuit to an intermediate pressure portion of the compressor via a second flow control valve; and
forming a second bypass circuit that connects a point between a first flow control valve and an internal heat exchanger to a point between the fourth control valve and the evaporator of the low-pressure refrigerant circuit via a third flow control valve so as to allow a high-pressure refrigerant to take a bypass, the first flow control valve being disposed between the internal heat exchanger and the ejector, the internal heat exchanger being configured to exchange heat between a refrigerant whose pressure has been reduced at the second flow control valve and the high-pressure refrigerant flowing in the high-pressure-side refrigerant circuit;
wherein, while the second flow control valve is opened such that the refrigerant flows through the first bypass circuit, the fourth flow control valve is switched to be opened or closed, and the third flow control valve is switched to be opened or closed.
101 compressor; 102 four-way valve; 103 condenser; 104 supercooler; 104a second supercooler; 105 first flow control valve; 106 ejector; 107 gas-liquid separator; 108 evaporator; 109 second flow control valve; 110 first bypass circuit; 111 third flow control valve; 112 second bypass circuit; 113 fourth flow control valve; 114 check valve; 115 opening and closing valve; 116, 118, 119, 120, 121 temperature sensor; 117 pressure sensor; 201 nozzle; 201a pressure reducing portion; 201b throat portion; 201c tapered portion; 202 mixing portion; 203 diffuser portion; 204 suction portion; 205 needle valve; 205a coil portion; 205b rotor portion; 205c needle portion; 205d signal cable; 300 control unit; 301 detected value receiver; and 302 control signal transmitter.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2010-081125 | Mar 2010 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2011/051469 | 1/26/2011 | WO | 00 | 9/7/2012 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2011/122085 | 10/6/2011 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 6718781 | Freund | Apr 2004 | B2 |
| 7207186 | Hirota | Apr 2007 | B2 |
| 20030066301 | Takeuchi | Apr 2003 | A1 |
| 20050178150 | Oshitani | Aug 2005 | A1 |
| Number | Date | Country |
|---|---|---|
| 2 492 612 | Aug 2012 | EP |
| 2003-97868 | Apr 2003 | JP |
| 2003-279177 | Oct 2003 | JP |
| 2004-37057 | Feb 2004 | JP |
| 2005-76914 | Mar 2005 | JP |
| 2006308181 | Nov 2006 | JP |
| 2007-263440 | Oct 2007 | JP |
| 2008-96095 | Apr 2008 | JP |
| 2008-116124 | May 2008 | JP |
| 2009-24939 | Feb 2009 | JP |
| 2009-270785 | Nov 2009 | JP |
| Entry |
|---|
| Office Action (Notification of Reasons for Refusal) dated Nov. 20, 2012, issued in corresponding Japanese Patent Application No. 2010-081125, and an English Translation thereof. (7 pages). |
| *International Search Report (PCT/ISA/210) issued on Mar. 8, 2011, by the Japanese Patent Office as the International Searching Authority for International Application No. PCT/JP2011/051469. |
| Office Action issued on Mar. 31, 2014, by the Chinese Patent Office in corresponding Chinese Patent Application No. 201180016373.2, and an English Translation of the Office Action. (18 pages). |
| Extended European Search Report issued on Aug. 31, 2016 by the European Patent Office in corresponding European Patent Application No. 11762326.4 (8 pages). |
| Number | Date | Country | |
|---|---|---|---|
| 20130042640 A1 | Feb 2013 | US |
